TW201235565A - Piston-chamber combination vanderblom motor - Google Patents

Abstract

A piston-chamber combination comprising a chamber which is bounded by an inner chamber wall and comprising a piston inside said chamber to be engagingly movable relative to said chamber wall at least between a first longitudinal position and a second longitudinal position of the chamber, said chamber having cross-sections of different cross-sectional areas and different circumferential lengths at the first and second longitudinal positions, and at least substantially continuously different cross-sectional areas and circumferential lengths at intermediate longitudinal positions between the first and second longitudinal positions, the cross-sectional area and circumferential length at said second longitudinal position being smaller than the cross-sectional area and circumferential length at said first longitudinal position, said piston comprising a container which is elastically deformable thereby providing for different cross-sectional areas and circumferential lengths of the piston adapting the same to said different cross-sectional areas and different circumferential lengths of the chamber during the relative movements of the piston between the first and second longitudinal positions through said intermediate longitudinal positions of the chamber, the piston is produced to have a production-size of the container in the stress-free and undeformed state thereof in which the circumferential length of the piston is approximately equivalent to the circumferential length of said chamber at said second longitudinal position, the container being expandable from its production size in a direction transversally with respect to the longitudinal direction of the chamber thereby providing for an expansion of the piston from the production size thereof during the relative movements of the piston from said second longitudinal position to said first longitudinal position, the container being elastically deformable to provide for different cross-sectional areas and circumferential lengths of the piston. This is accomplished by the combination comprises means for introducing fluid from a position outside said container into said container, thereby enabling pressurization said container, and thereby expanding said container and displacing said container between second and first longitudinal positions of the chamber.

Description

201235565 VI. Description of the Invention: [Technical Field of the Invention] 19617 Technical Field A piston chamber assembly includes a chamber delimited by an inner chamber wall and containing a piston inside the chamber wall, The piston will be movable relative to the chamber wall at least between the first longitudinal position of the chamber and the second longitudinal position. The chamber has a plurality of sections having the first portion in the chamber Different cross-sectional areas of the longitudinal position and the second longitudinal position and different circumferential lengths and at least substantially continuous different cross-sectional areas at intermediate longitudinal positions between the first longitudinal position of the chamber and the first longitudinal position And a different circumferential length, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position 'the actuator piston comprising one of the elastically deformable ones for salvating contact with the chamber wall a container of the container wall, the container being elastically deformable to provide different cross-sectional areas of the piston and different circumferential lengths for the piston in the first longitudinal position and the second Adapting to the different cross-sectional areas of the chamber and different circumferential lengths during relative movement between the positions through the intermediate longitudinal positions of the chamber, the actuator piston is produced to have the container without stress and A production size in a non-deformed state in which the circumferential length of the actuator piston is substantially the circumferential length of the chamber at the second longitudinal position. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a solution for an actuator that is used in an automobile and, in particular, an automotive motor, for an alternative and effective functioning of an existing actuator of 159900.doc 201235565, and It is an important target for such actuators to combat climate change. Additionally, the present invention relates to a solution for an effective shock absorber and pump. In particular, the present invention relates to a solution to the problem of obtaining a motor that does not use flammable technology similar to gasoline, diesel oil derivatives and comparable to current motors based on such combustible technologies. In addition, compliance with the need to reduce C〇2 emissions is also comparable to H2 or even air-based flammable motors because the flammable motor does not require a new distribution network for powering the motor. Combustible motors based on oil derivatives lag behind today's technical standards and are only an optimized version of the concept for about a century. This means that it no longer meets today's living standards: valuable and limited waste of available oils and sources of pollution, such as gases like C〇 and similar c〇2 emissions of gases that are important causes of climate change. In addition, the combustible motor tends to be heavy so that for passenger cars, the transport weight ratio (= the weight of one person to the total weight) can be from about 12 (small passenger cars) to 33 (four-wheel drive cars). New combustible motors based on H2 or even air are lacking in distribution networks for delivering energy to such motors, such as gas stations used today to deliver gasoline, diesel and NLG gases. Even current motors that work with air require a "filling" station that provides the necessary high levels of compressed air in large and heavy cylinders. The lack of such a distribution network is based on the air. The reason why the flammable method (for example, gasoline or diesel) works to construct 'so' returns to the Otto 〇 motor again, this situation should be avoided. 159900.doc 201235565 The establishment of a new network of suppliers of the new combustible materials to be used mentioned last time requires a very high financial investment' and gives difficulties due to situations that cannot be undone. Without a properly well-masked network, these motors will not be dispatched because no one will buy such a motor, due to lack of availability' and no one will want to invest until there is evidence that it will form a market In the network. In order to quickly introduce and widely distribute non-contaminating motors, this motor must be independent of the network used to provide the energy. Used for

The current development of Hj's use of filling stations appears to be an interesting but rather tricky idea' because of the extremely dangerous gases in this gas system and should only be disposed of by instructed personnel. 19617 The object of the present invention is to provide a combination of a piston and a chamber to be used in a pump, an actuator, a shock absorber, and the use of such actuators in a motor and others. SUMMARY OF THE INVENTION 19617 Overview of the Invention In a first aspect, the present invention is directed to a combination of a piston and a chamber, wherein: the combination includes for introducing a fluid from a location external to the piston a member in the container thereby enabling pressurization of the container and thereby expanding the container and displacing the container between the second longitudinal position of the chamber and the first longitudinal position. A classic actuator piston is located in the in-line cylinder and the piston includes a piston rod. The piston rod moves due to a pressure difference between the two sides of the piston. The piston mentioned last time may be a piston made of non-elastic material 159900.doc 201235565 and comprising at least one sealing ring, thereby The piston is sealed to the cylinder wall, wherein the piston moves relative to the steam. A piston rod can be guided by bearings on one or both sides of the cylinder. A piston rod external to the cylinder can push or pull a component. The piston rod can also be coupled to the crankshaft such that rotation of the crankshaft draw occurs, which can result in, for example, movement of the carrier (including the actuator and the crankshaft). The actuator piston may also be an inflatable piston when in the inline cylinder, such as the container type piston according to claim 5 of ΕΡ 179 140 B1 and the technical solutions of claims 28 and 34. If the inflatable piston has been internally applied, its preferably reinforced walls may be respectively engaged or sealed to the wall of the cylinder and may act in relation to its movement in the cylinder, as in the inline cylinder The above classic piston. In order to enable this movement, a valve on both sides of the piston (e.g., in the wall of the chamber) may be necessary, and the fluid in the cylinder on both sides of the piston having a certain pressure difference is more The change in pressure of the interior of the container wall mentioned last time may only affect the ability of the piston wall to engage or seal to the wall of the chamber. Still, the internal pressure may have an effect on the speed of movement of the piston via friction between the wall of the container and the wall of the chamber. The actuator according to the present invention is a piston chamber junction having an inflatable piston. The piston may preferably have a fluid under a certain pressure and/or a foam. The wall containing material and preferably a reinforcing piston may allow it to change shape and/or size, and the piston may move within the chamber Or vice versa, it is preferred that the fluid in the chamber and/or the pressure difference of the fluid or foam on both sides of the piston in the chamber is 'the fluid in the chamber can of course still be 159900. Doc 201235565 Another necessary parameter for, for example, air at atmospheric pressure (for example) for control purposes may be that the wall of the chamber is not parallel to the central axis of the chamber and the chamber wall is The angle of the piston in the desired direction of motion has a positive value 'so that the piston can expand in this direction. Preferably, the expansion is from a second longitudinal position of the piston (where the piston has its smallest circumferential dimension: its unstressed production size) to a first longitudinal position of the piston (where the piston has its largest circumference) To do this, see Epi I 384 〇〇 4 B 1 ° The movement of the piston can be initiated by the force towards the inner chamber wall of the container-type piston, which forces occur when the container expands. Thus, the motion can be initiated by a reaction force from the wall of the chamber to the wall of the container. These forces are a reaction to the expansion of the wall of the bar, and the expansion may be to increase the fluid in the piston by introducing more fluid into the container from a location outside the piston via a confined space. The result of volume and / or pressure. In the working prototype of the piston according to FIGS. 7A to 7C (WO 2004/03 1583) having the reinforcement of FIG. 8D (WO 2004/03 1583), the piston is rapidly advanced from the second longitudinal position to the first longitudinal position, And if there is no load, in the chamber having the so-called constant maximum working force shape (W〇2008/025391, Fig. 6B), the fluctuating speed 'has been under the overpressure of the piston inside a few bar more than atmospheric pressure. Pressure is present at both sides of the piston in the chamber, and the inner chamber wall is at a positive angle to the central axis of the chamber in a direction from the second longitudinal position to the first longitudinal position. The experienced fluctuations in the speed of the piston are explained below. 159900.doc 201235565 The contact between the wall of the container and the wall of the chamber can be spray-on or sealed. This situation depends more or less on the load on the piston rod, as disclosed in the prototype. In the absence of imperfections on the actuator, the contact can be (4) closed rather than sealed. In the case where there is a load on the actuator μ, the driving force on the container is greater than the driving force in the case of no load on the actuator, why is there a wall from the container? Sufficient force on the walls of the chamber such that the contact between the walls is sealed. Also for, in the piston

During the movement, the contact of the walls of the chamber can be sequential and sealed. The reason why the piston moves may be as follows. If the longitudinal component of the reaction force from the wall of the chamber to the wall of the container, which is directed to the first longitudinal piston position, is greater than the longitudinal component of the friction between the wall of the chamber and the wall of the piston (the system Pointing to the second longitudinal piston position), the total resulting force will be directed to the first longitudinal piston position and, therefore, the piston will move from the second longitudinal position to the first longitudinal position. Preferably, the end of the container closest to the second longitudinal piston position is secured to the piston rod by a cover (192) which will also move. Self-propelled actuators have emerged that can be replaced by pistons that move outside the piston and the pressure differential inside the chamber. The other end of the container is preferably slidably movable over the piston rod by means of a cover (191), which means that the cover (191) is moved over the piston rod toward the cover (192), the expansion of the container The covers (191) and (192) are closer to each other. This is due to the selected reinforcement of the wall of the container, which is preferably a layer of reinforcement tape from the cover (191) to the cover (192) which is placed in a plane parallel to the central axis of the chamber. Medium (for example, WO 20 (M/031583, Fig. 8D), and as appropriate; brother 159900.doc 201235565 has a slight angle to the central axis of the chamber and/or a stiffener that intersects each other at a very small angle At least two layers. The positive slope of the wall relative to the central axis of the chamber in the direction of the first longitudinal piston position, and the contact surface of the piston with the wall of the chamber is preferably located in the longitudinal direction The fact that below the midpoint of the elastically deformable wall of the piston (optionally just below the midpoint of the elastically deformable wall of the piston), this movement will result in expansion of the wall of the container. The original contact area between the equal walls will become larger and an increased friction will be obtained. This movement may be slowed down as the total resulting force towards the first piston position is reduced. At about the same time, the container is at that Increased contact area and the The wall expansion between the moving covers, which will cause the cover (191), the movable end of the piston to be closer to the cover (192) β fastened to the piston rod, which means that the interior of the container still exists Pressing (the volume of the enclosed space may need to be constant during the movement from the second longitudinal piston position to the first longitudinal piston position), adding HM cattle to the wall of the container, the wall also expanding, away from the second The closer the longitudinal position is, the more rounded it is. This means that the wall of the container flips the wall of the chamber such that the contact area moves away from the first longitudinal direction, thereby increasing the reaction of the wall of the chamber against the wall of the container. Component. The component of the resulting force toward the first longitudinal piston position will increase and will quickly become greater than the friction component such that the raft of the container closest to the second longitudinal piston position moves toward the first longitudinal piston position at an increased rate, Thereby moving with the non-movable cover (192) and thus also with the piston rod, the piston moves from the second longitudinal piston position to the first longitudinal piston position. 159900.doc -10- 201235565 Measuring relative to atmospheric pressure The past Pressure, why this is the case when the piston can be located inside the closed chamber, the last mentioned situation may need to be on both sides of the piston to be able to communicate with the periphery of the combined body, the combined body may preferably be under atmospheric pressure Instead of the enclosed chamber space, the fluid in the chamber can be in spatial communication with a enclosed chamber 'so that the fluid in the chamber does not stop the movement of the piston. This is a concept that can be used in shock absorbers. Whether the enclosed chamber space or the passage to the ambient environment depends on the necessary sealing force from the piston to the chamber wall. The piston-to-wall leakage can also be expected and can exist because the piston to the cavity A 1% seal of the chamber wall may not be necessary (engagement). Thus the passages connecting the spaces of the chamber on each side of the container may be interconnected by one of the channels included in the piston. The piston may comprise a confined space, such as a hollow piston rod. The interior of the piston can be in communication with the enclosed space. The enclosed (4) volume can be constant or variable. i The enclosed space can be connected to the pressure source. In a second aspect, the invention relates to a combination of a piston and a chamber, wherein: the σ piston cavity to the combination further comprises means for removing fluid from the container via the enclosed space for a second to Outside the piston, "a position, # a member that causes the container to contract. The movement during the stroke return portion of the a piston from its first longitudinal position to the second longitudinal position may be performed by at least three possible means. In the traditional way, the Helmet piston seals the wall of the chamber. However, the movement of 159900.doc •11·201235565 can consume energy because the balance of the fluid inside the container-type piston can be oriented toward the 4 enclosed space. The piston shrinks and thus reduces its internal volume, and the internal pressure of the enclosed space may increase. To save energy, the piston may collapse but not seal to the wall of the chamber, which will reduce the piston and the chamber. Friction of chamber 1. The last way can be done by reducing the internal pressure of the container by withdrawing fluid from the container during that portion of the stroke. This can be achieved by controlling the pressure in the enclosed space. In a third aspect, the invention relates to a combination of a piston and a chamber, wherein: the piston is movable relative to the chamber wall from at least a first longitudinal position of the chamber to a first Two longitudinal positions. It is possible to move the piston from the first longitudinal position to the second longitudinal position without engaging the wall of the chamber. This can be done by reducing the pressure inside the piston to the most J level. For example, at the minimum level the wall of the piston is unstressed and its circumference is the circumference of its production size at -pressure (eg, large (four)) when it is produced, so that the piston can reach the second longitudinal position without jamming. In a fourth and fifth aspect, the invention relates to a combination of a piston and a chamber, wherein the piston comprises a piston rod, the piston rod comprising the enclosed space. The piston is contained outside the chamber. Engagement members. The suspension of the piston rod may be a special: for example, according to the type of bearing glaze shown in WO 2008/025391, so that the piston will not be 159900.doc -12- 201235565 In the case of a cavity to the wall, the piston is guided during that portion of the stroke without the guidance of the piston itself. / The piston rod can extend from the piston in a longitudinal direction, and The bearing at the end of the chamber is guided. The case means the piston rod; the enclosed space is included and also includes, for example, a spray located outside the chamber: the component field/the tongue plugs from the first Moving the two longitudinal positions to the first longitudinal position The spitting member can be pushed or pulled. The opposite tie will not be able to push or pull the reciprocating member. One of the external forces of the piston can move the piston from the first longitudinal position to the second longitudinal position. It may not be sealed from the first longitudinal position to the second longitudinal position. 'The force on the piston rod can drive the piston when the piston contains the piston rod. This situation can be achieved by the harmonic member. It is also possible that the piston comprises a piston # extending in two longitudinal directions, and one piston rod may generally be a continuation of the other piston rod. piston rods may, for example, be located outside the chamber Engagement member. When the ends of the two piston rods can extend outside the chamber, one of the piston rods can be rigidly fastened to the chamber, and the other bearing can be moved relative to the chamber. When the piston is moved from the second longitudinal position to the first longitudinal position, the salvage member can be pulled and pushed simultaneously. The opposite return stroke will not be able to push or pull the hinge member. A force external to the piston can drive the piston from a longitudinal position to a second longitudinal position. When the piston may not move sealingly from the first longitudinal position to the second longitudinal position relative to the chamber, when the piston includes the piston rod, the force on the piston rod can drive the piston. This situation can be achieved by the engagement member. 15990〇.d〇c 13· 201235565 In the sixth and seventh aspects, the present invention relates to a combination of a piston and a chamber, wherein the piston rod is coupled to a crank shaft, wherein: a crank is adapted to The movement of the piston between the second longitudinal position of the chamber and the first longitudinal position is translated into rotation of the crank. The crank translates its rotation into movement of the piston from the first longitudinal position of the piston to the second longitudinal position. The engagement member can be a crankshaft that is coupled to the piston by the piston rod. In order to be able to initiate at least the movement of the piston from the first longitudinal position of the chamber to the second longitudinal position, the crankshaft should be rotated before the movement begins by the piston, such that from the second longitudinal position of the piston to The anti-gravity propulsion of the crankshaft resulting from the movement of the first longitudinal position can be transmitted to the piston. Another option is that the movement of the piston between the first longitudinal position and the second longitudinal position can be performed by movement of the crank shaft, for example by another piston chamber combination, wherein The piston simultaneously moves from a second position in its chamber to a first position (at least two cylinders acting together on the same crank shaft). The initial movement of the piston can be performed, for example, by an electric motor that initiates and briefly maintains the rotation of the crankshaft (for a starter motor until the crankshaft is rotated by the piston chamber assembly) In the seventh and eighth aspects, the present invention relates to a combination of a piston and a chamber, wherein the piston rod is coupled to a crank shaft, wherein: the crank shaft includes a second enclosed space. The second enclosed space is connected to a power source. 159900.doc -14· 201235565 The crank shaft can be hollow and the crank &# i曰3 is a confined space. Its anti-gravity is made by l§ «i Sr, and each of them is formed from a cavity of the crankshaft toward the end of the crankshaft shaft. The seal is sealed by the force of the horse. The passage may be in communication with the source of the house. It may also be located in the crankshaft (including the crank pumping so that it can communicate with an external power source. In the ninth aspect, the present invention relates to the piston body , where: main <,. mouth σ

- during a period in which the piston moves from the first longitudinal position to the second longitudinal position of the chamber, the second enclosed space communicates with the first enclosed space in the piston rod ^ from the first longitudinal direction of the stroke During a portion of the position to the second longitudinal position, the piston can be at a certain pressure level at which the piston is produced, and the reduced pressure can be achieved by the piston during the necessary period of time from the first longitudinal position of the piston The first enclosing type is performed in the second enclosed space of the crankshaft. The pressure level at which the piston is produced may not be atmospheric but may be of any pressure rating. When the first enclosed space and the second enclosed space are connected to each other, the higher the pressure level, the less energy may be lost. In a tenth aspect, the present invention relates to a piston and a chamber, wherein: ° ° - the crank shaft includes a third enclosed space in which the third enclosed space is A first enclosed space of the piston rod is in communication during a period in which the second longitudinal position of the chamber is moved to the first longitudinal position. 159900.doc • 15- 201235565 When the movement of the piston changes the direction from the final second longitudinal position toward the chamber to move toward the first longitudinal position of the chamber, the third enclosure space has again Piston pressurization function. The dusting is performed by connecting a third enclosed space to the first enclosed space, the third enclosed work having an overpressure relative to the first enclosed space. After the movement has changed, the M can be added as quickly as possible. ▲ In the tenth aspect, the present invention relates to a piston and a person

Body, wherein: Q - the third enclosed space is sealed from the second enclosure during a period in which the piston moves from the second longitudinal position of the chamber to the first longitudinal position. A shock absorber comprising: - a member for engaging the piston from a position outside the chamber according to all of the previously mentioned aspects, the engaging member having an outer portion, ^ ^ ^ ^. The 卩 position at which the piston is at the second longitudinal position at the position. The shock absorber may further comprise a containment space in communication with the container. The enclosed space may have a variable volume or a constant volume. The grain product may be adjustable. - a shock absorber can comprise the container and the enclosed space which can form at least a substantial portion of the fluid contained in the chamber between the two shells, when the chamber moves to the first longitudinal position _ A § x compression. In the job-longitudinal position, the fluid may be subjected to a pump for pumping fluid, which may include a second piston for engaging the second chamber from a position outside the chamber. a member, a fluid inlet connected to the second chamber and including a valve member, and a fluid outlet connected to the second chamber. a pump wherein the engagement member can have an outer position and an inner position at which the piston can be at a first longitudinal position of the chamber at which the piston can be in the chamber Two longitudinal positions. a pump wherein the engagement member can have an outer position and an internal position at which the piston can be at a second longitudinal position of the chamber at which the piston can be located At the first longitudinal position. The technology of the piston chamber combination can be used in motors, in particular in automotive motors, in particular self-propelled actuators. The piston can also move within a chamber relative to the tapered wall, which can be cylindrical or conical (the chamber in which the piston is not shown (actuator) can be of the following type, where the φ μ The chamber may comprise a convex shaped wall of a longitudinal section near the first longitudinal position. The portion may be divided by a common boundary, and the distance between two subsequent common boundaries defines the longitudinal section The height of the wall, the south degree decreasing with increasing internal pressure rating of the piston, or in the direction from the first to the longitudinal position to the second longitudinal position, the lateral height of the common boundary of the section may be Maximum working force to determine that the maximum working force can be selected to be constant for the common boundaries. Additionally, the chamber can include a wall of a worn surface that is parallel to the cavity 159900.doc -17· 201235565 The central axis of the chamber and the 'the piston chamber combination can be a transition section between the wall of the convex shape and the parallel wall, wherein the transition section can comprise at least one wall of a concave shape 'The wall of the concave shape Located adjacent a second longitudinal position. and 'the piston chamber assembly may comprise a 1-shaped wall that may be located on at least one side of a concave shaped wall. 19617 Overview of the Invention · Feasibility Study The feasibility of the green j motor is as follows. Please review Figure 10B and Figure nB. The two figures give a good bird moth diagram for this problem. This is a system in which the output of the motor is replaced by a new one. The propulsion system is produced in which a τ ^ gas-filled actuator piston is moved from a minimum cross-section to a larger cross-sectional area by means of internal pressure in a chamber having continuously different cross-sectional areas. Thereby reducing the internal dust force' while the fluid of the actuator piston is further decompressed during the return stroke, wherein

τ " mourning is repressurized by using a cascade of energy-saving piston chambers to the combined pumping system according to WO 2000/070227, at least one level in # is by an external green power source ( For example, the 'solar' or preferably any other persistent source of power or optionally a non-sustained source of power. A more efficient and reliable solution can be found in Figures 11G and 13F. The system follows the specifications described earlier. Translational Power Source for a "Green" Motor Based on the Principle of Figure UA The overall system solution for the present invention is that the "green" motor can therefore be based on comparable structural components currently used in combustible engines, but requires new The construction elements are much more effective than their construction elements of the current combustible motor, and are much more efficient, so that the energy used can be from a better "green" (eg 'like the sun' 'It is preferably obtained during operation of the motor by, for example, electrolysis or, as the case may be, by η2 refillable storage tank + combustion of η2 produced by the fuel cell; and/or from -dust force_," The storage tank contains a working body, which is filled in the production of the horse material, preferably low pressure (for example, about 10 bar), and optionally high pressure (for example, < 300 bar).

And preferably, the motor is operated _added, optionally refilled when the motor is not operating; and/or obtained from the battery, the f battery is charged while the motor is being produced, and preferably recharged while the motor is running, And/or optionally recharging when the motor is not operating; and preferably obtained from the system itself, as the energy required may be less than the total energy available for the system to perform the task of generating motion; optionally from another Source obtained. WO 2000/070227 discloses a piston chamber combination technique in which the smallest cross-sectional area of a chamber is at the point where the highest pressure occurs: at the second longitudinal position, the technique can save a lot of energy, for example at the second longitudinal piston position. In a tube with 0 17 mm (0 6 〇 melon (4) from the first longitudinal position, for pumps at 8 bar (current working pressure of the motor motor) to (for example (10) bar, up to 65% energy is saved. Conversely, # is used by actuators rather than pumps, even more efficiently. w〇2〇〇4/〇31583 reveals an expandable piston type (eg, ellipsoidal spheres: small spheres, large spheres) When the unstressed production size of a piston has a circumference, the expandable piston type is not caught in the chamber, and the circumference is approximately the circumference of the portion of the cavity having the smallest cross-sectional area : This minimum cross-sectional area can be at the second longitudinal position. This piston type exhibits special characteristics, using 159900.doc -19· 201235565 as the actuator piston in the chamber' and these characteristics are claimed in the present invention: Yu Yu 4房#远4· If the piston is pressurized at its second longitudinal position from a source of pressure outside the chamber via its enclosed space, and between the sides of the piston in the chamber When there is no pressure difference, there is a non-zero angle between the wall of the chamber and the central axis of the chamber. In a working principle, the actuator piston expands and advances to a chamber card at 260 N. The first longitudinal piston position 'at the first longitudinal piston position, the cross-sectional area being the largest, the chamber has been designed to have a constant maximum working force of 260 N (WO 2008/025391, WO 2009/083274). It can be used in this "green" motor to 'exchange the energy based on the energy obtained from the combustible technology', however, the crankshaft is still used. The energy used for the expansion can be about 5 bar (for example, from 1 bar to 5 bar overpressure, due to an increase in the volume of the piston), for example by a constant volume of the enclosed space from the ellipsoidal sphere expansion (WO 2009/083274). This pressure drop must be obtained again in the system because During the stroke, the actuator piston needs to be in the second longitudinal The position of the piston becomes unstressed, at the second longitudinal piston position it has its production size, and therefore has, for example, the inner pass of the slap. When the enclosed space of the piston is connected to another enclosed space '5 bar overpressure at the first longitudinal piston position can be reused, the other enclosed space can be located, for example, within the crankshaft' and it is again subjected to pressure via, for example, a two-stage pumping process 5 bar is added to the bar. This situation can be effectively carried out by using another aspect of the piston chamber combination technology disclosed in WO 2000/070227, so that 65% can be saved during repressurization. Energy: Further developments are further claimed in the present invention by using, for example, a piston based on, for example, EP 1 179 140 B1, or a piston based on w 〇 2000/065235, 159900.doc -20-201235565 5A to 5H. Additional energy is saved by connecting the crankshaft of the pump to the main crankshaft of the actuator piston from this 65% energy reduction: for example, the additional savings can be assumed to be 35%. Therefore, the total savings are: 76 7% (65 + 1/3 χ 35%). Therefore '23 3% of energy should be obtained from another pump, for example the same as the pump mentioned last time, but now it is derived from, for example, an electric motor from which the electric motor Receiving its power, the battery is optionally by solar cell (which should not be larger than the roof of an ordinary car, or incorporated

The solar cell in the paint of the car is charged, or optionally charged by the fuel cell' or preferably by an alternator, which can be from the shaft or small of the motor's own system轴The shaft of the combustible engine gets its rotation. The energy necessary to make the pump work is 35% of UK, which is 8_2%. - Both the two passes or the noise may not generate heat, and the weight of the motor may be consistent (eg, 60%) lower than the weight of the current combustible motor, while almost all additional control devices required by the combustible motor (eg, It may be unnecessary to control the water temperature for cooling purposes, to control the oil temperature and the exhaust system. A gasoline tank with a Ming and/or plastic body may also be unnecessary. In the future, it can be half the weight of the current car. For example - (10) 836 kg, and designed and produced according to the invention, the weight can be 425 kg. In the case of only the driver, the TWR is: 6.3 可 can be used when only one solar cell can be used The battery will be driven for a long time, but the 'lights of the town street t-lights can give enough light to the solar cells first. 159900.doc •21- 201235565 Moreover, the gear box can be necessary because of this "green" The rpm of the motor can be lower than the rpm of the flammable motor. 19617 Revision 19611 Additives/Feasibility Study The feasibility study has so far not quantitatively incorporated the lack of heat generated by the motor of the present invention compared to the Otto motor type. The type of motor of the present invention is more interesting and convincing when heat losses can be incorporated. Heat loss can give current Otto Motors 25% efficiency. It can be assumed that in the first example the motor types of the invention do not generate heat (isothermal) at all, it is possible to pressurize the fluid from 5 bar to, for example, 10 bar (when the motor is produced, 10 bar has been The energy present in the pressure reservoir is reduced by about 65%. With a self-propelled actuator piston, the overall efficiency of the motor type according to the invention can then be less than 10%, ie 8.75%, and so far this month t» is the work month ij (David JC Mackay, Sustainable Energy-without the hot air-2009). Moreover, when the pump for regenerative pressure (shown in the present invention) uses the type of piston chamber assembly according to the present invention, an additional 65 can be saved. /. Energy. Therefore, if we ignore the heat generated by the pump, this can result in a total energy use of 8.75 % x 〇 875 = 7.6%. However, when a portion of the energy used for pumping may come from another source of energy (from total motor power), such as a battery that is charged by, for example, solar energy (photovoltaic) and/or fuel cell (eg, H2), from the flywheel. Or from the regenerative braking device coupled to the generator, the total energy used can still be less than 10 〇 / 。. It has been previously concluded that the configuration of the motor type according to Fig. 15C or Fig. 15D and Fig. 19D can be the most efficient (simple construction, almost isothermal thermodynamics), and can be additionally the most reliable (no leakage), and The configuration of Figure 13F does not make the 159900.doc •22· 201235565 with a crank that produces a rotation, and the configuration of Figure 13F will be used in the quantitative evaluation of the automotive motor. We use the current VW Golf Mark II model RF, 1600 cc, weigh 836 kg 'with 53 kW / 71 pk gasoline motor' containing 4 cylinders of 0 81 mm and 9 bar pressure ' and 77 mm stroke, as this The basis of the invention. This situation gives a maximum force of 1159 N per cylinder, approximately U6 kg per cylinder. If all the burning parts are taken out of the vehicle body, and aluminum is used instead of steel for the vehicle body', it can be assumed to be about 50°/. The weight is reduced. Therefore, it must be 58 kg per cylinder to drive the aluminum body, up to 4 passengers and luggage. The chamber of the pump shown in WO 2008/025391 has a maximum working force of 260 N (26 kg), approximately in the entire 4 mm stroke from 2 bar to 1 bar, and has 0 58 mm to 0 17 respectively. The diameter of mm. The use of an inflated ellipsoidal shaped piston in this chamber, the actuator works very well in practice. Thus, two of these chambers, now part of the actuator, can be equivalent to one of the cylinders of the VW Golf Mark II gasoline motor, now made from Shaoxing, and all parts related to combustion are taken out . In the motor according to the invention, the pressure in the enclosed space of the actuator piston will change from X bar (stroke: second, first longitudinal position) to about 〇 bar (stroke first, second longitudinal position) ). The value of "x" can be chosen to be as small as possible to limit energy usage. Since this special chamber type is used, the magnitude of the working force is independent of the pressure value, and it is possible to use a pressure window to limit the pressure to a maximum level of 3.5 bar to a minimum level of about 55. The starting points can be moved to the configuration of the pressure in the spherical shaped piston in the rotating chamber of Figure 13F, however 'the chamber can now have the shape shown in Figure 13F 159900.doc • 23- 201235565 A simpler shape, since 31⁄2 bar uses only a fraction of the stroke in this particular chamber (216.2 mm for 400 mm), the force per actuator piston is a maximum of 260 N. The volume change of the sphere can be quite large: from V2=4/3x3.14x 12·553 (彡25.1 mm; P2=0.35 N/mm2)=8280 1111111x^=4/3x3.14χ 23.453 (Lu 46.9 mm ; PfO.05 N/mm2)=54015 mm3 ' It is 6.5 V and P=7. The angle of the wall of the chamber with respect to the central axis is: 1^=302.78-86.57=216.21, r=l 0.9: angle=2.9°, which is good. For a cylinder, a full stroke L is used to "virtual" the volume of the actuator piston at the first longitudinal position (indicator 1) to the volume at the second longitudinal position (indicator 2) The energy is:

WjS0thermal P]Vjln(P2/Pi)=0.35x54015xln 7=0.35^54015^ 2.302585><log 7=36788 Nmm/channel/piston/rotation=36.8 j/channel/piston/rotation if each channel will only exist An actuator piston. Regarding the number of strokes per minute, the motor according to the invention is not as fast as the gasoline motor (900 revolutions per minute) 'this is due to the slower expansion and contraction taken by the actuator piston'. Made of reinforced rubber. Let us assume that the number of revolutions per minute is 60, so it is rotated once per second (15 times slower than the combustible motor)"W = 36.8 J / channel / piston / s. There is a 2X4 "equal" chamber (cylinder) and the power is therefore 294.3 J/S/piston, which is 〇.295 kw/piston. § When using 5 pistons, these 360. For one of the five sub-chambers to the middle of each of the chambers (Fig. 13F), the power produced can be: 5 χ〇 295 kW = 1.47 kW ° For the hypothetical 1 rotation/second check: A quantity of 53 kw of flammable gasoline horse 159900.doc * 24 · 201235565 reached, which was previously described in this study, can save 92.4%: only 7.6%: 4.03 kW can be used. If the number of revolutions per second can be roughly (rounded): 3 rotations/second, then the situation can be followed first by following the above conclusions. Therefore, 'a motor contains 2x4 "equal" chambers, each chamber containing 5 pistons in 5 sub-chambers, rotating at 3 rotations/second (=丨8 rotations/min) 3x1.47 = 4.4 kW of power, this power is enough to shake the VW Golf Mark II with the name body. Literature (David JC Mackay,

Sustainable Energy-without the hot air, page 127, Figure 20.20/20.21) exposes a small electric car that operates at a power of about 4.8 kW' and the power comes from an 8x6V battery, which can be charged by a battery to drive 77 km. And the charging time is several hours. This may be an option if the energy is from a battery that is not rechargeable during the driving of the brake, but is not a preferred embodiment. How much energy is required to pressurize and decompress the actuator piston, and can the pressurization and decompression be performed while driving the car? The pressure must be varied in the actuator pistons of the motor that are energized. We use the principles known in Figures 11F and 13T. The energy may be from kinetic energy from the rotating chambers, wherein, for example, a piston of a classic piston chamber combination is moved by a camshaft that is coupled to the main motor shaft of the motor. If we have used data to calculate the motor power, the pressure change of the inflatable ball piston can be changed by changing the volume of the enclosed space of the actuator piston by changing the volume of the "below" of the classic piston. . The actuator piston is required from the second longitudinal position to the first longitudinal position (due to 159900.doc •25· 201235565 from a small sphere shape (0 25.丨mm) with medium internal pressure (3.5 bar) to low The volume change per stroke per stroke of the larger sphere shape (0 46.9 mm) of pressure (0.5 bar) is made by the internal pressure change of the actuator piston 'where the volume of the enclosed space is constant. The force is 26〇N/stroke/piston, independent of internal forces. Therefore, in the case of 8 chambers each containing 5 pistons, and with 3 rotations per second, the power generated is: 4.4 kW . The required energy for the first longitudinal position to the second longitudinal position (Figs. 14A and 14B): 1 . The actuator piston is deflated by deflation of the actuator piston into the enclosed measurement space The shape of the sphere (0 46.9 mm; 0.5 bar) changes to its production shape (0 25.1 mm; 〇bar (overpressure)), which now increases the volume of the enclosed space, if the pump piston and the wall of the enclosed space The friction between them is small enough 'this increase volume may not consume energy. 2. Inflate the sphere (0 25) claws; 〇巴) by reducing the volume of the enclosed space (0 25.1 mm; 3.5 The energy required for the pump piston to be closer to the actuator piston is:

Wjsotbermal — P1 V1 ln(P2/P , ) = _ 1 (check this)χ 4/3 x 3”4 X 1 2 · 5 5 3 X In UVlUxmoxuowwog 4 5 = 12454 Nmm/channel/piston/rotation, and for 2x4 chambers, 5 actuator pistons per chamber, 3 rotations per second, = 12.5x8x5x3 Js = 1.5 kW. (If absolutely 卩(五)巴', ρϊ>2 is definitely 4.5 bar). Therefore, the resulting gross power is 4 4 kw and the power required to operate the motor is at least 1.5 kW, so about 159900.doc • 26 - 201235565 2 kW is required in addition to other possible losses. In order to pick up the motor, if the pump according to the above will be present in the car, then we compare it to what is available: the current compressor has the following specifications: 220 V, 170 Ι/min, 2.2 kW, 8 bar, Pressure storage tank 100 1. We need power, but at a lower pressure, the modified compressor inflates the pressure reservoir a little faster. For 8 bar, P = 2200 W, therefore, for 3% bar, using the same repressurization time as 8 bar, only 3/8x2200 = 825 W is required. Even if the battery is a 24 V battery, the current will still be 825/24 = 34 4 a, this current is very sufficient for the battery's and therefore, the motor group in Figure 11A, Figure HB, Figure 11G and Figure 12A, Figure 13A In the state, there will be many batteries available, in which the pump with reference numeral 826/831 will be electrically powered. It would be possible to charge only the external power source so that the vehicle would be inactive during the multi-hour 'capacitor solution (Figure 15E) is still in its research phase, this solution is not a preferred embodiment, but An option. It may be better to avoid power conversion and use the motor configuration of Figure 1C. In the motor configuration of Figure 15C, pump 826/83 1 is connected to the shaft of a combustible motor using, for example, H2. Preferably electrolysis and, as the case may be, production by a fuel cell. The last mentioned process was powered by electricity from a battery that was charged by an alternator that was in communication with the shaft. The combustible motor requires 825 W. This motor can be used with 24 cc/66 cc of Otto cycle (VW Golf Mark II with 53 kW, 1600 cc, Lu 90 159900.doc -27- 201235565 mm, 4 cylinder motor) , 825 w is about 24 ", 9 〇 a cylinder ' or 3 times faster; 2.2 kw is about 66 ", 9 〇 一个 a car classic motor, which can be comparable to the large current light treadmill motor used A light-duty treadmill motor was shown on television a few months ago, using electrolysis of water stored in a tank (originally used for gasoline) and using the generated helium for the combustion process, which is feasible. A car, an externally-assisted motor of this size, all the extra combustible equipment that we have thrown out of the earlier Golf Mark II in order to obtain a lower weight needs to be replaced by a comparable (four) of a light-duty treadmill motor. Unfortunately, it is necessary to benefit from pollution or CX)2 emissions, and the noise can be successfully reduced by the noise reduction measures of the #, and the weight is only one car and the weight of the 15 i water tank of = 15 0 Assuming a 1/6 (= about 35 kg), this feasibility study can still be established. Ending the Addition described in 19617 Revision 19611_Feasibility Study The further development of the piston can be moved in a specially designed chamber to maximize the force of the piston, but the expansion of the gland is minimized (=pressure drop and ' The interrupted movement or "pause behavior" of the piston (see page XX) can be compensated by the corrected internal shape of the chamber. The motor is also controlled according to the first principle of Figure 1A. For example, each crankshaft-actuator piston chamber combination is as follows. It is assumed that the pressure reservoir may have been pressurized only once by an external pressure source and is therefore added to waste during production of the motor. The piston can be actuated by means of an electric starter motor using a battery that has been charged by the solar battery and/or charged by a classic generator that rotates around the spindle shaft of the motor. The starter motor initially makes The crankshaft rotates and, due to the movement, pressurizes the actuator piston inside 159900.doc -28·201235565, the pressurization of the actuator piston will then replace the start of the movement of the actuator piston, And thus the start of the rotation of the crankshaft. The starter motor can then be decoupled from the crankshaft. It is also possible to start the fluid 822 by internally pressurizing the actuator piston by means of the open pressure reservoir 814. The motor, the pressurization initiates movement of the piston, see Figure 1B. Accelerating the motor (i.e., accelerating the rotation of the crankshaft) can be accomplished by raising the pressure inside the actuator piston The so-called pressure reducing valve between the pressure groove and the actuator piston is opened in the open (tube) line [829]. Slowing the rotation of the crank shaft can reduce the pressure inside the actuator piston, By closing the opening of the pressure reducing valve. In order to give more power to the motor (torque on the spindle shaft), this can be done by increasing the pressure for the existing configuration of the actuator piston chamber assembly. Or more than one actuator piston chamber assembly may be present per shaft. Stopping the motor may be accomplished by fully closing the decompression chamber in the (tube) line [829]. The governor is connected. Lu hai actuator live Further details of the pressure management can be organized as follows: There may be holes in the wall of the crank of the crankshaft and at the end of the piston rod, the holes being associated with a second and third enclosed space and the circumference Enclosed space communication" at a point in time, the holes may be in communication with one another such that the enclosed space of the actuator piston may be associated with the second enclosed space or the third enclosed type within the crankshaft Spatially communicating, when in communication with the second enclosed space, the piston can then be pressurized via its enclosed space and moveable from the second longitudinal position to the first longitudinal position in the chamber. The three-sealed enclosed space is connected to 159900.doc -29- 201235565. When the piston can be moved from the first longitudinal position to the second longitudinal position, the deflation reduction of the piston may occur. The main piston pump (818) starts. a decrease in pressure in the third enclosed space in the crankshaft and a decrease in pressure in the enclosed space in the piston rod, respectively due to the crankshaft of the pump and the actuator piston The associated preset position of the crankshaft, which can be mounted In the same shaft. More details of the pressure management of the actuator piston can work as follows. There may be holes in the last second longitudinal position of the piston. More than one actuator piston chamber combination in the motor may be present on the same shaft. However, this concept may not help to comply with these specifications. Because of the current flammable motor, more than one piston chamber assembly per shaft may make the motor run more smoothly. Moreover, of course, the torque on the shaft will increase. The crankshaft itself may be a less efficient way of generating rotational motion, and in addition, the stroke length of this type of piston chamber combination may be greater than, for example, the stroke length of the current combustion motor, ie, the crankshaft" Miscellaneous (4) <face is substantially lower than the current combustion motor cut m. The gear can be required for the target system and the gear ratio can be different from the gear ratio of the current combustion motor. The gearbox can reduce efficiency by, for example, 25%, and this efficiency can be used by using. Improved by low friction bearings such as fluid dynamic bearings (improved eg: %). Since the motor may be running all the time, it may be necessary to leave the device. Therefore, the % of energy required for an automotive motor should come from, for example, green energy, such as 'solar energy from, for example, solar cells on the roof/hood of a car/paint of the entire car body, and the solar energy may be excessive . Of course, 159900.doc 201235565 If some special batteries are charged with energy from wind or solar energy, they may be added. This addition increases the static weight of the vehicle and increases the WTR ratio. A decentralized structure is required. Therefore, when the target is, for example, a "green" car motor, this motor type may not fully comply with these specifications. Therefore, in order to comply with the specifications, a crankshaft and gears can be avoided. A rotary power source for a "green" motor based on the principle of Figure 2A. This situation leads us to the point where the piston can be rotated rather than translated. This new type of motor can be a "green" Wankel motor. . A better use of A1 energy can be obtained by using a motor without a crankshaft, at least for the propulsion system' using the same principles as those mentioned above. In addition to the foregoing, the reduced use of energy can be specifically rotated around a centerline in a chamber by rotating the piston from "1" to "2" in the chamber. The distance of the position is reduced to approximately the radius of the piston such that the motor can power the shaft almost continuously to obtain the surrounding centerline concentrically resting around the spindle shaft of the motor. A1 A conical chamber may be curved in a circular direction in the longitudinal direction and may fill 360° or a portion thereof, in which a piston may act as a self-propelled actuator. There may be at least one piston acting in the chamber. The motor may include one or more actuator piston chamber assemblies that may use the same shaft. In the center of the circular movement of the actuator piston and/or the chamber, there may be a shaft that can be coupled to a 159900.doc -31 - 201235565 construction element that operates the vehicle or another vehicle. Such as wheels, such as propellers. There are two ways to construct such a motor. One way is to move the central axis of the actuator piston rod in a plane in which the central axis of the chamber lies. Another possibility is that the central axis of the actuator piston rod can be positioned perpendicular to the plane of the central axis of the chamber. In either case, the actuator piston can be moved, or the chamber can be moved, or both can be moved. Actuator pistons similar to those used in elongated conical chambers (ellipsoid to sphere and sphere to ellipsoidal shaped piston) in a circularly curved chamber (eg, WO 2000/070227, Figure 9A, Figure) The actuator piston of 9B, Fig. 9C)) appears to be impossible to operate because the chamber can be curved in a circular direction in its longitudinal direction, so that the bearing of the piston rod of the actuator piston is lost. In fact, it is possible to use (smaller) spheres to (larger) spheres and (larger) spheres to (smaller) sphere type actuator pistons (eg, W〇2002/077457, Figures 6A-6H, 9A to 9C), which is a less complex construction of the bearing for the piston rod due to its symmetrical form. For example, the piston is positioned to be perpendicular to the plane of the central axis of the circularly shaped chamber via the sigma actuator piston. Since the shape of the chamber is the same as the shape of the in-line chamber used when the piston is moved, the actuator piston can move in the chamber 'but now it moves in a circular shape. However, a portion of the wall of the piston (which is located behind the displaced central axis of the piston that is perpendicular to the central axis of the chamber) and from the center of the piston to the chamber engages (or seals, or engages or seals) the piston The line of the line 159900.doc • 32· 201235565 is substantially smaller in size than the ellipsoidal sphere piston that translates over the central axis of the elongate chamber. This is why the power used by each actuator piston (sphere to ball) may be less than the power used by the ellipsoidal ball actuator piston. This situation requires a motor 'where more than one actuator piston is used per chamber. An additional problem is also the need for a motor because the actuator piston is intermittently moved (see later) and more than one piston in the same 360° chamber produces smooth motion. Moreover, when the (equal) actuator piston has expanded to its maximum extent, a very short moment occurs, during which the pressure in the actuator piston is reduced, and this pressure reduction can also give motion. The "pause instant" is such that one actuator piston overcomes the "pause" in the movement of the other actuator piston, which may be located at different locations on the central axis of the chamber. As an example, if 36〇. The chamber can be divided into four identical sub-chambers, and the number of actuator pistons can be five, halving 360. . A major advantage of such a rotary motor may be that the length of the return stroke of the actuator piston from the first circular position to the second circular position has been substantially reduced compared to the crankshaft option and may be at least in the first circle The size of the largest radius of the piston at the location is due to the fact that the circular first position and the circular second position continue directly in the direction of rotation. It is therefore necessary to manage the pressure drop inside the actuator piston and the subsequent pressure rise. There are two basic ways in which abalone can change the internal pressure of the actuator pistons. An option is that each of the actuator pistons can be connected to the valve by a passage that can increase/decrease the force of the actuator pistons 159900.doc -33 - 201235565. The valves can be computer operated such that the pressure inside each of the actuator pistons is optimal for its position in the chamber. In addition, it may be the case that the computer manipulates the pressure tank from a pressure source that acts as a source of pressure = pressure so that the distribution of available pressure in each of the actuator pistons can optimize the available fluid waste forces at such Use in actuator pistons. The second option is, for example, a very short change in the volume of the enclosed space. This change can be replicated by a moveable piston that is sealingly coupled to, for example, the wall of an elongated chamber. The chamber may be suitable for a type having a different cross section in the displacement direction. Due to the speed of movement, the chamber can be of a type having a weird circumference such that the piston bends only during operation. However, of course, a chamber having a different displacement circumference can also be an option. The plug H is moved within the chamber, a tongue plug cup that is in communication with a cam plate that is connectable to a shaft to which the motor is mounted. - The wheel can be at the end of a piston rod that flips the cam disc. Therefore, this motor type thus consumes no fluid 'only consumes the energy (pressure) contained in the fluid. 360. The chamber is rotatable about - (four), and the 14 lines of the (four) can intersect the center of the chamber. The chamber may be part of a wheel and the outer portion of the wheel may have a recess' in which there is a drive belt that can drive an auxiliary device, such as a generator. The chamber rotates and the piston does not move. The motor is undoubtedly the less complex solution of the two options for a rotatable motor. The resulting torque is also better', for example, five times in this solution because there are more than five pistons of the same size per chamber. One of the most reliable systems can be a fixed piston in a rotating chamber 159900.doc -34· 201235565 is 'The motor can contain more than one piston, for example 5 pistons, each of which can be located at different rotational positions' Since the displacement of the piston from its first rotational position to its second rotational position can be powered by, for example, the other four pistons, this positioning allows the motor to rotate smoothly. Moreover, the "pause behavior" (see later) of a piston moving from the second rotational position to the first rotational position can also be supported by, for example, the other four pistons, so that a pause may not be observed. "." A gearbox may be unnecessary

Because the pressure rating of the fluid inside the piston will define the speed of the spindle rod 'this necessary pressure window can be easily obtained by the construction of the motor, the pressure wheel can easily be adjusted by a speed To define. Therefore, it can be redundant, and this adds an additional weight loss of about 5 〇 kg. (10) Mark Π conversion has now been reduced to about 35 〇 kg. Twr is now about 5.6. Controlling the rotary motor can be performed in a manner similar to controlling a motor having a translational piston (or 4 to a motor having a shifting chamber and not moving the piston, or even when both the chamber and the piston are not shown). Start, accelerate, slow down, power supply, control means: make the motor work stop, and stop using. Actuating the motor can be performed by a power on/off switch, the power on/off switch is turned on, and the other switch is connected to the circuit so that the starter motor is connected to the persimmon pole. Turn. There may be a starter motor on the same shaft used for moving the piston or moving chamber. The starter motor uses I59900.doc •35- 201235565 from the starter battery. The starter battery itself is from solar energy. Power charging. The starting motor can rotate the shaft and thus initiate rotation. Pressure management can be performed as follows.

A In the motor in which the piston moves, it is necessary to pressurize the piston and change the pressure when the maximum circumference changes to the transition point of the minimum circumference. This situation can be done electronically by means of a computer and jets. This solution requires a new solution as the fluidity continues. Otherwise, it is possible to create a mechanical solution because the change in pressure is of a certain frequency: for example, cam pumping, which is in communication with the drive shaft via a synchronous belt. The cam draws (iv) a flexible membrane in fluid communication with which the pressure of the fluid needs to be managed. To make this solution less complicated' the chamber may contain one, but not for example four sub-chambers, so that the pressure only needs to be changed once.

AA, in a motor in which the chamber moves, it is necessary to pressurize, for example, 5 pistons, and change the force when the maximum circumference changes to the transition point of the minimum circumference. This can be done electronically by means of a computer and jets. Since the pressurized fluid needs to be sustained, this solution requires a new solution. In the motor in which the chamber moves, the inner (four) force is required to be different from each other but in the same order and the pattern itself is repeated in each round, so that the camshaft solution is also possible here. The timing belt is in communication with the drive shaft. The cam disc can be in fluid communication with the flexible membrane of the 159900.doc 201235565. The pressure of the fluid needs to be managed per piston.

A more reliable system for the translational power source B of the motor based on the principle of FIG. 11F can be obtained by the new principle for pressure management according to FIGS. 11F and 13F, ie by using the piston and the enclosed space. The fluid is separated from the fluid in the repressurization phase, and the change in pressure in the piston can be obtained by a change in the volume of the enclosed space of the piston. This improved reliability can be related to reducing the number of displacements of the pressurized fluid, which may not leak. In this principle, the control device can use energy primarily to change the volume of the enclosed space. This situation can be done very well, so that the energy is also reduced here by using a piston again (for example, one piston is used for the function of the piston, and preferably one piston is used for speed/power, as the case may be A separate piston for power management), the piston is moved in a sealed manner in a cylinder having continuously different cross-sectional areas of the cross section and, for example, a varying circumference so that the energy used can be regained 65 〇/ Reduce y. Moreover, for this principle, an embodiment with a fixed piston in the rotating chamber can be the best option for reducing energy usage. A constant circumference can also work 'but the reduction may be lower.

The change (and consumption) of the pressure of the fluid in the B-inflated piston can also be performed in an alternative manner to the principle illustrated in Figure 11A. By temporarily changing the volume of the enclosed space of the piston, the adjustment of the volume gives a change in the power (torque) of the motor, and this can be done continuously or simultaneously. The energy system is from 159900.doc -37· 201235565 This is still a more efficient way of using available energy, and this new principle can increase the reliability of the motor relative to the principle shown in Figure 11A. In this new principle 'in the joint (such as 'crankshaft - large end bearing, and two parts of the connecting rod), the high pressure fluid and the piston when the piston moves from the second longitudinal position to the first longitudinal position There is no leakage between the low pressure fluids when the first longitudinal position is moved to the second longitudinal position. The energy used can be used to move the piston in a conical chamber that can be > star optimized to reduce the working force applied to the piston rod of the piston to change the volume of the enclosed space. In addition, the energy used can be used to adjust the volume of the enclosed space in a piston chamber combination similar to the piston chamber combination for the volume change. The movement of the volume change piston can be performed by using a pressurized liquid that moves the piston from the point to the other point in the chamber by means of, for example, a valve or other type of control device or by magnetic guidance. __ point and move from another point to - point. This situation is also established for the piston that adjusts the volume of the enclosed space. The control of the movement of the plug can be performed by communicating with a governor controlled by, for example, a person or a computer. The rotary power source for the motor based on the principle of Fig. 13Ε The fluid (four) force change (and consumption) in the gas-filled piston can also be performed in place of the principle (four) of Fig. 12 . By (iv), the volume of the enclosed space of the piston is changed, and the adjustment of the valley product at the same time as U can give a change in the power (torque) of the motor, and the action can be performed continuously or simultaneously. This principle is more effective in rotating power sources than in the displacement power source system, because the distance from the first rotational position to the _ coin-rotation position is almost 159900.doc •38· 201235565 J lightly by the cam disc to 'the motor power source around the shaft zero, therefore, changing the enclosure space guidance 'the cam disc can be mounted on the shaft to rotate. In fact, this motor is the most efficient motor. A motor having a circular chamber may comprise a wall having at least a portion of the length parallel to the chamber; a centerline in the motor, a conical chamber (slim or Type, which is produced by the actuator piston, can be

Fixed. This may also be the case where the knife incorporated in the motor is any of mercury, the chamber in which the actuator piston is located may include an internal convex shape of a longitudinal section near the longitudinal position. The wall's portion may be divided by each other by a common boundary, and the distance between the two adjacent common boundaries is determined by the height of the wall of the longitudinal section, the height of which is increased with the internal pressure of the piston. Decreasing in value, or in the direction from the first longitudinal position to the second longitudinal position, the lateral height of the common boundary of the sections can be determined by the maximum working force, which can be selected for These common boundaries are determined. Where the piston is located in a longitudinal chamber having an inner wedge-shaped center, the convexly shaped walls are concavely shaped. Moreover, the piston chamber assembly can include a wall of a cross-sectional boundary that is parallel to the central axis of the chamber. Moreover, the piston chamber assembly may include a transition between the convex shaped wall and the parallel wall, and the transition portion may include at least one concave shape 159900.doc •39·201235565 shaped wall, The concave shaped wall can be located adjacent a second longitudinal position. Moreover, the piston chamber assembly may include a concave shaped wall that may be located on at least one side of a convex shaped wall. The various embodiments described above are provided by way of illustration only and should not be construed as limiting the invention. It will be readily apparent to those skilled in the art that various modifications, changes and combinations of the elements of the invention can be made without departing from the spirit and scope of the invention. All piston types, in particular those of a container having an elastically deformable wall, are sealingly connected to the chamber s during its movement between longitudinal positions, halally connected or not connected to the chamber 15 wall. Alternatively, it may be connected to the chamber wall in a saliva and sealing manner. In addition, it is also possible between the walls; there is engagement, it is possible that the walls are in contact with each other' and this may occur, for example, in the case where the container moves from the first longitudinal position to the second longitudinal position in the chamber. 'The type of connection between the walls (sealed and/or meshed and/or contacted and/or unconnected) can be achieved by using the correct internal pressure inside the wall of the container: high pressure for sealingly connected, Lower pressure for the connection of the saliva and for the connectionless (production-sized container), for example, atmospheric pressure, therefore, a container having a -enclosed space may be preferred because of the enclosed type The space can control the pressure inside the container from the position outside the piston. Another option for the spray connection is a thin wall of the container which may have a reinforcement extending beyond the surface of the wall so that the leak can occur in the wall and cavity of the container 159900.doc • 40- 201235565 Between the walls of the room. In the case of an actuator piston connected to the spindle shaft by a crankshaft, and there are more than one actuator pistons all connected to the same spindle rod, the advantage may be that the longitudinal positions of the actuator pistons are different from one another The rotation of the spindle shaft can be more stable, such that the "suspension moment" that occurs when each of the actuator pistons moves from the first longitudinal position to the first longitudinal position may occur at other time points. . It may be necessary that the actuator pistons are engaged in the chamber or in a sealed manner (this situation may differ between a longitudinal position and another longitudinal position when moving in the chamber) Moving from the second longitudinal position to the first longitudinal position and from the first longitudinal position to the second longitudinal position, the situation having the following characteristics 'force on the piston rod and thus from the actuator piston to the connecting rod of the crank shaft The force can be independent of the position of the actuator piston (see description and drawings with reference to "19620") to synchronize the force of each of the actuator pistons with the spindle. The susceptibility study has so far not been quantitatively incorporated into the absence of heat generated by the motor of the present invention as compared to the Otto motor type. The motor of the present invention is more interesting and convincing when we share heat loss. The heat loss gives the current Otto Motor 25% efficiency. When we assume that the motors of the present invention do not produce flaws at all in the first example, it is possible to pressurize the fluid from 5 bar to, for example, 1 bar (when the motor is produced, 1 bar is already present at the pressure) The energy in the tank is reduced by about 65%. With a self-propelled actuator piston, the overall efficiency of the motor according to the invention can then become less than 1%, ie 8.75%, and this is unprecedented (David 159900.doc 41 - 201235565 JC Mackay, Sustainable Energy-without the hot air). Further, when the pump for regenerative pressure (shown in the present invention) uses the type of piston chamber assembly according to the present invention, an additional 65 〇/〇 of energy can be saved. Therefore, if we will ignore the heat generated by the pump, this will give a total energy use of 8 75% x 〇 875 = 7.6%. However, when a portion of the energy used for fruit extraction can come from another source, such as solar energy (photovoltaic), from a flywheel, or from a regenerative braking device, the total energy used can still be less than 丨〇0/〇. A motor based on a crankshaft solution with an elongated chamber and a piston (Figs. 11A-11D and 11F) can be preferably used as the main motor of a transport vehicle (e.g., a car) with a piston rod/ A connecting rod is connected to the crank shaft. The wheels or thrusters can be coupled to the central main motor by a drive shaft and a dispersing device such as a universal joint. Optionally, the motor type can be used as an eccentrically positioned motor that can be directly coupled to each of the propulsion devices, such as a wheel or a propeller. A chamber based on a chamber and a piston is preferably used as a eccentrically positioned motor in a transport vehicle (eg, a "L car), the chamber being located around a central axis, the piston increasing and decreasing The size of the chamber (Fig. 12A to Fig. 12 (:, Fig. 13A to Fig. 13G). Each of the motors can be directly connected to each of the propulsion devices. As a case, as a center motor , which can be connected to the propulsion devices by a drive shaft. The control of the motors can preferably be performed by a computer, in particular, one of more than one propulsion device used in each motor directly connected to the transport vehicle. A flywheel' can be preferably connected to a main center motor and, as appropriate, 159900.doc 42· 201235565 is eccentrically positioned to each of the propulsion devices. A flywheel can be used to keep the motion steady (classic solution) Or after the braking of the transport vehicle (and simultaneously storing the dynamic braking energy), the energy for acceleration is obtained, or the energy is given to the pressure storage tank (for example, reference symbol 814, 839, 89 〇, 889). One of the pumps (For example, reference element symbols 818, 821, 82A, 826, 826' in FIGS. 11A, 11B, 11C, 11F, 12A, 12C, 13A, ΠΒ, 13E, 13F). All or some of these types of flywheels may be present in a transport vehicle comprising a motor according to the invention. Another aspect of regaining energy while braking may be a pump directly connected to a spindle rod The spindle shaft can be a central drive shaft (eg, reference component symbols 821, 82A) that pumps fluid to a much higher pressure and communicates the resulting high pressure fluid to a pressure reservoir (eg, reference component symbol) Optimal configuration of the chambers of the 814, 839, 890, 889) ° 19617 actuators. The geometry of the chamber that is optimally used in conjunction with the actuator piston may be different from the chamber intended for optimal use of the pump. The geometry of the chamber may vary depending on the actuator and the conditions used in the pump. For example, the actuator piston needs to give maximum force when moving at the appropriate speed by using as little energy as possible. Actuator connected to the crank The plug, the sub-condition may be different from, for example, the sub-condition of the actuator piston in communication with the rotating chamber: for example, the point in time at which the maximum force is required. In order to use the actuator piston as a self-propelled piston, the elongate chamber must be The wall of the chamber is of a type that widens outwardly from 159900.doc •43 to 201235565 when moving from the second longitudinal position to the first longitudinal position. Thus, from the second longitudinal position to the first longitudinal position, the wall is relative to The angle of the central axis of the chamber needs to be positive. This angle determines the speed of the actuator piston. Moreover, of course, the transition from one point of the wall to another in the longitudinal direction needs to be smooth, so that the limit Friction between the actuator piston and the wall of the chamber. The inflatable actuator piston itself needs to have an internal pressure to be able to carry the wall of the chamber. In order for the actuator piston to be movable, the center of the flexible wall needs to be closer to a first longitudinal position than the circumference, the first longitudinal position being smoothly connected to the wall of the elongated chamber. The longer this distance, the higher the speed of the actuator piston in the chamber. The reaction of the wall of the chamber against the actuator piston determines the force with which the piston pushes itself away from the wall of the chamber in the direction of the first longitudinal position. Therefore, if at least one cover of the actuator piston (preferably closest to a second longitudinal position) is fitted to the piston rod, the force to the piston rod is also determined. In part 1962 of the present patent application, a chamber (eg, Figure 21A) is shown. 'The chamber will reduce the working force of the piston rod at 8 bar to the bottom of the pumped fluid when used in a pump. About 65%, which is excellent for achieving pumping purposes. This reduction will be seen in comparison to the force required in an inline cylinder, and this reduction is a comparison of a classic high pressure bicycle pump and an advanced bicycle pump having the shape of Figure 21A. In the chamber, the maximum force is substantially independent of the pressure of the fluid in the chamber and is therefore substantially constant during the pumping stroke (e.g., from 2 bar when the maximum force has been reached). The same chamber in the actuator for the actuator containing the actuator piston can have the following advantages: a large 159900.doc •44·201235565 constant stroke during the stroke from the first to the longitudinal position to the first longitudinal position. The working force can therefore be only about 1/3 of the working force when the in-line cylinder 10 having a certain diameter has reached the maximum pressure (the same comparison source as the comparison source mentioned above). The force may not be suitable for the purpose of the actuator piston, and in addition, a constant force may not be suitable for use with the crank. The same situation can be established if the right chamber is J-wound ("round") rather than slender. In a particular solution where the actuator piston does not move and is located in a chamber for rotational movement, a chamber type such as the chamber type mentioned above may be used. If more than one piston is used, for example 5 pistons (eg, Figure 10B), such a chamber may be necessary, with each piston at a different circular position in each sub-chamber to the middle, thus having a different pressure At this time, the force obtained by each/tongue plug can be the same for all pistons so that none of the pistons pushes the other pistons, the total force being five times the force when only one piston will be used. Therefore, a gear may be necessary to achieve the required torque and speed, depending on the purpose. Other optimal configurations of the actuator chamber may be possible. The parameters of the actuator piston connected to the elongated chamber of a crank may be: • a relatively short length L of the chamber to obtain a relatively short stroke length, force F(p, d, μ) in the second The longitudinal position can be varied during the stroke of the first longitudinal position such that the maximum force is obtained when the actuator piston reaches the extreme of the first longitudinal position [where F = force from the piston rod; ρ = pressure inside the actuator piston) ;d=the diameter of the chamber at a certain longitudinal position; μ== the friction between the wall of the chamber and the flexible wall of the actuator piston 159900.doc •45- 201235565 number], • at The frictional force F() is zero during the entire return stroke, and this friction is zero by gently withdrawing the overpressure of the actuator piston to obtain [F() = the wall of the winning chamber and the actuator piston The friction between the flexible walls], • the rate v(, F) should be optimized by the length l of the chamber [where v = the speed of the actuator piston relative to the chamber; The angle between the wall of the chamber and the central axis of the chamber; F = force from the piston rod], • the energy used is as small as possible, This: When moving the actuator piston from the second longitudinal position to a first longitudinal position, while changing its volume, while the space enclosed Formula temporarily closed, the pressure drop required as small as possible. There is a chamber having a wall circumferentially about a central axis, the center of the chamber being located at the center of the main motor shaft, wherein the chamber rotates 'and there is more than one actuator piston therein and The pistons do not move and spray the chamber wall 'other than the chamber of Figure 21A, the parameters of the chamber may have a circumferential cross section: • Regardless of the distance from the center of rotation, the circumference of the chamber wall needs to be the same This may affect the shape of the cross section of the chamber. • The frictional force needs to be optimally small, for example, by using an enhanced lubricator like a super-strong lubricating oil, which is much smaller than the super-strong lubricating oil. The friction coefficient of other lubricants works well for both rubber and metal (similar to steel or aluminum). However, it may be necessary to also produce an optimum configuration of the piston to achieve the effect that the circumference of the chamber wall (regardless of the distance from the center of rotation) needs to be the same circumference of the chamber wall (distance from the center of rotation) Irrelevant) needs to be phase 159900.doc •46· 201235565 the same - 19617 thermodynamic problem when the system (the elongated chamber with the actuator piston connected to the crank shaft, can be symmetrically arranged around a central axis, can be When the fluid in a crankshaft or a chamber in communication with the main shaft of the motor is compressed, it is entirely possible to generate heat. When producing a device in which the motor is used, storage of the fluid in the pressure reservoir may have been configured. When the motor is running, when a higher pressure fluid from the last pump of the pressurizing pump cascades into the fluid of the reservoir, a smaller portion of the heat may be generated in the reservoir, wherein the reservoir may have Low pressure (Fig. 11A to lie, Fig. 12A to Fig. 12C, Fig. 13A to Fig. 13B). The pressurization of the fluid from the third enclosed space of the motor type using a crank generates a greater portion of the heat in the first pump of the pressurized pump cascade, wherein the β Hai crank is mounted on the spindle shaft of the motor The first pump can receive its energy from the spindle shaft. Moreover, another portion of substantially the same amount of heat may be generated by a pump that can obtain its energy from other sources of energy (such as any solar energy source, such as a solar cell, a fuel cell, a battery that has been charged by solar energy, or A classical energy source, such as a battery that is charged by a generator connected to the internal combustion engine, as appropriate (Fig. 11A to Fig. UC, Fig. 12A). In the actuator piston, the pressurization from the second enclosed space in the cavity of the enclosed space + actuator piston body and the expansion in the third enclosed space occur due to the pressurization Slightly larger than the expansion, so the actuator piston can obtain a higher temperature than its temperature at the start of the motor (Fig. UA to Fig. 11 (:, Fig. 11F, Fig. 12A to Fig. 12C, Fig. 13A to Fig. 13E)» 159900.doc •47· 201235565 Therefore, this system generates heat, which can be used, for example, to heat a car's cab or to heat a third enclosed space in which the expansion occurs in the third enclosure (adiabatic) Since the third enclosed space is located in the crankshaft, the adiabatic is not easy to complete. Therefore, the third enclosed space may be more or less diathermy* Of course, when heat is generated, It is best to compensate for the heat generation: isothermal conditions. The pressure change inside the actuator piston is moved in the cavity of the two-way pump to (in fact, the enclosed space of the actuator In the case where the piston is controlled, it occurs in the chamber by changing its volume. Compression and pressurization 'balances heating and cooling: this situation can be the case of not moving the combination of the actuator piston and the moving (rotating) chamber (Fig. 13G). In addition, now the thermodynamic aspect This principle is the most effective motor principle 'because (theoretical) efficiency can be almost 100%. 19617 Revision 19615 The energy motor working with the motor can work with any other energy source, preferably continuous, as the case may be Non-sustainable. Such energy sources may require about 7.5% of the energy fed to the motor, and 7.5% may be the limit of efficiency improvement relative to, for example, the classic motor that burns fossil fuels by using the Otto cycle. Similar to, for example, the sun, potential energy from water and wave energy, and other sources, such energy sources do not cause emissions of undesirable chemicals such as C〇, C〇2, NO, etc. when generating energy. For motors according to the present invention, The energy source may preferably be, for example, an electric power, an electric grid (= power stored in a condenser), or any type of battery Without a focusing member (mirror), 159900.doc -48- 201235565 is charged by, for example, photovoltaic solar cells by solar energy or by, for example, using a fuel cell compressed by H2 or air by hydraulic potential energy or the like. The fuel cell can be charged. "There can be obtained from the electrolysis that can be stored in the tank: the electric power can come from a special battery (non-starting battery) that can continuously give energy." The battery can be used with the motor. The alternator charging 'and/or power from the shaft can be from the photovoltaic solar cell ring can also be stored in a special tank and can be directly inserted into the fuel cell. The optional energy source can be power, capacitor or (d) type f A battery, which is charged by a steam-steering generator, which is burned by fossil fuel: or by a motor-driven compressor, burning fossil fuel, etc., the motor of the present invention can have a .... —, outside, Μ月5 Hold: Sexual, as the case is continuous and non-sustainable. (When the motor is used as a transport device with limited possibilities for connecting to a large energy source, or by a motor in a train, car or airplane), the battery can be temporarily suspended.

The amount of raw material (for example, through the material of the electric coffee (for example, Η士私)) is carried out by means of softness. Therefore, the temporary energy-containing material of the external energy source is made by ι 5 hai (special). "The pick-up of the person in the middle of the piece can be moved beyond this strategic distance, in the strategic distance power: long-term. 卩 full. Strategic distance can be as good as for the commuter car (four), every case is enough The helmet f can be refilled and refilled, for example, for driving a longer distance. 159900.doc •49- 201235565 It may be necessary to drive without refilling, or even twice the distance The last mentioned value may be the limit that a person can perform every day. Preferably, a mobile power source (e.g., a battery, a fuel cell, the available H2 that is used to achieve combustion purposes) has been installed in the transport device. H2〇 electrolysis, pressurized fluid, or other possibilities not mentioned herein) may be self-contained for at least one day. It may be preferred to drive at night. The power source may preferably not increase much. Extra dead weight (increased rat), this pair of cars It's not important, but this extra deadweight increase may not be decisive for efficiency. There are several battery types, and the latest #battery type is high power and effective, but adds a lot of extra weight and space. It takes a long time to charge a new battery, but a fast exchange of batteries is not feasible because this fast exchange requires infrastructure and may not separate the old battery from the new battery. Charging from and/or solar cells Energy usage may not be sufficient (see Feasibility Study). & 胄 has a plug and connection to the power network, the power network is available infrastructure. To reduce charging time to i minutes to 2 minutes, based on suitcase size The load of the capacitor and the controlled release of power to the pool of the motor system can be a complete solution to all of the problems mentioned above when using the battery. The battery is still under development in the United States. Fuel cells may not be cheap and effective, but they won't increase much. External weight, and its no noise, this is the traditional method used when the flammable (fossil) motor is connected to the alternator. 159900.doc •50· 201235565 Contrary to (for example, the required h2 can exist safety hazard#, call it Storage can be difficult 'this is due to leakage from the tank, and no leakage for other substances. Although there are already household electrolysis systems on the market that use electrolysis to produce h2 for own use, a distribution infrastructure may be required. However, After seeing a light-duty treadmill with a combustible motor (<50 cc) in 2009, the combustible motor (<50 cc) uses instant electrolysis from water contained in a tank that typically stores gasoline. It is also possible to do this for the motor according to the invention. The electricity for electrolysis can come from a battery, which is set

The juice is used for equipment (constant use)' and the battery can be charged by the alternator using rotational kinetic energy from the motor, while the power is additionally charged by, for example, a solar cell. By using a fuel cell (eg, using the generated power to charge the battery, the power generated by the battery can be used in the motor portion. An alternator can be in communication with the spindle shaft of the motor and additionally charge a battery, such as The constant-use battery and a possible start-up motor battery for a possible start-up motor. Solar cells can be added to the charging of the batteries. By means of a fuel cell (for example, using electricity, the generated electricity can be directly Connected to the motor function, bypassing the battery, etc. Another possibility may be, for example, H2 for flammable purposes, for example, a motor comprising a classic piston in-line cylinder combination with a crankshaft, The shaft connected to the alternator rotates, and the alternator charges the battery. The alternator can also be directly connected with other motor functions by wires. The power of the combustible motor can be supplemented by the power, so The motor of the present invention is not capable of generating power. The flammable motor is 159900.doc • 51· 2012 The power of the 35565 may be extremely small compared to when the current combustible motor is used for motor functions. This makes it possible, for example, to make the electrolysis process for generating h2 movable, for example, for use in an automobile. If, for example, an electric motor can be used to steer the shaft that is in communication with a crank, the two-way effect of, for example, the volume of the enclosed space in the rotating chamber that does not move the ball piston can be changed. Power is required, the piston rod of the pump has been fitted to the crank. The shaft can be a main shaft of the combustible motor that uses, for example, & as a fuel. In another configuration, it can have And the configuration of the same configuration in the overall solution, in which the pump is used for repressurization of the fluid, and the repressurization of the fluid is used to control the actuator, the actuator Controlling the pump. When the pump has been exchanged by a camshaft, another configuration that does not use electricity to change the volume of the enclosed space can be used, so the power can therefore only be used for the starter motor, and the power Can come from a battery, which can be charged by an alternator driven by a spindle of the motor and/or by a solar cell. The camshaft solution can preferably use more than one piston, optionally using a piston. A small pump is needed for acceleration 'this acceleration means that the higher pressure 'electric motor in the actuator piston driven by the spindle rod or by the electric motor is self-designed for constant use of the battery to obtain its energy. The external water storage tank is filled with a tank containing conductive water, and if the water is not electrically conductive, it is possible to add a conductive material to make the water conductive. The pressure storage tank can be pressurized not only by the cascade of pumps, but also by The situation can be borrowed from an external pressure source (for example, 2701 in the respective drawings) by a pluggable connection. The battery can be used not only by actuators, solar cells or/and % fuel cells. Charging 'and optionally charging via an external power source via a pluggable connection (eg, 2700 in the respective figures) 〇 the piston and the chamber may both revolve around the chamber The turn around the midpoint to rotate. The invention can be constructed to have a lighter weight than a motor based on a classic piston-cylinder combination. It may be necessary to supplement or add to the solar cell insofar as the motor can function in the dark. This can be, for example, any other persistent power source such as, for example, a H2 type fuel cell that reacts with 〇2 in the atmosphere and gives power and H2 〇. This fuel cell may require a relatively small reservoir. The reservoir may have a reduced pressure. That is, the distribution system can be at home or the distribution system may not be very dense. In a motor type in which the enclosed space is cascaded with the repressurizing pump of the pump, electrical power can be used to impart energy to the electric motor that drives the piston pump via another crankshaft, which can be used, for example, in the dark The supplement of the monthly amount of the solar cell b, or this can be done at any time. Additionally, a generator can be added to this type of motor that can be driven by the spindle shaft and can charge the accumulator. In a confined space, the type of motor that separates the fluid from the H cascade can require more power to control the valve. This makes it possible to have another power source, such as the fuel cell described above, 159900.doc -53- 201235565 solar cells are more likely. Electrical energy can also be used in an external pump cascade system that has not been added to the drawings of Figures 11F and 13F, which may be required to repressurize pressure tanks 1063 and 889, respectively. This can be done by cascading the pumps. At least one of the pump cascades is in communication with the main shaft and at least one is in communication with an external power source. The pumps can be in communication with a pressure tank. For the solution in Figure 13F, a pump may also be sufficient. 19617 Gearbox-Clutch The motor according to the present invention may have a certain maximum number of revolutions per minute (rpm) that is subjected to two transition points (first longitudinal position and first) when the piston is operating in the elongated chamber The change in shape and/or pressure at the point of change from the first circular position to the second circular position is limited at the two longitudinal positions or when the piston is operating in the circular chamber. The flexibility of the inflatable piston is critical: its wall, which can be made, for example, of rubber, thus the hardness of the rubber; and the reinforcement layer; and how many reinforcement layers are used; and if more than one layer is used, For the angle between the reinforcing layers, see Section 1965. When the piston is operating in an elongated chamber, the motor according to the invention is a two-stroke motor: half rotation = power stroke and the other half is a return stroke. When comparing the motor to a four-stroke 4-cylinder 1595 ec VW Golf Mark II petrol motor with a maximum idle speed of 7 rpm to 8 rpm and a maximum of 2500 (check) rpm in the feasibility study, By the configuration according to the feasibility study, in order to generate the same power, the phase g speed of the motor according to the invention can be half of the above & speed. This reduced speed will be suitable for the motor according to the invention. 159900.doc -54- 201235565 *When the clutch starts to mesh with the flywheel, the reduced speed will limit the advancement of the main motor shaft. In the feasibility study, we have pointed out that when the vehicle has a considerable torque per kg of weight (relative to the above mentioned G〇if n, according to the invention, the net weight of the vehicle is reduced by 5〇%), the motor is now not available. The configuration is taken into account as long as we maintain the configuration. Right using a gearbox (manual, automatic _ for example, Variomatk® from Van Doorne or automatic gearbox with fluid), the gear ratio and gear number of the gear can be different from the gear ratio in the car used before # The number of gears. The last mentioned situation has to deal with the specific characteristics of a combustion motor (restriction of the functional window in terms of rpm, usually the main motor shaft) which is not present as a major part of the motor according to the invention. If a gearbox would be necessary, the last mentioned case would preferably have an automatic gearbox' as appropriate with a manual gearbox. The number considerations can be as follows: - Wheel diameter: 0 0.65 m (VW Golf Mark II), - Motor idle speed: 350 rpm to 400 rpm - Motor drive speed: 2 > Therefore: 60 km/h: Motor: 750 rpm Wheel: 490 rpm Therefore: Gear ratio: 1:1 5 down 90 km/h: Motor: 1 rpm Wheel: 735 rpm Therefore: Gear ratio: ι:ι · 35 down 120 km / h: motor · · 1250 rpm wheel: 980 rpm Therefore: gear ratio: 1:1.28 down 159900.doc -55- 201235565 140 km / h: motor · · 15 rpm 1 · · 1 · 31 Down wheel: Π43 rpm Therefore: Gear ratio: Conclusion: • If reverse traction is not required, the gearbox can be unnecessary and the weight reduction can be obtained. • It seems that the shape change of the inflatable piston is still too high, and if the situation has been proven to be correct, the gearbox j is unnecessary. If so, the relatively slow-turning motor may require a button. Still its rPm, in order to be able to couple the motor to the wheel by the clutch; Ding, Ma can use these rpm for normal size wheels, it may be necessary to slow down again. The 19617 motor sound is attributed to the lack of an explosion, and the height of the power portion of the motor according to the present invention has a very small amount, and this can be greatly different from the generally well-known engine sound based on the Otto motor design of the gasoline horse: See 仏他咖, pp. 86-89, February 2007 '", post (10) _" 'About prior art). In fact, there may be a sound of the inflatable rubber piston body rubbed by lubrication (e.g., super lubricating oil) from the metal or plastic of the chamber, which sound may have a low frequency. Only in the elongated chamber design, there will be a frequency of pitch (from the second longitudinal position to the first longitudinal position) / silence (from the first longitudinal position to the second longitudinal position), while in the circular cavity There will be continuous sound in the room design, because these sounds are also frictional sounds, so the sound can have a low frequency two because the motor according to the invention is a two-stroke motor (remember: green motor 丨), and today's car motor is large Most are four-stroke motors, so the root 159900.doc .56· 201235565 The number of revolutions per minute of the motor according to the invention can be half of the number of revolutions per minute of the motor designed according to Otto in order to achieve the same or equivalent power. This also reduces the number of revolutions per minute, which adds sound that will be low frequency. In addition, there is a sound from a pump (compressor) that produces a pressure for repressurization of the pressure tank. When a pump is of the type of piston chamber according to the present invention, it can give some noise from the valve and noise from the release of the fluid from the chamber to the pressure tank and the suction of the reduced pressure fluid, according to the motor of the figure. Type of pressurization. The current air compressor based on the piston moving in the elongated chamber sounds absolutely boring. These sounds may come from the fact that the speed of the air may exceed the speed of the sound, making the shock wave a source of boredom. In the design according to the invention, the velocity of the fluid will preferably be lower than the speed of the sound, as the case may be, for example, by opposing wave design (such as what Audi did in his racing car, 纟 almost no The noise, #i motor is still the case for the combustion motor type) to suppress shock waves from waves exceeding the air speed. In the repressurization type according to Fig...., there is no valve and only the extra piston chamber combination is present for pressure change. This motor type is furthermore the most efficient and otherwise quietest of all motor types according to the invention. The generation of electricity for (re)charging of the pump-powered battery may require a better h2 as the motive fluid, optionally as a motive fluid for gasoline/diesel or any other combustible fluid (see Feasibility Study). A pump of approximately 60 cc (comparable to a light-duty treadmill motor) can be repressurized with a pressure of 159900.doc •57·201235565, which can be applied to the pressure of the main motor section. The sound of such a light-duty treadmill motor is often boring, but it may sound acceptable if sound suppression is sufficient. Therefore, the total sound of the motor according to the present invention is not zero, such as in the case of an electric motor, but a sound having a high frequency and a low frequency. This makes it possible to recognize the car as a car by sound, which is better than a car that runs at a low speed with only one electric motor. If a low frequency is inferred from a working prototype, the low frequency can be changed.

19620 Overview of the Invention I In a first aspect, the invention is directed to a combination of a piston and a chamber, wherein: the chamber includes a wall at a boundary of a section parallel to the axis of the nail of the chamber. [The chamber includes a second chamber in communication with the first chamber via a passage, the passage comprising a longitudinal section of the wall having a concave shape, the wall of the second chamber being parallel to The central axis of the chamber ^ ] (for example) the conical chamber of the advanced bicycle pump can be divided into a plurality of longitudinal sections. The common boundary of the longitudinal sections is by the longitudinal position of the piston from the chamber. The overpressure (eg, above atmospheric pressure) rating (eg, 丄巴, 2 bar..., i〇巴) that may be generated when moving to the second longitudinal position is defined. The chamber includes convex and concave shaped portions of the longitudinal section portion that are divided from one another by a common boundary, the resulting height of the walls of the longitudinally-section portions decreasing with increasing overpressure rating, The lateral length of the common boundary of the section is determined by the maximum working force 159900.doc • 58· 201235565 selected to be constant for the common boundary, at least in the vicinity of a second longitudinal position. Another factor that is decisive for the proper shape of the longitudinal section of the chamber in the bottom position (second position) (with respect to the proper sealing of the piston to the wall of the chamber) is that there must be sufficient space for the piston At the position and allowed to move (for example, when the chamber has been designed to reduce the working force): Minimum longitudinal cross-sectional area at the point of highest pressure: for example, WO/2008/025391, where the smallest part of the chamber It is 0 17 mm. The longitudinal section portion may have a convex and/or concave side. A portion of the chamber is used in the bicycle pedal pump to achieve the purpose of maintaining the convex/concave shaped portion of the chamber at a person's engineering height so that the user feels comfortable while pumping (WO/2008/ 025391), at the chamber portion, the 'convex shape ends and the concave wall portion begins and the chamber portion matches the conical bottom portion. There is a spring-operated piston, for example, a flexible inflatable inflatable container piston (eg, EP i 384 〇〇 4 B1) 'If there is a seal from the piston to the wall of the convex/concave chamber wall Pressure, and if the longitudinal component of the friction between the piston and the wall of the chamber is less than the longitudinal component of the sealing force, then the piston can begin to move itself from a second longitudinal position to the chamber in the chamber The first longitudinal position, wherein the cross-sectional area and circumference of a second longitudinal position are smaller than the cross-sectional area and circumference of a first longitudinal position. The position of the chamber in contact with the piston may have to be parallel to the central axis of the chamber, such that the piston maintains its position controlled by, for example, the user of the bicycle pump. This parallelism provides a sealing force that does not have a longitudinal component, and thus the piston sealed to the wall of s is only held in the position that the user wants to be in. 159900.doc • 59- 201235565 eg EP 1 179 14QB1 shows a chamber in which a portion of the inner wall of the chamber is parallel to the center in the top (first longitudinal position) and bottom (second longitudinal position) of the chamber Axis: Therefore, when the pump is not in use, the piston rod is positioned here, or when the pump is in use, the piston rod is in the direction of the user, and the last mentioned direction change also occurs in the top of the chamber. . In EP 1 1 79 140 B1, there is no reasoning about parallelism. For this type of piston, it is possible to move the second longitudinal position to the first longitudinal position in the chamber when the piston is (4) (4) in the chamber or when the piston is sealably movable in the chamber of. In the second aspect, the invention relates to a combination of a piston and a chamber, wherein: ° ° the chamber has an outlet between a convex wall and a concave wall, § Hai exit with a soft Pipe connection. The longitudinal section portion may have a convex and/or concave side. The part of the chamber is used in the bicycle pedal system to achieve the purpose of keeping the convex/concave shaped portion of the chamber at a person's engineering height, so that the user feels comfortable when pumping (wouoo'ww) At the chamber portion, the convex shape ends and the concave wall portion can begin and the chamber portion can match the conical bottom portion. If the bottom portion is hollow, it can be used in three ways. An option is to keep the portion open and to add an outlet to the chamber at a second longitudinal position of the chamber. The outlet can preferably be in direct communication with a hose. Depending on the condition, the outlet includes a stop valve, wherein the check valve is in communication with a swelled 159900.doc 201235565 expansion chamber. The expansion chamber is built into the bottom portion of the chamber. The expansion chamber may only be required for higher pressures, and thus retard the speed of the pump at lower pressures 'this is because the volume of the expansion chamber will also be inflated, regardless of pressure. Such a solution if the piston will be stuck in a concave shape transition from the wall portion of the convex shape of the chamber to the other longitudinal position, or if the tongue plug is too large to travel to another longitudinal position Can be required. In the third aspect, the invention relates to a body of a piston and a chamber, wherein: the wall of the concave shape is located between at least two common boundaries. The hollow portion is preferably used as an additional pumping volume for the chamber and the piston should be able to move toward the bottom portion and within the bottom portion without jamming. Therefore, a smooth transition from the wall of the convex shape of the cross-sectional portion is necessary. The transition portion contains a wall of a concave shape. Depending on the height of the section, depending on the pressure rating, the walls of such concave shapes may be located at least between the two common boundaries, ± mentioned below at higher Fortitude forces. If there is not enough space in the vicinity of the first longitudinal position for the piston to move, then it is optional to use: at that position the piston must have sufficient space and allow it to move. In a third aspect, the present invention is directed to a piston and a chamber body, wherein: the second chamber includes a third chamber, the third chamber and the second chamber via a check valve Connected. 159900.doc • 61 201235565 Therefore 'there may be a point on the wall of the chamber at which the convex shape on the side of the longitudinal section must be converted to the bottom of the chamber from a first longitudinal position In the other part, in which the wall of the chamber wall is parallel to the central axis, in order to smoothly perform the transition, a transition from a convex shape to a concave shape is required, and therefore, the shape of the side of the longitudinal wear surface at the transition portion is The direction from the first longitudinal position to the second longitudinal position needs to be concave. If the piston has a seal that takes a certain length, the length of the seal is so long that the seal does not conform to the transition from the convex shape side to the concave shape of the longitudinal section, the solution can be by one-way The valve closes the chamber and forms an outlet, and uses the remainder of the chamber as an expansion tank. This can be useful for proper pumping under high pressure. In both cases (the bottom portion is used as an additional pumping space for use as an expansion tank), the locations of the common boundaries have different lengths from a first longitudinal position and the distance therebetween is different, the pump with the expansion tank The stroke volume is less than the stroke volume of the pump using the bottom portion as part of the stroke volume. In a fourth aspect, the invention relates to a combination of a piston and a chamber, wherein: the chamber is lifted by an open fourth chamber, the chamber having an outlet, the outlet ending at the In the four chambers. The fourth chamber is simply a base chamber that has nothing but its characteristic shape. The chamber may have an outlet which is a nozzle. In the fifth aspect, the present invention is directed to a piston and a chamber, wherein the outlet is in communication with a hose. 159900.doc -62- 201235565 In order to optimize the pumping speed, the hose of the bicycle pump can expand under a certain pressure so that an expansion groove is formed there. This means that the pump is extremely efficiently pumped at low pressure, wherein the hose does not form an expansion tank, and such a pressure tank produces a larger volume than the volume of the tire alone for pumping. Most pumping needles are made for low pressure tires. The expansion of the hose can be limited by the stiffener of the hose' and the expansion can occur only on one portion of the hose. The piston is moveable in engagement with respect to the chamber wall. The piston is sealingly movable relative to the chamber wall. The additive described in 19617-19620 uses the chamber from Figure 21A (which is used in advanced bicycle pumps), and the amount of energy used relative to current high-pressure bicycle pumps can be reduced from 8 bar to 1 bar pressure. About 65%. The reduction is calculated as follows: The chamber of Figure 21A has been designed such that at any pressure, especially at higher pressures, and therefore at 8 bar or 1 bar, the maximum force is 26 〇Ν β. The current high pressure pump contains the inner diameter. For an in-line cylinder of 0 27 mm, the working force at 8 bar is: ρ = ρ χ〇 = 〇 .8 Χ〇 · 25 χ 3 · 14 χ 272 = 458 N. At 10 bar, this working force is: 572 N. At 8 bar, the reduction is: 458_26 〇 / 458 = 198/458, making the reduction J .43/. And under 1 baht is: 54%. At 12 bar: μ, 272*/687 leads to 60% ' and 14 bar gives: 8〇1_318**/8〇1=66%, and 16 bar gives: 916-363',, /916= 60.3〇/〇. The efficiency of this advanced bicycle pump is much higher than the current high pressure (four) treadmill pump, and this situation affects the choice of 260 N as the maximum force. However, the following design has been made: when using an in-line cylinder section of 0 17 159900.doc -63 - 201235565 mm in addition to the conical section of the chamber, the pump can have a pressure rating higher than ι〇巴:F at 12 bar: 1.2x〇.25x3.14xl72=272N*; F at 14 bar is: 318N**, 16 bar is 363N***. Conclusion: However, 'because the selected maximum force F=260N affects the result, the 65% stated at 8 to 10 bar should be 54%, so the recalculation is optimized for the bicycle pump (but now it is specifically targeted The chamber used in the motor may have benefits. 19617-Addition to the design of the 19620 elongate conical chamber

The chambers of Figs. 21A, 21B, 22 to 25 (inclusive) of Ep Patent Application No. 100754027 (08-09-2010) have been designed based on the following mathematical considerations. The elongate conical chamber of a pump (having a central axis) is shaped to connect some point coordinates outside the central axis: along the central axis, the y-seat is perpendicular to the central axis. The chamber has a different cross-sectional area & and a first longitudinal position and a second longitudinal position, the first longitudinal position having a cross-sectional area greater than a kneading area of a second longitudinal position

a mid-piston moving between the first longitudinal position and the second longitudinal position, the piston sealingly coupled to the wall of the chamber, having (4) a production size of the circumference of the second longitudinal position 'the piston attribution The shape of the chamber has a certain predetermined maximum working force. The positions of the points related to the center and the axis are determined as follows. When the piston moves from the first longitudinal position to the second longitudinal position in the elongated tubular chamber, the remaining volume is Vx, which is defined from the overpressure side of the plug to, for example, the furthest away Second longitudinal position (defect) measurement 159900.doc -64 - 201235565 The interlobed product of the chamber at positions Lx, Lx, where there is an overpressure Px, and the overpressure system is relative to the standard pressure (eg, Calculated by the large gravitational pressure, the remaining volume V x is used in this calculation:

Vx=3.14.[〇.〇〇〇46.Sx3-f(l.118-0 0.00139.L2).Sx] where: °〇139.L).sx2+(〇〇9〇〇-2.236.L+ Ρχ=ζ The remaining volume under the bar, where νχ=

Vx is above the standard pressure V〇/(z+l) Ο

V〇 = total volume length of the conical chamber. Where S = L = total of the conical chamber

Sx = step size in the iterative calculation process. It is now possible to iteratively calculate the step size S (to overcome the calculation of the cubic equation when the computer software is not available) px=z bar (z) appears in the longitudinal direction of a job-pressure window (eg 51 bar to 10 bar overvoltage) Bit [step S may be part of the total length 1 of the conical chamber calculated along the central axis (eg,

1/1000): The sx is found from the equation and the coordinates of the point are given as SX.L.

If the chamber contains a non-conical portion (as seen, for example, in Figures 21A, 21B), then only the projected length of the conical wall portion on the central axis needs to be used in the calculation of I^LX.找到 Find the y coordinate of the point as follows. If a certain maximum working force F_ has been selected, the position of the points at the longitudinal position Lx at the central axis from the selected point can be obtained as follows: 〇χ=υ〇·〇〇8.Ρχ( Ρχ Ρχ 为 为 Ρχ Ρχ Ρχ Ρχ 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 若 若 若 若 若 若 若 若 若 若 若 若 若 若The y coordinate of the point at which the axis is at the longitudinal position Sx 为 is Dx/2 形状 the shape of the chamber wall is thus the line through all the points found. In practice, if the line is drawn as a fold line, the line may be smoothed ("peditise") such that a continuous shape of one of the chamber walls will be obtained. 19630 Round Chamber Design, Overview of the Invention The circular chambers shown in Figures 13C and 14D have been divided into, for example, four identical sub-chambers in which one chamber can be moved And the piston does not move. The chambers have been constructed in such a way that the effect of each chamber can be that each piston having a different position in each of the circular subchambers can have the same circular force to the chamber wall. of. This will avoid unnecessary friction, which will reduce efficiency and increase wear of the piston. The chamber can have a circular force of helium and therefore a constant torque. The size can only depend on the pressure. Thus, it is not necessary to divide the circular chamber into more than one chamber in order to contain more than one piston. However, the angle of the walls of the sub-chambers is greater than the angle of the wall of a chamber having the same circle as the central axis. Therefore, the force of each chamber is greater than the force for only one chamber for several pistons. The chamber in the circle 12B may in fact have the same basic design as the design mentioned above with respect to Figures i3c and 14D, in which the piston is movable and the chamber is immovable. The piston can have a constant circular force to the chamber wall. 159900.doc • 66- 201235565 The sub-chambers have been constructed such that the chamber contains two circular portions in the circular portion. Each of the circular portions has its own center point 'Shai's center point is placed in the opposite quadrant, around the center point of the circular central axis of the (sub)chamber and is the same distance from the center point distance. The circular portions are placed around the central axis of the chamber and may be circular. SM-PVT1 in a final version 'with the presence of the elongated chamber of Figure 21A/B parallel to each other and perpendicular to the (virtual) common boundary line of the central axis (3) of the elongated chamber (1) (9, 11, Compared with the cross-sectional portion of 13, 15, 17, 19, 21, 23, 25, 27), we expect the cross-section of the chamber such that a common boundary line in the longitudinal section of the circular chamber is from the cross-section The line drawn from the farthest boundary of the chamber to the center point of the central axis of the circular chamber (for example, the two arrowed lines in Fig. 27C with two center points) converges, but does not know exactly Where is the center point and the center point of the farthest circular chamber line of the section is the same as the center point of the nearest circular chamber line of the section (in Figures 27A-27C, we take two centers Point), in view of the requirement, the maximum force of the cavity-to-center actuator to the chamber wall is independent of the position of the actuator in the chamber' and thus independent of the internal pressure of the actuator. The SM-PVT2 cavity to (with the characteristics mentioned above) is slidably and/or sealingly moved through the spherical shaped piston (Fig. 10H, with the pilot configuration of the chamber), the piston being located in the chamber in. By moving the chamber over the piston, a considerable problem arises, such as when the front wheel of the car is turning at the corner, the two front wheels are not located at the same distance from the center of rotation (?), and in order to make the steam 159900 .doc -67- 201235565 The car turns over the corner, the wheels need to have separate shafts, and the angle of the wheels relative to the direction is different at the same time - the speed of the wheels is different at the same time . Therefore, the reaction force from the chamber to the contact area of the piston is not equally divided on the circumference of the contact line, and the contact line should be the same as the common boundary line (of the elongated chamber). Thus, in either case, the intermeshing/sealing connection to the wall of the piston may not be a circular line, but more of the circle points (the boundary of the section closest to the center of the circular chamber) And a combination of a circular cross section (on the boundary of the cross section farthest from the center of the circular chamber), and wherein the point and the cross-sectional portion have different sizes and also have different shapes. This situation may not be a major hazard because the connection to the wall of the chamber only needs to be intermeshing in order to create the motion of the chamber. Due to the size of the circumference, the contact is self-sealing (closest In the center of the chamber around the central axis) becomes intermeshing (farthest from the center of the chamber around the central axis) and becomes a sealed contact and a salvage contact between the sealed contact and the inductive contact A combination of all kinds. This affects the amount of friction between the piston and the chamber wall, and thus affects the direction in which relative motion may occur. In the configuration taken here, the direction should be the direction of the shape of the chamber, which is my The configuration of the trial (Figure 27A to Figure 27C). To reduce friction, the ball piston is rotatable about its piston rod and thus rotates about the central axis of the piston rod, the central axis being parallel to the axis extending through the center point of the chamber, perpendicular to the cross-sectional portion of the chamber. The actuator piston and chamber geometry takes into account the configuration of the piston and piston chamber: the circular conical tube contains a constant surface 159900.doc -68 · 201235565 Product, variable volume, flexible actuator, in contact with the wall The piston beta chamber is constructed as a Fermi tube. The exact calculation of volume and contact area is attached to the rough annotated Maple worksheet. Indicates the actuator force distribution. To illustrate the importance of geometry, the pattern is somewhat extreme. 1 · Fermi tube structure The center base circle (the chamber is "bent" around it) is represented by the parameter "unit speed", which has a radius and the origin in the sigma of the determined brother

(〇,〇,〇) See the blue circle in Figure 32G, Figure 3211, etc. The vector function of the base circle is standard: (1.1) y(u) = R · (cos(u/R), sin(u/R), 0) ... With this base circle, we will only consider the piston and the cavity The angle of rotation of the chamber wall contact we[0, Z]. The child ue[0,L]' is in the circle of D human boundaries in each orthogonal plane of the base circle (see Fig. 2 and Fig. 2), which will eventually depict the entire chamber and therefore also the piston. Has the other part of the chamber wall contact. These circles have a radius P(8)^ and other semi-controls depending on the base circle parameters; and they all have their respective centers on the base circle. The circle of the 歹J is drawn from the base circle, and the tube is taken out from the tube. The false twist function is linear in w such that the corresponding Fermi surface can be referred to as a conical shape' as shown in Figures 32F, 32G and 32H. The conical effect (which will ultimately drive the piston inside the chamber) can be obtained by the "eight: octupon function. The linear radial function is therefore as follows (this function applies to the specific values of α and β in the part and In this report, it is used to say 159900.doc -69- 201235565): 2 Piston and chamber (1 · 2) p(u) = au + β Parameterization of radius function household (8) around the base circle The surface of the Fermi tube is then given by the following vector function: 0.3) γ(«, ν)= Y(w)+p(M)(c〇s(v)-ei(M)+sin(v). E2(M)), where ei(u) and e/乂) are orthogonal unit vectors that straddle the orthogonal plane of the base circle (as shown): (1.4) e, (u) = (cos(u /R), sin(u/i?),〇) e2 (m) = (0,0,1) 'The parameterized Fermi tube solid with the radius function ^^(1) also "curved" around the base circle For: (1.5) f(w,V, w) = γ(+ w · p(w). (cos(v). e, (M)+ Sin(v). e2(M)). The surface is simply obtained from the corresponding solid by setting W = 1: 〇 · 6) γ (Μ, ν) = 〒 (Μ, ν, ΐ). The volume of the Fermi tube solid (corresponding to the rotation angle interval [〇L]) is determined by the following equation: (1.7) v〇1=L〇LL5(u,v,w>^, where the Jacobian function (jacobi The functi〇n) integrand is given by the partial derivative of ? as follows: Π.8) J(w,v,)=|(puxpv)·self|. The area of the surface of the Fermi tube (corresponding to the rotation angle interval [0, L]) is: (1·9) Area= £ ί/ν , where 'the Jacobian function integrand is now: 159900.doc -70- 201235565 (m) */(m,v)=|«|.

The Maple output attachment contains a ten-digit example of the total total area and total volume calculated from the selected values of the constants defining the geometry in the particular case considered and displayed. This situation is completely general and can be evaluated numerically by any other choice of geometric description values. The total area and total volume include values from the end caps that we now discuss. Piston and chamber 3 2. End caps We assume that the end caps are spherical. This situation is not absolutely necessary. What we need is a circular fit between the two ends to the tube portion of the chamber and a handle on the enclosed volume and total surface area of the piston. Both of these cases are most easily obtained by ball end caps for current model considerations, see Figures 32D and 32E. In fact, the 'spherical assumption is not completely realistic: given a very good elastic piston material 'the piston will always have a constant average curvature' regardless of whether it does not have a wall contact, (d), in this setting, it will (prone) Have the same spherical radius at both ends. This condition is not implemented in the current discussion. By correcting the (four) domain of the flexible piston material, it is possible to estimate the actual shape of the end cap 'the volume it encloses, and (iv) the internal pressure inside the piston at each moment. The spherical cap has a simple expression for its area and the "enclosed" volume (that is, the volume that is cut from the solid sphere when the cover is cut by a flat cut in winter). "There will be a spherical cover here." Assume to continue under 159900.doc -71 - 201235565. The area of the cover with the degree a and the base circle radius β (see Fig. 3) is: (2.1) A(h, ρ)=π·{α2 +h2) ° Cover with a radius 基 and a base circle radius α The volume is (2*2) V(h, p) = ^.jt-h-(3a2 +h2) ° 6 ' For completeness, we also show the virtual spheres taken by the respective end caps (respectively, M = 0 and the radius of "=£": (2·3) K«)=/?(«)· . In the tube geometry, the values of ^ and /; are determined only by the radius function at the W-end of M=0 and W=L, respectively, and their derivatives ^;...; the radius of the base circle has no effect! (2.4) a = p(u) h = P(u)· (J^ + {p'(u)f -p'(ufj therefore 'the end cap area and volume are simply by the assumption that the spherical hypothesis is true p And the respective values of 〆 determine. 4 Piston and 4 chambers are supported or attached to the shaft (for example, the rigid version of the base circle) because of the end cap, therefore, the attachment and the force between the shaft and the piston Inductive coupling will change the spherical geometry of the end of the piston. Gives an accurate description of the attachment and piston material 'The geometry of the resulting deformed end cap may be estimated. This will not be considered here. 3. Mobile piston and shaft attachment most The area of the precise contact between the piston and the chamber wall and the geometry of the shape of the piston. Through this contact, the driving force to the piston is activated. In the current model, the wall contact is surrounded by a given base circle. The Fermi tube is modeled; the volume (pressure) and the area (force at the wall) are calculated accordingly. The actual sliding force along the wall of the chamber is shown by the chamber shown in Figure 32Η to Figure 32Μ (inclusive). The geometrical symmetry of the total gray force on the segment (around the direction of the axis) is double projected Therefore, the resulting sliding force is proportional to the longitudinal length of the section and the internal pressure of the piston; pressure = force per area. • depends on the friction model (friction between the chamber wall and the piston) and depends on In the material properties of the piston (elasticity, etc.), the resulting force will drive the section in the longitudinal direction. Since the force at each section is proportional to the longitudinal length of the section and therefore from the base circle The distance of the center is proportional and therefore will tend to (first order and again heavily dependent on the entity descriptors mentioned above) to cause the resulting motion of the free piston surface to become a rotation around the center of the base circle. If the piston is attached to the chamber The axis along the axis of the base circle can also apply the force described to pull or push the attached circular shaft to make a circular motion about the center of the base circle. 19640 Overview of the invention ΕΡ 1 179140Β1 A piston (Fig. 105A to Fig. 105A of the present patent application) is shown on 5 to 5 inches (inclusive) comprising six support members 43' which are rotatably secured to the piston rod 45 about an axis 44. These The other ends of the brace members are mounted on a watertight flexible sheet between the flexible domes. The flexible loop is sealingly connected to the wall of the piston chamber assembly, wherein the chamber is Conical. The cymbal ring is pressed by the support members to the wall by 159900.doc • 73· 201235565, which is due to the pulling of a plurality of springs which are assembled on the piston rod at one side, And at the other end, the support members are mounted on the support member in the vicinity of the cymbal ring to extend the support members from the piston rod to the wall of the chamber. In addition, the volute spring (which is placed in a watertight sheet) The center of the upper circumference is on the central axis of the chamber and presses the cymbal ring to the wall of the chamber, wherein the support members do not directly support the 〇$ ring. This is the main solution as a solution principle. An unresolved aspect of this configuration is that the water-impermeable flexible sheet is free of L-hanging and that it can push the piston inwardly when pressurized by the fluid beneath the sheet (changing its shape X Figure 5G, Figure 5H). Another aspect that has not yet fully developed is the proper assembly of the Ο-shaped ring to the support members. And, suitably fitting the support members to a member that holds the cymbal ring in position between the support members and the assembly point of the cymbal ring. There may be two preferred solutions for avoiding changes in the shape of the watertight flexible sheet. Other solutions are possible but not yet shown. One solution is that the watertight flexible sheet can be assembled to the end of the piston rod, for example by a screw. Alternatively, the solution may be to vulcanize the sheet only on the piston rod and (iv). This securing of the sheet to the piston rod substantially reduces (but does not avoid) the change in shape of the sheet upon application of pressure. Moreover, in addition, the shape change of the sheet can be additionally reduced by the commercially available reinforcement of the sheet. First, the sheet may need to have a production size that has a circumference that is approximately the circumference of the chamber wall at the second longitudinal position. In order to seal the foil to the wall of the chamber, when the piston is moved to the longitudinal position, in the example of p, when the piston is first moved from the second dimension 159900.doc -74· 201235565 to the -first longitudinal When in position, the sheet may need to be expanded. The pull springs on the sub-building members can be pulled slightly more than the pull power in the water-impermeable sheet, and when the piston is not in the second longitudinal position, it is pulled back to its production size. The third force can pull the stirrup ring from the wall, and the situation occurs when the sheet is bent upwardly when pressurized. $ substantially prevents the situation, the reinforcement may comprise a concentric reinforcement 'the equivalent reinforcement may be made of a flexible material in its length, or if it is made of a non-flexible material as a spiral, then #塞# The center axis is centered. Other firmware possibilities are possible but not shown. The use of such reinforcing patterns means that the sheet can be widened on the buckle, in a transverse plane, perpendicular to the central axis of the chamber, and only widened a little in the direction of the central axis of the chamber. The reinforcing layer of the sheet is preferably positioned to be closest to the high pressure side of the sheet' and the other layer without the reinforcement may be vulcanized on the first layer mentioned. The production thickness of each layer may be so thick that the thickness reduced at the first longitudinal position may be sufficient for the piston to function properly for a long period of time. The (10) ring may also have a production size wherein its outer circumference is approximately the size of the circumference of the chamber at the second longitudinal position. Here, the production diameter of the stirrup ring should also be large enough to compensate for the reduction in thickness that occurs as the piston moves to the first longitudinal position. A water impermeable sheet can be vulcanized on/in the crucible ring to achieve a proper seal when the beryllium ring is sealingly attached to the wall of the chamber. A lying spring can be vulcanized at the end of the stirrup ring, the support members, and on the water impermeable sheet. This keeps everything together. In the case where the watertight flexible sheet has been assembled to the piston rod, the widening of the sheet 159900.doc -75· 201235565 can be substantially by the pulling force of the spring on the supporting members and by the Caused by the rotational force of the support member. The impervious flexible sheet, the internal pulling force of the 〇-shaped ring and the urging force of the lying volute spring and the urging force of the supporting members may have a force balance with the reaction force of the wall to the O-ring. The jaw ring is always pressed against the wall of the chamber to achieve a sealed connection. The lying volute spring shown in the prior art diagram will likely not give enough force for the job, and the lying snail spring should primarily have the 〇-shaped ring at the end of the support members. Keep in place. The fact is that the 'elastic metal rod allows the (10) ring to be better held in place. The two ends τ of the oscillating rod slide between two adjacent struts, and the two rods are slidable along each other via a support member. 19650 Summary of the Invention 1 179 14G B1 discloses an elastically deformable member reinforced by its components, which are rotatably affixed to a common component, such as a piston rod (where the piston can be elastically deformable) In the case of production). The elastically deformable members may have a cross section that is a trapezoidal cross section. When moving from the -first longitudinal position to the second longitudinal position in the chamber, wherein the wall of the chamber is parallel to the central axis of the chamber at a second longitudinal position, the trapezoid becomes more and more It tends to a rectangle. The stiffeners are rotatable to an angle wherein the stiffeners are generally positioned about the central axis as the 竽, 八八丁田忒 pistons are moved from a first longitudinal position to a second longitudinal position. Parallel to a foam may expand from a second longitudinal position of a larger shape at a longitudinal position of the elongate chamber to a first. However, the expansion can be performed in a manner different from the expansion of an inflated 159900.doc -76 - 201235565 type of sifter. The inflatable container has a production wall of a flexible wall so that the circumference is substantially in the first The circumference of the wall of the chamber at the two longitudinal positions (see, for example, EP 1 384 004 B1). The thickness of the wall of the container can be reduced ("balloon effect") when it is moved to a first longitudinal position and it may need to be meshingly coupled to the wall of the chamber. A motor wherein one of the pumps has a piston that is meshably and/or sealingly movable in a chamber, wherein: - the elastically deformable member is made of a polyurethane foam, - PU foam The body comprises a polyurethane foam and a polyurethane foam. The polyaminophthalate foam contains a majority of the polyaminophthalate memory foam and a small portion of the polyaminophthalate foam. An elastically deformable member can be made of a foam. In particular, for harsh environments (e.g., moving pistons in the chamber of a pump), a good feature may be a polyamine phthalate foam. The increase in size of a foam moving from a second longitudinal position to a first longitudinal position can be performed by amplifying the foamed cells (ceU) in which the fluid is located. In the chamber 0, when the foam cells are open, that is, when the interior of the foam cells can communicate with the atmosphere around the foam, it is possible in the chamber. Therefore, at a second longitudinal position, the 'foam needs to be under pressure so as to be able to reduce the size of the open-developed cells in the foam' and at a second longitudinal position, the foam needs to be under pressure' In order to be able to expand itself when moving to a first longitudinal position. The foam (and therefore the material that opens the wall of the cell) can therefore be extremely flexible. 159900.doc •77- 201235565 Such a material may be a polyamino phthalate ("Pu") foaming body and a very flexible type of Pu foam may be a so-called memory hair. “,,: However, the very flexible material itself may not be able to withstand the high pressure, but the extreme pressure of the party is the ability of the piston. In order to get better resistance to pressure, a kind of interlayer can be manufactured. The interlayer may be made, for example, of two layers of pu, one of which is made of a pu foam which is inflexible compared to a memory foam, and a layer of pu memory foam which can be glued to If there is no space for the layer and/or it may be difficult to manufacture - a sandwich, a mixture of a PU foam and a Pu memory foam may be a solution. The percentage of a common PU foam may be a small fraction of the mixture σ a motor 'where the pump has the piston, wherein the support members are bendable, - the support members have a predetermined bending force, - the members are locked in a holder, the holder Attached to the piston bore, and rotatable about the end of the stiffener in the retainer, the tip being under the pressure of an adjustable member - the longer end of the stiffener having an increased thickness. Memory foaming When the material is released, after it has been pressed, at the normal working temperature (such as quickly regaining its original size. At a lower temperature such as the freezing point, the flower f is longer ^ (may be too long) Time) in order to comply with the requirements of meshing and/or sealingly connecting the cavity to the wall. The stiffeners may have to be made of a spring material so that the piston is from a second longitudinal position. The reinforcing members may press the foam outward when moving to a first longitudinal position. A predetermined bending force may be necessary, and the bending may be performed by, for example, the end of the reinforcing member. a length that is much shorter than the total length of the stiffener, whereby the angle can lock the end of the stiffener in the retainer, the retainer being connectable to the piston rod. The predetermined bending force can be achieved by Obtaining a component that presses a short end of the stiffener, the adjustable component being a rotatable component lockable in a position. When moving from a first longitudinal position to a second longitudinal position The foam may be pressed inwardly by the wall of the chamber, and the foam may need to have a shape such that no lateral force exists to adhere to the cast foam of the reinforcing members (which may It is preferably made of polyamine phthalate which has become non-tacky, so that its function is lost. In order to prevent the reinforcement from becoming non-sticky, another measure is to increase the thickness of the long end of the special reinforcement. The long end is close to where pressure is obtained from the fluid below the piston in the chamber. A motor wherein the pump has the piston, wherein the flexible, water-impermeable layer has an unstressed production size, the production size Having a circumference 'the circumference is substantially the same as the circumference of the wall of the chamber at a second longitudinal position. The foam piston having the open development bubble is meshingly coupled to the wall of the chamber. To make it sealable Attached to the chamber wall, it is necessary to add a water impermeable layer such as a natural rubber layer. This rubber layer may need to follow the same circumferential extent as the inflated capacitive piston. Therefore, the size of the layer may be 159900.doc -79-201235565 to have a circumference of the circumference of the chamber wall which is unstressed at a second longitudinal position, therefore, the assembly needs to be foamed under pressure. Around the body. When moving from a second longitudinal position to a first longitudinal position, the foam and thus the reinforcing members need to press the layer into a shape (trapezoidal shape) when the foam is at a first longitudinal position. Upon returning to the second longitudinal position, the layer can be collapsed into a generally rectangular shape of the foam at a second longitudinal position. This layer needs to be flexible. The water impermeable layer may need to be in fluid communication with the uncompressed side of the piston to cause the open development bubble when moving from the second longitudinal position to the first longitudinal position and from the first longitudinal position to the second longitudinal position Cells can communicate ("breath"). 19660 Overview of the Invention 179140 B1 shows an inflatable container live 384 004 B1 showing that this piston type should have an unstressed production size, wherein its circumference at a second longitudinal position of an elongated chamber should have substantially the same cavity The circumference of the circumference of the chamber is the same to avoid jamming of the piston when moving from the first longitudinal position to the second longitudinal position. The piston expands when moving from the -second longitudinal position to the -first longitudinal position. Μ i 384 _ B1 shows that the reinforcement used for this type of behavior can be a layer 'where the reinforcing strips are tiled side by side in an unstressed production model, and the strips connect the two end portions' in the two end portions One of them is mounted on the piston rod, and the other _slider__ rubber of the piston rod is directly vulcanized at one end. The reinforcement layer is (4) and the reinforcement layer is protected by a further layer of layers having a reinforcement strip. The two layers are at the end portions of each other, and there may be another additional on top of the two layers: 159900.doc 201235565 The function of the second layer is to prevent the reinforcing strips from "stretching" the outer layer, This makes it impossible to have a sealed contact with the wall of the chamber, however, for meshing contact, this is just the case. Having a second layer on top of the reinforcement layer works well in practice and has been shown to be possible from 0i7 in the chamber of the pump (see 1962〇) where the force applied to the piston rod is constant (see 1962〇) The second longitudinal position) is expanded by approximately 33% to 059 mm (first longitudinal position). The two reinforcing layers that overlap each other at a very small angle are placed one on top of the other and the top of the "second" layer mentioned above makes the container stronger, but may swell much less than 330%. The rubber type of the layer rubber may vary, but should be compatible so that the rubbers can be vulcanized on each other without being lost from each other under normal operating conditions. It has been observed that when the ellipsoid-shaped container-type piston is fully expanded into its spherical shape, there is a complete chance of breakage, why is it possible to change the design so that by keeping other variables (such as 'chamber design) unchanged, The length of the piston that is not subjected to the stress production model increases, and therefore, may not reach the shape of the sphere and does not expand to 330%, and is only a rounded body that almost becomes a sphere shape, which makes the piston reliable, even with reinforcement This is still the case for one of the layers. The shape of the container in the unstressed production state may also be such that the wall of the container is not parallel to the central axis but parallel to the wall of the chamber because the walls of the chamber are not parallel at a second longitudinal position. On the central axis. In this unstressed state, only the wall of the chamber is detached from the wall of the container. 19660-1 Update to the Function of the Actuator Piston 159900.doc • 81 - 201235565 The actuator piston includes a container containing a wall around a cavity that can be inflated and fluidized Pressurizing, and/or arranging 3/packages, the sump moving from a second longitudinal position of the chamber to a first longitudinal position in a chamber upon pressurization, the chamber having a plurality of sections The sections have different cross-sectional areas and different circumferential lengths at the first longitudinal position and the second longitudinal position and at least substantially continuous at intermediate longitudinal positions between the first longitudinal position and the second longitudinal position The cross-sectional area and the circumferential length at the second longitudinal position are smaller than the cross-sectional area and the circumferential length at the first longitudinal position due to the wall of the container of the actuator piston Sliding on the wall of the chamber. This may also be the case for chambers having cross-sections having different cross-sectional areas and equal circumferential lengths at the first and second longitudinal positions and at the intermediate, intermediate, and longitudinal positions. The wall of the piston may preferably have a symmetrical shape about the transverse central axis in the longitudinal direction of the chamber between the end caps (movable and immovable), wherein each symmetrical half has a plurality of longitudinal sections, The longitudinal sections have different cross-sectional areas and different circumferential lengths, at least substantially continuous different cross-sectional areas and circumferential lengths at intermediate intermediate positions between the transverse central axis and the end cap. This situation can also be the case when the lengths of the circumferences are equal. The wall of the container of the actuator piston is provided with a reinforcing layer to smooth the outer portion of the wall and, when pressurized from the cavity of the container, is preferably convexly shaped. This situation provides a small contact area with the wall of the chamber. The expansion force of the wall of the container is directed in a direction perpendicular to the surface of the wall of the chamber. The expansion force may be much greater than the pressure inside the cavity of the actuator piston, depending on the t/R ratio (R = transverse radius of the longitudinal section, t = actuator piston The thickness of the wall is 'particularly at t/R<<<>. When the actuator piston is in the wall of a chamber that has a positive angle to the central axis of the chamber in a direction from the second longitudinal position to the first longitudinal position, because it is closest to the chamber There will be no reaction force at the chamber position of the first longitudinal position and at the final position closest to the first longitudinal position portion of the contact area (wall chamber_container), thus, from the chamber The asymmetry of the reaction force of the wall of the chamber will occur, and as a result the wall of the container will be bent towards the wall of the chamber at such locations until the reaction force of the wall is equal to the expansion force of the wall of the container, The wall of the container of the actuator piston flips over the wall of the chamber. This rollover increases the contact height of the wall of the container with the contact area of the wall of the chamber, and the frictional force in the crucible is thus increased. The expansion of the wall of the container of the actuator piston causes a small pressure drop in the (four) portion of the weir, which reduces the expansion force of the wall of the piston when the volume of the enclosed space remains constant Therefore, the friction is also reduced. Movement of the actuator piston toward a first longitudinal position may occur (slide). This reduces the contact height because the portion of the wall of the container that is closest to a second longitudinal position reduces its circumference, and thus the portion of the contact area that is closest to a second longitudinal position also reduces its circumference. Due to the lubrication between the wall of the chamber and the wall of the container, the propulsive force is still greater than the frictional forces, and the actuator piston will slide to the new chamber position closest to a longitudinal position until The asymmetry of the force occurs again. The cycle can then start again. 159900.doc -83 · 201235565 It is possible to increase (= roll over) the contact height in the longitudinal section of the meshing wall of the container and the wall of the chamber, thereby making the height in the immediately adjacent portion of the existing height greater, This is the main reason for the behavior of the actuator piston. The components for this action are: • a bendable reinforcement layer 'where the reinforcement is substantially parallel to the central axis of the chamber in the longitudinal direction, • almost no reinforcement in the transverse direction, • the container is laterally symmetrical a symmetrical wall around the axis, the wall of the container will be bent outwardly from the final circumference of the contact area closest to a first longitudinal position between the wall of the chamber and the wall of the container under internal pressure The wall of the chamber thereby increasing the surface area of contact, and in the vicinity of a second longitudinal position, the wall of the container will thereafter be retracted from the wall of the chamber under the bend, after which the wall of the container The surface area of contact between the walls of the chamber is again reduced." When there may not be enough internal pressure to press the wall of the container of the actuator piston against the wall of the chamber, the actuator piston will stop facing the first The longitudinal position operates such that a circumferential leak occurs. This can occur, for example, in the case of a chamber as shown in section 19620 of the present patent application, when a common boundary of the overpressure is present in the chamber, which was previously disclosed in the description as " Suspend behavior." See the following behavior. When the pressure inside the cavity of the actuator piston is 159900.doc -84 - 201235565, the force of the actuator piston is gradually moved, and the movable cover of the actuating piston is moved. Positioning is closest to the -first-vertical position. The reason may be that 'in addition to the expansion of the wall of the container due to internal pressure, the expansion of the wall of the actuator piston when moving from the second longitudinal position to the first longitudinal position is additionally forced to be closest to The contact area of the wall of the actuator piston in the first longitudinal position with the wall of the chamber, and thus the frictional force. In the case where the non-movable cover is positioned closest to the first longitudinal position, so in the "front" of the container in the direction of the Lu (four), the movement is smooth even if the pressure is low. The original® may be such that the additional force of the wall of the container increases the expansion force and does not exceed the friction. Therefore: the wall of the piston is made of a flexible reinforcing material which, when pressurized by a pressure source via the enclosed space, causes a smooth outer surface of the piston wall, and thus, the piston wall and the Providing a height of the circumferential contact area in the longitudinal section of the piston between the walls of the chamber, the height being changed during movement of the piston at an intermediate longitudinal position between the second longitudinal position and the first longitudinal position Size This sliding can be performed on several different cross-sectional areas of the wall of the actuator piston and the wall of the chamber. This is possible because the walls of the container are convexly shaped and flexible while the several different regions are continuously positioned relative to one another. 207 SUMMARY OF THE INVENTION In general, a new design for a combination of a chamber and a piston, for example, of a pump, is generally sufficient to apply sufficient force to operate the pump during the entire pumping operation. 159900.doc •85- 201235565 Low to make the user feel comfortable, feel the length of one stroke is appropriate, especially for women and young people ^ have the most ", can not be long, and feel pump, 乂" ° components and almost free of maintenance The invention relates to a combination of a piston and a chamber, wherein: the chamber defines an elongated chamber having a 'longitudinal axis, the chamber being at its first + ganj$ longitudinal position Having its first cross-sectional area and having its second cross-sectional area = 95% or less of the first cross-sectional area at its first longitudinal position, the cross-section of the chamber is changed - at least substantially continuous between the longitudinal position and the second longitudinal position, the piston being adapted to adapt itself to the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber. In the current context, the section is more Preferably, it is taken perpendicular to the longitudinal axis. Moreover, due to the fact that the piston can be sealed against the inner wall of the chamber during movement between the first longitudinal position and the second longitudinal position, the change in the cross-section of the chamber is preferred. At least on the real treasure, that is, there is no sudden change in the longitudinal section of the inner wall. In the present context, the cross-sectional area of the chamber is the cross-sectional area of the internal space in the selected section. Therefore, as will be As is apparent in the text, the fact that the area of the internal chamber changes results in the possibility of making the combination practically suitable for several situations. In a preferred embodiment, the combination acts as a pump by which the piston Movement will compress the air and output this compressed air via a valve to, for example, a dry center. The area of the piston and the pressure on the other side of the valve will determine the force required to provide air flow through the valve. , the required six recognition and '^ knife adjustment 159900.doc • 86 - 201235565 can occur. Moreover, the volume of air supplied will depend on the area of the piston. However, in order to compress air The first translation of the piston will be relatively easy (relatively low pressure) whereby air compression can be performed over a large area. Therefore, in general, it can be provided at a given pressure during a single stroke of a certain length. a relatively large amount of air. Naturally, the actual reduction in area may depend on the intended use of the combination and the force described. Preferably, the first cross-sectional area is 95% to 15% of the first cross-sectional area,

Such as 95% to 70%. In some cases, the second cross-sectional area is about 50% of the first cross-sectional area. This combination can be implemented using several different techniques. These techniques are further described with respect to subsequent aspects of the invention. One such technique is a technique in which the piston comprises: - a plurality of at least substantially rigid ± negatively rigid support members rotatably secured to a common component: the elastically deformable member The support members (4) are sealed against the inner wall of the chamber, and supported by a crucible or the like. The p piece can be attached to the buckle with respect to the longitudinal axis. Rotate between. Used in a ::: shape, the common component can be attached to the handle for the operator to place the cutting member in a direction relatively far from the handle in the chamber

The intermediate extension β A is preferably a longitudinal axis. The support member is rotatable so as to be at least substantially parallel and the combination may further comprise an inner wall bias against the chamber 159900.doc • 87. 201235565 The component of the special support member is another technique Wherein the piston comprises an elastically deformable container comprising a deformable material. In that case, the deformable material may be a fluid or a mixture of fluids such as water, steam and/or gas or foam. σ Also, in a cross section extending through the longitudinal direction, the container may have a first shape in a first longitudinal direction and a second shape in a second longitudinal direction. The first shape is different from the second shape. Thus, at least a portion of the deformable material can be compressible, and wherein the first shape has an area greater than the area of the second shape. Alternatively, the deformable material can be at least substantially incompressible. The piston can include a containment space in communication with the deformable container, the enclosed space having a variable volume. The volume can be by an operator: Variable 'and the volume may comprise a spring biased plunger. Yet another technique is that the first cross-sectional shape differs from the second cross-sectional shape in that the change in the cross-sectional shape of the chamber is at least substantially continuous between the first longitudinal position and the second longitudinal position. In one case, the first cross-sectional area may be at least 5% larger than the second cut-off product, preferably at least 10% (such as at least 2%), preferably at least (such as at least 4%), Preferably at least 5% (such as at least 6%), preferably at least 70% (such as at least 80%, such as at least 9%). Less and 'the first cross-sectional shape may be at least substantially circular, and wherein the second cross-sectional shape is an elongated shape having a first size (such as an elliptical circle) the first-sized system and the first The size is at least 2 159900.doc -88 - 201235565 times (such as at least 3 times), preferably at least 4 times the size of the angle. Further 'the first cross-sectional shape may be at least substantially circular, and wherein the second cross section The shape comprises two or more at least substantially elongated (such as convex) portions. And 'in the cross section at the first longitudinal position, the first circumference of the chamber may be the second longitudinal direction of the chamber 8〇% to 120% (such as 85% to 115%) of the second circumference in the cross section, preferably 9〇% to 11〇% (such as 95% to 105%), preferably 98% to 1〇2 Preferably, the first circumference is at least substantially identical to the second circumference. An optional or additional technique is the following, wherein the piston comprises: 'an elastically deformable material adapted to Adapting the first longitudinal position of the chamber to the second longitudinal position to adapt itself to the section of the chamber And a helical plate spring having a central axis at least substantially along the longitudinal axis. The spring is positioned adjacent to the elastically deformable material to support the elastically deformable material in a longitudinal direction. In that case, the piston Can go further, red meeting / fr hot ► aunt...

The spring rotates with the interface between the elastically deformable material.

>3^ rq u 'The present invention relates to the combination of a piston and a chamber in a second aspect of the body 'where: 159900.doc • 89 - 201235565 The S-chamber defines an elongated chamber having a longitudinal axis, The chamber has its _ cross-sectional area at its first longitudinal position and a second cross-sectional area at the 'longitudinal position, the first cross-sectional area being larger than the second cross-sectional area' The change is at least substantially continuous between the first longitudinal position and the second longitudinal position, the piston being adapted to adapt itself to the cavity when moving from the first longitudinal position to the second longitudinal position of the chamber A section of the chamber, the piston comprising: - a plurality of at least substantially rigid branch members rotatably secured to a common component, 'elastically deformable members supported by the support members for abutting The inner wall of the chamber is sealed and the support members are at 10 relative to the longitudinal axis. With 40. Rotate between. Preferably, the support members are rotatable to be at least substantially parallel to the longitudinal axis. Thus, the manner in which the piston can accommodate different areas and/or shapes is as follows, wherein the piston includes a plurality of rotatably securing members that hold a sealing member. A preferred embodiment is the embodiment in which the piston has an umbrella-like overall shape. Preferably, the common component is attached to the handle for use by an operator, such as when the combination acts as a pump, and wherein the support members extend in the chamber in a direction relatively away from the handle. This has the advantage that by forcing the handle into the chamber to increase the pressure, the support members and sealing members are simply pressed against the walls of the chamber, thereby increasing the seal. 159900.doc •90- 201235565 In order to ensure a seal after one stroke, the receiver is biased by the chamber to the components of the material. w is used in the third aspect, the present invention, wherein: the combination of the lunar system and the piston and the chamber defines an elongated chamber having a longitudinal axis, the chamber being at its first The longitudinal position has its first face area and has a 篦-cut product ^ ^ m ^ at its first longitudinal position, the first cross-sectional area: the first cross-sectional area, the cross-section of the chamber The change is at least substantially continuous with the second longitudinal position, the piston being adapted to adapt itself to the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber, The piston comprises an elastically deformable container comprising a deformable material. Thus, by providing an elastically deformable container, a change in area and/or shape can be provided. Naturally, the container should be sufficiently secured to the piston to conform to the remainder of the piston as it moves within the chamber. The deformable material can be a fluid or a mixture of fluids such as water, steam and/or gas or foam. The material or a portion thereof may be compressible, such as a gas or a mixture of water and gas, or it may be at least substantially incompressible. When the wearing area changes, the volume of the container can be changed. Thus, the container may have a first shape ' in a first longitudinal direction and a second shape in a second longitudinal direction, the first shape being different from the second shape. In one case, the deformable material to 159900.doc • 91 - 201235565 is less compressible and the first shape has an area greater than the area of the second shape. In either case, the total volume of the container changes, whereby the fluid should be compressible. Alternatively or optionally, the piston can include a second enclosed space in communication with the deformable container, the enclosed space having a variable volume. In one way, when the deformable container changes volume, the enclosed space can draw fluid. The volume of the second container can be changed by the operator. In that way, the total pressure or maximum/minimum pressure of the container can be changed. Moreover, the second enclosed space may comprise a spring biased piston. A member for defining the volume of the enclosed space such that the pressure of the fluid in the enclosed space is related to the pressure of the fluid between the piston and the second longitudinal position of the container may be provided. In this way, the pressure of the deformable container can be varied to achieve a suitable seal. A simple way would be to adapt the boundary m to define the pressure in the enclosed space such that it is at least substantially (four) the pressure between the piston and the second longitudinal position of the container. In this case, a simple piston between the two forces can be provided (to avoid releasing any of the deformable containers). The use of this piston can define the relationship between the pressures (4) because the piston is translated therein. The circumference m can be tapered in the same manner as the main chamber of the combination. To withstand the friction and shape/size change of the chamber wall containing an elastically deformable material such as a fiber reinforcement, the container can The elastically deformable material comprises a reinforcing member, I59900.doc • 92· 201235565 in order to achieve and maintain a proper seal between the container and the chamber wall, preferably, the piston is translated from the first longitudinal position to the second The longitudinal position or translation from the second longitudinal position to the first longitudinal position during an internal (four) force (such as 'pressure generated by the fluid in the container) is higher than the most extreme pressure of the surrounding atmosphere. The invention relates to a combination of a piston and a chamber, wherein: σ 11 the chamber has an elongated chamber with a longitudinal axis, the chamber having its first position at its first longitudinal position a cross-sectional shape and an area and having a second cross-sectional shape and an area at a second longitudinal position thereof, the first-sectional shape being different from the second cross-sectional shape, the change in the cross-sectional shape of the chamber at the first-longitudinal position and the first The two longitudinal positions are at least substantially continuous, the piston being adapted to adapt itself to the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber. The pattern is based, for example, on the fact that the different shapes of the geometry have a varying relationship between their circumference and area. Moreover, the change in the two shapes can occur in a continuous manner such that the chamber can be in its longitudinal direction. The position has a cross-sectional shape and has a further cross-sectional shape at a second longitudinal position while maintaining a preferred smooth variation of the surface in the chamber. In the present context, the shape of a cross-section is its overall shape, regardless of its Size. Two circles have the same shape 'although one circle has a diameter different from the diameter of the other circle. 159900.doc •93- 201235565 Preferably, the first face The product is at least 5% larger than the second cross-sectional area, preferably at least 10% (such as at least 2%), preferably at least 3% (such as at least 4%), preferably at least 5% (such as at least 6〇). %), preferably at least (such as at least 80°/., such as at least 9〇%. In a preferred embodiment, the first cross-sectional shape is at least substantially circular, and wherein the second cross-sectional shape In the form of an elongated shape (such as an elliptical shape) having a first dimension, the first dimension is at least 2 times (such as at least 3 times), preferably at least 4 times the dimension of the first dimension. In a preferred embodiment, the first cross-sectional shape is at least substantially circular, and wherein the second cross-sectional shape comprises two or more at least substantially elongated (such as raised) portions. In the section at the longitudinal position, the first circumference of the chamber is 1 鸠 (such as 85% to!) of the second circumference of the section at the second longitudinal direction of the cavity. ! 5%), preferably 9% to i 1% (such as 95% to 105%) ‘preferably 98. /. By the time of 102%, I saw several advantages. When attempting to against a wall of a varying size, the seal is due to the fact that the sealing material should provide sufficient sealing and change its size. The problem may arise. If in the preferred embodiment the situation is that the circumference changes only to a small extent, the seal can be more easily controlled. Preferably, the first circumference and the second circumference are at least substantially the same such that the sealing material only bends and does not stretch to any significant extent. Alternatively, it may be desirable for the circumference to vary slightly as the sealing material (e.g., curved) will have one side compressed and the other side stretched when bent or deformed. Total. Accordingly, it is desirable to provide a desired shape having a circumference at least close to the circumference of the sealing material that will automatically "select". 159900.doc -94· 201235565 One type of piston, which can be used in a combination of this type, is a piston comprising: - a plurality of at least substantially rigid support members rotatably secured to a common A component, an elastically deformable member supported by the support members for sealing against an inner wall of the chamber. Another type of piston is a piston comprising an elastically deformable container comprising a deformable material. Another aspect of the invention relates to a combination of a piston and a chamber, wherein: the chamber has an elongated chamber having a longitudinal axis, the chamber having its first position at its first longitudinal position a cross-sectional area and a second cross-sectional area at a second longitudinal position thereof, the first cross-sectional area being greater than the second cross-sectional area 'the change in the cross-section of the chamber between the first longitudinal position and the second longitudinal position At least substantially continuous, the piston includes: an elastically deformable material adapted to adapt itself to a cross-section of the chamber when moving from a first longitudinal position to a second longitudinal position of the chamber, and having at least substantially The spiral sheet spring along the central axis of the longitudinal axis is positioned adjacent to the elastically deformable material to support the elastically deformable material in the longitudinal direction. This solution solves the problem of providing only a large amount of elastic material as a potential problem material for the piston to be elastic. This will provide the problem of piston t deformation and lack of sealing due to the elasticity of the material under pressure increase. This problem is particularly problematic in the case where the size change required by 159900.doc -95- 201235565 is large. In the current aspect, the elastic material is supported by a spiral plate spring. The helical spring can be deployed and compressed to conform to the area of the chamber, while the flat structure of the material of the spring will ensure that the spring is not deformed by pressure. In order to, for example, increase the area of engagement between the spring and the deformable material, the piston may further comprise a plurality of flat support members between the elastically deformable material and the spring, the support members being along the spring Interfacial rotation with the elastically deformable material. Preferably, the support members are adapted to rotate from a first position to a first position, wherein in the first position the outer boundary thereof can be included in the first cross-sectional area, and wherein in the second position Its outer boundary may be included in the second cross-sectional area. Another aspect of the invention is the aspect associated with a combination of a piston and a chamber, wherein: the chamber defines an elongated chamber having a longitudinal axis, the piston being self-contained in the chamber A longitudinal position is moved to a second longitudinal position. a cavity to an elastically deformable inner wall having at least a portion of the inner cavity to the wall between the first longitudinal position and the second longitudinal position, » the cavity to the first longitudinal position of the piston at the first position Having its first cross-sectional area at its second longitudinal position and having a second cross-sectional area when the piston is at the position, the first _ cross-sectional area being greater than the second cross-sectional area, when the piston is at the first When the longitudinal position is moved between the longitudinal position and the second longitudinal position, the change in the cross-section of the chamber is at least substantially continuous between the first longitudinal position and the second longitudinal position of 159900.doc 201235565. Thus, instead of adapting the piston to a combination of changes in the wear of the chamber, the sample is directed to a chamber having an adaptability. Naturally, the piston can be made of a material that is at least substantially incompressible, or a combination can be made from an adapting chamber and an adapting piston, such as a piston according to the above aspect. Preferably, the piston has a shape in the cross section that tapers in a direction from the second longitudinal position along the longitudinal axis. A preferred way of providing an conditioned chamber is to have a chamber comprising: - an outer support structure enclosing the inner wall, and - a fluid defined by the outer support structure and the inner wall Space accommodation. In some ways, the choice of fluid or combination of fluids can help define the properties of the chamber, such as the seal between the wall and the piston, as well as the force required.

Where the moon is seen from the joint, the piston and the chamber can be fixed and the other is moving, or both can move. This has no effect on the function of the combined body. Naturally the 'current combination can be used for several purposes as it focuses primarily on providing a novel way of adapting the translation of the piston to the amount of force required/occupied. In fact, the area/shape of the cross-section can be varied along the length of the chamber to accommodate the combination to suit a particular purpose and/or force. One purpose is to provide a pump for women or adolescents, ie, still 159900.doc •97- 201235565 should be able to provide a pump of a certain pressure. In either case, the ergonomically modified pump' can be required by determining the force that the person can provide at this location of the piston and thereby providing a chamber having a suitable cross-sectional area/shape. Another use of the combination would be for a shock absorber where the area/shape would determine which translation would be required for a certain impact (force). Moreover, it can be provided that the amount of fluid introduced into the chamber will provide for different translation of the piston depending on the actual position of the piston prior to introduction of the fluid. In fact, the nature of the piston, the relative position of the first longitudinal position to the second longitudinal position, and the configuration of any valve connected to the chamber can provide different pressure characteristics and different forces to the pump, motor, actuator, shock absorber, and the like. characteristic. If the piston pump is a hand pump for tire inflation purposes, it may have PCT/DK96/00〇55 (including US part of the continuation of April 18, 1997), PCT/DK97/00223 and/or An integrated connector for a connector as disclosed in PCT/DK98/00507. These connectors can have any type of integrated pressure gauge. In a piston pump according to the present invention for use as, for example, a foot pump or a "car pump" for achieving inflation purposes, a dust gauge configuration can be integrated into the pump. Certain piston types (eg, piston types of Figures 4A-4F, 7A-7E, 7J, 12A-12C) can be combined with any type of chamber 0 certain mechanical pistons (eg (eg ) pistons shown in Figures 3A through 3C) and certain composite pistons (such as, for example, the pistons shown in Figures 6D-6F) and chambers having a constant circumferential length in the form of a convex shape (e.g., Figure 7L) The combination of the chambers shown therein can be a good combination. 159900.doc 201235565 The combination of a composite piston, such as the piston shown in Figures 9 through 2, can be used well with a convex form of the chamber, regardless of the possible change in circumferential length. The "umbrella" piston shown in this application has its own open side at one side where the pressure of the medium in the chamber loads the "umbrella" at the open side. The "Umbrella" is also very likely to be inverted. An inflatable piston having a skin containing a fiber structure that has been shown has an overpressure relative to the pressure in the chamber. However, it is also possible to have a pressure in the piston that is equal to or lower than the pressure in the chamber, and the fibers are therefore under pressure rather than under tension. The resulting shape can be different from the shape shown in the drawings. In either case, any load regulating members may have to be rotated differently and the fibers may have to be supported. For example, the load adjustment member shown in Figure 9D or Figure 12B can then be constructed such that movement of the piston of the member, for example by the elongation of the piston rod, gives a suction at the piston t such that the piston It is now on the other side of the hole in the • 13⁄4 piston rod. The change in the form of the piston is therefore different and a collapse can be obtained. This can reduce the life expectancy. With such embodiments, a reliable and inexpensive pump optimized for manual operation, such as a universal bicycle pump for women and adolescents, can be obtained. The shape of the walls (longitudinal section and/or cross section) of the pressurized chamber and/or the piston member of the pump shown are examples and may vary depending on pump design specifications. The invention can also be used with all types of pumps, such as multi-stage piston pumps, as well as dual-function pumps, piston pumps driven by motors, (for example) chambers only 159900.doc • 99-201235565 or piston moving pumps And the type of simultaneous movement of the chamber and piston. Any type of media can be pumped in the piston pump. These pumps can be used in all types of applications, for example in pneumatic and/or hydraulic applications. Moreover, the present invention is also applicable to pumps that are not manually operated. The reduction in applied force is a substantial reduction in the investment in the equipment and a substantial reduction in energy during operation. The chambers can be manufactured, for example, by injection molding from a wedge-shaped tube or the like. In a piston pump, a medium is drawn into a chamber which can thereafter be closed by a valve arrangement. The medium is compressed by movement of the chamber and/or the piston and a valve releases the compressed medium from the chamber. In a 0 actuator, a medium can be pressed into a chamber via a valve configuration and the piston and/or the chamber moved to initiate movement of an attached device. In the shock absorber, the chamber can be completely enclosed, wherein a compressible medium can be compressed by movement of the chamber and/or the piston. In the case where an incompressible medium is present inside the chamber, for example, the piston can be equipped with several small passages that give a dynamic friction that slows the movement. In addition, the present invention can also be used in propulsion applications in which a medium can be used to move a piston and/or chamber. The piston and/or chamber can be rotated about an axis (e.g., in a motor). The above combinations are suitable for all of the applications mentioned above. Accordingly, the present invention is also directed to a pump for pumping a fluid, comprising: a combination according to any of the above aspects, - for merging the piston from a position outside the chamber Component, 159900.doc • 100- 201235565 - connected to the chamber and containing a fluid inlet of one of the valve members and - connected to one of the fluid outlets of the chamber. In the present case, the engagement member can have an outer position and an inner position at which the piston is in its first longitudinal position, at which the piston is in its second longitudinal position. This type of pump is preferred when a galic fluid is desired. In another case, the engagement member can have an outer position and an inner position at which the piston is in its second longitudinal direction. In the position, the piston is in its first longitudinal position at the internal position. Pumps of this type are preferred when no substantial pressure is desired but only fluid delivery is desired. In the case where the pump is adapted to stand on the floor and the piston/engagement member compresses fluid (such as air) by being forced downward, the maximum force can be artificially provided to the piston/engagement member/handle The lowest position. Therefore, in the first case, this means providing the highest pressure here. In the second case, this simply means that the maximum area is seen at the lowest position and thereby _f to the maximum volume. However, due to the fact that a pressure that exceeds, for example, the pressure in the tire is required to open the valve of the tire, the minimum cross-sectional area not far before the lowest position of the engagement member may be desirable to cause the resulting pressure to open the valve and The larger cross-sectional area forces more fluid into the tire (see Figure 2b). Moreover, the present invention relates to a shock absorber comprising: - a combination according to any one of the combined body aspects, - a member for engaging a piston from a position outside the chamber, wherein the engaging member has an outer position And an internal position at which the 159900.doc • 101 · 201235565 plug is in its first longitudinal position, in which the piston is in its second longitudinal position. The shock absorber can further comprise a connection to The chamber also contains a fluid inlet for a component. Moreover, the shock absorber can include a fluid outlet connected to the chamber and including a member. The chamber and the piston preferably form a cavity comprising a fluid - at least substantially sealed, the fluid being compressed as the piston moves from the first longitudinal position to the second one-position position. Typically, the shock absorber will include means for biasing the piston toward the first longitudinal position. Finally, the invention also relates to an actuator comprising: - a combination according to any one of the combined body aspects, - a member for sliding the piston from a position outside the chamber, - for A member that introduces fluid into the chamber to displace the piston between the first longitudinal position and the second longitudinal position. The actuator can include a fluid inlet coupled to the chamber and including a valve member. Moreover, a fluid outlet σ 连接 can be provided that is coupled to the chamber and includes a valve member. Additionally, the actuator can include a member for biasing the piston toward the first longitudinal position or the second longitudinal position. The various embodiments described above are provided by way of illustration only and are not to be considered as limiting. It will be readily apparent to those skilled in the art that various modifications, changes and combinations of the elements of the present invention will be made without departing from the exemplary embodiments and applications described and described herein without departing from the invention. The true spirit and scope. All piston types' are in particular piston types of containers with elastically deformable walls that are sealingly connected to the chamber wall during their movement between longitudinal positions, meshingly or not connected to the chamber wall. Alternatively, it may be coupled to the chamber wall in a snug and sealing manner. In addition, there may be no engagement between the walls, it is possible that the walls are in contact with each other, and this may occur, for example, in the case where the container is moved from the first longitudinal position to the second longitudinal position in the chamber. . The type of connection between the walls (sealed and/or sprayed and/or contacted and/or unconnected) can be achieved by using the correct internal pressure inside the wall of the container: high pressure for sealing connection a lower pressure for galvanic connection and an atmosphere for a connectionless (production-sized container); 1. Therefore, a container having a confined space may be preferred because The enclosed space may be from the outside of the piston - the pressure of the inside of the position-controlled container is used for the spray-bonding connection - the thin wall of the container may have a reinforcement extending beyond the surface of the wall. The leakage can occur between the wall of the container and the wall of the chamber. 653 ASSEMBLY OF THE INVENTION In a first aspect, the invention relates to a piston and body, wherein: the container is manufactured to be elastically expandable and has no stress at its production size of 159900.doc 201235565 And its circumferential length in the undeformed state, substantially the circumferential length of the inner chamber wall of the container at the second longitudinal position. In the present context, the section is preferably taken perpendicular to the transverse direction of the longitudinal axis. Preferably, the second cross-sectional area is from 98% to 5% of the first cross-sectional area, such as from 95% to 70%. In some cases, the second cross-sectional area is about 50% of the first cross-sectional area. This combination can be implemented using several different techniques. These techniques are further described with respect to subsequent aspects of the invention. One such technique is the technique wherein the piston comprises a container comprising a deformable material. In such cases, the deformable material may be a fluid or a mixture of fluids such as water, steam and/or gas or foam. The material or a portion thereof may be compressible, such as a gas or a mixture of water and gas, or it may be at least substantially incompressible. The deformable material can also be a spring operated device such as a spring. Thus, the container can be adjustable to provide a seal to the walls of the chamber having different cross-sectional areas and different circumferential dimensions. This can be achieved by selecting the production size of the piston (no stress, no deformation) to be approximately equal to the circumferential length of the smallest cross-sectional area of the section of the chamber, and expanding it when moving to a longitudinal position having a larger circumferential length. And it is achieved by shrinking it when moving in the opposite direction. Moreover, this can be achieved by providing a member for retaining a certain sealing force from the piston on the wall of the chamber: H is maintained at a certain internal pressure of the piston 159900.doc -104 - 201235565 ( The internal pressure can be kept constant during the stroke at a predetermined level. The pressure level of a certain size depends on the difference in the circumferential length of the sections and depends on the possibility of obtaining a suitable seal at the section having the smallest circumferential length. If the difference is large and the appropriate pressure level is too high to achieve a suitable sealing force at the minimum circumferential length, the change in pressure can be configured during the stroke. This situation requires pressure management of the piston. Materials used commercially are generally not compact, especially when comparable pressures can be used, so there must be a possibility, for example, by using a valve to maintain this pressure for inflation purposes. In the case of a device that is operated using a spring force to obtain pressure, the valve may not be necessary. When the cross-sectional area of the field is changed, the volume of the container can be changed. Thus, in a section through the longitudinal direction of the chamber, the container may have a first shape in a first longitudinal direction and a second shape in a second longitudinal direction 'the first shape may be different from the second shape. In one case, at least a portion of the deformable material is compressible and the first shape

The force remains constant during this stroke.

The pressure in the piston can be defined. L兮—spring biased piston. This spring can vary in volume of the enclosed space 159900.doc 201235565. In some ways, 彳 change the total pressure or maximum and minimum pressure of the container. When the enclosed space is divided into a first-enclosed space and a second enclosed space, the spaces further comprise a volume for defining the first enclosed space such that the first enclosed space The pressure of the fluid in the fluid can be related to the pressure in the second enclosure. The space mentioned last time may be inflated 'for example by means of a valve, preferably an inflation valve (such as a Schrader valve). The possible pressure drop in the container due to leakage (eg, via the wall of the container) may be balanced by entraining the second enclosed space via the defining member, which may be a pair of pistons. One of the defined members in each enclosed space can be adapted to define the first enclosure space and the pressure in the container to be at least substantially constant during the stroke. However, any type of force level in the container can be defined by the defined components: a female candidate. The expansion of the piston when the piston moves to the large cross-sectional area at the first longitudinal position makes it possible to make the contact pressure under the current dust force value become too strong, so that it is necessary to maintain a suitable Sealed. Defining a member-to-piston, each enclosed space t & a enclosed space can be inflated to a certain pressure level such that a pressure rise can be transmitted to the first circumference. Enclosed type::::"15' regardless of the fact that (9) such as the piston and the living thing (the second enclosed type "": the chamber meter with no = area The pressure drop can also be set to 159900.doc -106 - 201235565 The pressure management of the piston can also be achieved by the pressure of the fluid in the enclosed space and the pressure of the fluid in the chamber. Relatedly achieved by providing a member for defining the volume of the enclosed space in communication with the chamber. In this manner, the pressure of the deformable container can be varied to achieve a suitable seal. For example, a simple The manner will be such that the defined members are adapted to define the pressure in the enclosed space to rise as the container moves from the second longitudinal position to the first longitudinal position. In this case, a simple piston between the two pressures (to avoid releasing the Any fluid in the shape of the container. In fact, the use of this piston can define any relationship between the pressures, as the chamber in which the piston translates can be tapered in the same manner as the main chamber of the combination. The direct delivery of the piston rod to a device in the container may also change the volume of the damper and/or the pressure therein. The piston may not have a valve for inflation or a valve for inflation (closed system) Or having a valve for inflating or communicating with a valve for inflating. When the piston does not have an inflation valve, the fluid may not pass through the material of the wall of the volume. One step in the installation process may therefore be The volume of the container is permanently closed after the fluid is placed in the volume of the piston and after the container has been positioned at the second longitudinal position of the chamber. The speed at which the piston can be obtained can depend on the large amount of fluid without excessive friction. The possibility of flowing down into the first enclosed chamber and out of the first enclosed chamber. When the piston has an inflation valve, the wall of the container is permeable to the fluid 0 159900.doc • 107- 201235565 = the device can be inflated by a pressure source contained in the piston, or an original similar to the outside of the combined body and/or when the chamber is the source of the pressure itself Pressure source. All solutions require a valve that communicates with the piston. Preferably, the valve is preferably an inflation valve, preferably a Schrader or a valve with a spring-operated spool. The Schrader valve has a spring. It is biased and closed independently of the force in the piston, and all kinds flow through it. However, it can also be a different valve type, such as a check valve. The sifter can be inflated by the enclosed space. The spring-biased rotary piston operates as a check valve. The fluid can flow from a pressure source (10) such as a pressure source or, for example, an internal pressure vessel, through a bearing of the piston rod of the spring-biased piston. Longitudinal pipe. * When the enclosed space is divided into a first enclosed space and a second enclosed space, the inflation can be performed by using the chamber as a source of force.

The enclosed space can prevent the first enclosed space from being inflated via the remaining _ 4L Zhengtian. The chamber may have an inlet valve 1 in the base of the chamber. The inflated 'available-inflating valve (for example, a valve with a spring-operated spool such as a Schrader valve) and an actuator . This may be a valve actuator according to actuation of 96/10903 or \^〇 97/435 70 or a valve actuator according to |〇99/2_2 or still 5,〇94,263. The core pin of the valve moves toward the chamber when closed. The actuating pin from the wo file cited above has the advantage that the force of the spool operating with the open spring force is so low that the aeration can be easily performed by a manually operated pump. The actuators cited in U.S. patents may require the force of a conventional compressor. The piston 159900.doc -108 - 201235565 is automatically inflated when the working pressure in the chamber is higher than the pressure in the piston. When the working pressure of the chamber to the middle is lower than the pressure in the piston, it is necessary to obtain a higher pressure by, for example, temporarily closing the outlet valve in the base of the chamber. When the valve is, for example, a Schrader valve that can be opened by means of a valve actuator according to w〇99/26〇〇2, this can be achieved by forming a bypass in the form of a channel, which is The road system is formed by connecting the chamber to the space between the valve actuator and the bearer of the valve. This bypass can be opened (the Schrader valve can remain closed) and closed (the Schrader valve can be opened) and can be accomplished by, for example, a movable piston. The movement of the piston can be manually configured, for example, by a pedal that is rotated by the operator about an axis from an inactive position to an active position and from an active position to an inactive position. Movement of the piston can also be accomplished by other components (like actuators), initiated by the results of pressure measurements in the chamber and/or the container. Obtaining a predetermined pressure in the container can be accomplished manually, and the operator is informed by a pressure gauge (e.g., a 'pressure gauge) that measures the pressure in the container. The predetermined pressure in the container is also automatically achieved, e.g., by the release valve in the container. The release valve releases fluid when the pressure of the fluid exceeds the maximum pressure setting. Obtaining the predetermined pressure in the container can also be achieved by a spring operated lid that closes the passage from the pressure source above the valve actuator when the pressure exceeds a predetermined pressure value. Another solution is the equivalent solution for the closable bypass of the outlet valve of the chamber, the pressure measurement being necessary in the damper, the wishing force measuring the steerable actuator, the actuator being The bypass of the valve actuator according to WO 99/26002, which opens and closes the Schrader valve of the container at a predetermined pressure value. 159900.doc •109- 201235565 The solution mentioned above also applies to any piston comprising a container, including the pistons shown in WO 00/65235 and WO 〇〇/70227. One such technique is the technique wherein the piston comprises a container comprising an elastically deformable container wall. The expansion or contraction of the container wall can be achieved by selecting a stiffener that forces the wall of the container to expand or contract in three dimensions, wherein the expansion or contraction of the container wall is by the circumferential length of the cross section. Change the size to start. Therefore, there will be no excess material between the wall of the container and the wall of the chamber. The effect of the pressure in the chamber on the piston is tolerated in order to limit the length of the contact. (longitudinal stretching) can also be performed by selecting a suitable reinforcement. The reinforcement of the wall of the container may be located in the wall of the container and/or may not be located in the wall of the container. The reinforcement in the wall of the container may be made of a fabric material. The wall of the container may be a layer, but preferably at least two layers that intersect each other, making the reinforcement easier to install. The layers can be, for example, woven or braided. Since the braided wires are placed closely to each other in different layers, the wires can be made of an elastic material. The layers can be vulcanized in, for example, two layers of an elastomeric material (e.g., rubber). When the barter has its production size, not only the elastic material of the wall, but also the reinforcement is unstressed and non-deformable. The distance between the intersections of the reinforcing walls of the container and the in-line expansion of the stomach (=the size of the stitches) can be made large, and the contraction during the contraction of the lines reduces the size of the stitches. The sealing of the wall of the container to the wall of the chamber can be established by pressurizing the container to a certain pressure. By this, the line will expand a little, making the stitch size become 159900.doc •110- 201235565 large. The contact of the wall of the container prevents internal pressure from causing the container to expand in such a way that the contact length will become too large and avoid jamming. The braided reinforcement can be made, for example, from elastic strands and/or elastically bendable wires. The expansion of the wall of the container can be carried out by stretching the bending loop of the knitted product. When the wall of the container contracts, the stretched loop can be changed back to its invariant state. Fabric reinforcements can be produced on the production line where the woven or warp knitted fabric reinforcement is placed into a cylinder in two layers of elastomeric material. A rod is located in the smallest cylinder on which the lid is held in a top-down, top-down, etc. order, and the lids are movable on the rod. At the end of the rank, a vulcanization oven is held. The interior of the flood box may have the size and form of the container in a state of no stress and no deformation. Portions of the cylinders inside the oven are cut in length, with two caps located within the cylinders, at the ends, and held at the ends. The oven was closed and steam at a high pressure of more than 100 ° C was placed. The oven can be opened after about 1 minute to 2 minutes and a finished container wall is formed in which the two covers are vulcanized in the other wall. In order to use the momentary lead time of vulcanization, there may be more than one oven' such as rotating or translating, and all ending at the end of the line. It is also possible for the line itself to have more than one oven, which uses the delivery lead time as the cure time. The production of the fiber reinforced walls of the container can be carried out analogously. The reinforcing fibers can be produced, for example, by injection molding (including assembling the stem) or by cutting the strips that will be placed at the ends of the assembled tube holder. Both options are easy to produce continuously. For the remainder, the production process will be similar to the production process mentioned above for fabric plus 159900.doc -111- 201235565 firmware. The piston of the i3 elastically deformable container may also include a reinforcing member that is not located in the wall, such as a plurality of resilient arms, which may or may not be inflatable, attached to the wall of the container. In the case of an inflatable type, the reinforcement also acts to limit the deformation of the wall of the container due to the pressure in the chamber t. Another option is a stiffener external to the wall of the container. Another aspect of the invention is the aspect associated with a combination of a piston and a chamber, wherein the chamber defines an elongated chamber having a longitudinal axis, the piston being at least self-contained in the chamber a second longitudinal position is moved to a first longitudinal position, the chamber having an elastically deformable inner wall along at least a portion of the inner chamber wall between the longitudinal position and the second longitudinal position, the chamber The chamber has a first cross-sectional area at its first longitudinal position when the piston is at the position and a second cross-sectional area at the second longitudinal position thereof when the piston is at the position, the first cross-sectional area being greater than The second cross-sectional area, when the piston moves between the first longitudinal position and the second longitudinal position, the change in the cross-section of the chamber is at least substantially between the first longitudinal position and the second longitudinal position On the continuous. Therefore, instead of a combination of pistons suitable for cross-sectional changes of the chamber, this aspect relates to a chamber having an adaptability. Naturally, the piston can be made of a material that is at least substantially incompressible, or a combination can be made from an adapting chamber and an adapting piston, such as a piston according to the above aspect. 159900.doc -112· 201235565 乂 地 ' The piston has a shape in the cross section along the longitudinal axis - a shape that tapers in a direction from the second longitudinal position. A preferred manner of providing an adaptation chamber is to have a chamber comprising: an outer support structure enclosing the inner wall, and a fluid defined by the outer support structure and the inner wall A space to accommodate. The choice of a combination of fluids or fluids in such a way can help define the biomass of the chamber, such as the seal between the wall and the piston, and the force required. In another aspect, the invention relates to a combination of a piston and a chamber, wherein: the chamber defines an elongated chamber having a longitudinal axis, the chamber having its first position at its first longitudinal position a cross-sectional shape and an area and having a second cross-sectional shape and an area at a second longitudinal position thereof, the first cross-sectional shape being different from the second cross-sectional shape, the change in the cross-sectional shape of the chamber at the first longitudinal position and the first The two longitudinal positions are at least substantially continuous, the piston being adapted to adapt itself to the cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber. This very interesting aspect is based on the fact that, for example, the different shapes of the geometry have a varying relationship between their circumference and area. Moreover, the change between the two shapes can occur in a continuous manner such that the chamber can have a cross-sectional shape at one of its longitudinal positions and have a cross-sectional shape at a second longitudinal position of 159900.doc • 113 · 201235565 'At the same time maintain a preferred smooth change in the surface of the chamber. In the current context, the shape of the - section is its overall shape, regardless of its size, the two circles have the same shape, although the _ circles have a diameter different from the diameter of the other circle. Preferably, the 'first cross-sectional area is at least 2% larger than the second cross-sectional area (such as at least 5%), and the vehicle cross-over is at least at least (such as at least 2%), preferably at least 鄕 (such as at least 40%), preferably. At least 50% (such as at least 6%), preferably at least 70 〇/. (such as at least 80%, such as at least 9〇% 'such as at least %%). In a preferred embodiment, the first cross-sectional shape is at least substantially circular ' and wherein the second cross-sectional shape is an elongated shape (such as an elliptical shape) having a first size The first dimension is at least 2 times (such as at least 3 times), preferably at least 4 times the size of an angle. In another preferred embodiment, the first cross-sectional shape is at least substantially circular and such that the second cross-sectional shape comprises two or more at least substantially elongate (e.g., convex) portions. § In the section at the first longitudinal position, the first circumference of the chamber is between 8〇% and 120% of the second circumference of the section at the second longitudinal direction of the chamber (such as 85% to 115%) ), preferably 90% to 11% (such as 95% to 105%), preferably 98% to 102%, see several advantages. When attempting to against a wall seal of varying size, problems may arise due to the fact that the sealing material should provide sufficient sealing and change its size. If in the preferred embodiment the situation is that the circumference changes only to a small extent, the seal can be more easily controlled. Preferably, the first circumference and the second circumference are at least substantially 159900.doc • 114-201235565, such that the sealing material only bends and does not stretch to any significant extent. Alternatively, it may be desirable for the circumference to vary slightly, as the material (e.g., 'bending) will have one side compressed and the other side stretched when bent or deformed. In general, it is desirable to provide a desired shape with a circumference at least close to the circumference of the sealing material that will automatically "select". One type of piston (which can be used in a combination of this type) is a piston containing a piston, which contains a deformable container. The container may be elastically deformable or non-elastically deformable. In the last mode, the wall of the container is movable in the chamber. The elastically deformable container can also be used in a combination of this type' and can particularly have a high speed piston having a production size that is approximately the circumferential length of the first longitudinal position of the chamber. It has a type of reinforcement that allows it to shrink under high friction. It is also possible to use an elastically deformable container having a production size substantially equal to the circumferential length of the second longitudinal position of the chamber, having a reinforcement type of the outer skin, the reinforcement type The portions of the wall of the container are allowed to have different distances from the central axis of the chamber in the longitudinal section of the chamber. Clearly, depending on where the combination is viewed, one of the piston and the chamber can be stationary and the other can be moved, or both can be moved. This has no effect on the function of the combination. The piston can also slide on the inner and outer walls. The inner wall may have a wedge shape and the outer wall is cylindrical. Naturally, the current combination can be used for several purposes, as its main 159900.doc • 115· 201235565 is to provide a way to make the translation of a piston suitable for the required/occupied force: a novel way of approach . In fact, the area/shape of the cross-section may vary along the length of the chamber to accommodate the combination for a particular purpose and/or force to provide a system for use by a woman or adolescent, i.e., still adequately provided A pump of a certain pressure. In either case, an economically improved pump can be required by determining the force that the person can provide at this location of the piston, and thereby providing a chamber having a suitable cross-sectional area/shape. Another use of the combination would be for a shock absorber where the area/shape would determine which translation would be required for a certain impact (force). Moreover, an actuator can be provided in which the amount of fluid introduced into the chamber will provide for different translation of the piston depending on the actual position of the piston prior to introduction of the fluid. In fact, the nature of the piston, the relative position of the first longitudinal position to the second longitudinal position, and the configuration of any valve connected to the chamber can provide different pressure characteristics and different force characteristics to the pump motor, actuator, shock absorber, and the like. . A preferred embodiment of a combination of a chamber and a piston has been described as an example to be used in a piston pump. However, this should not limit the scope of the present invention to this application, as it may be primarily a valve configuration of the chamber to initiate movement in addition to the fact that which items or media may initiate movement, which may be of the type of application Decisive: pump, actuator, shock absorber or motor. In a piston pump, a medium can be drawn into a chamber, which can be closed by a valve arrangement. The medium can be compressed by movement of the chamber and/or the piston, and A subsequent valve can release the compressed medium from the chamber. In an actuator, a medium can be pressed into a chamber by a valve configuration, and the piston and/or the chamber can be moved to initiate an attached device 159900.doc •116·201235565 mobile. In the shock absorber, the chamber can be completely enclosed, wherein a compressible medium can be compressed by movement of the chamber and/or the piston. Where the non-compressible medium can be located inside the chamber, for example, the piston can be equipped with several small passages. These small passages can give a dynamic friction so that the movement can be slowed down. Additionally, the present invention can also be used in propulsion applications in which a medium can be used to move a piston and/or chamber that can be rotated about an axis (e.g., in a motor). Any kind of principle according to the invention can be used for all of the above mentioned applications. The principles of the present invention can also be used in pneumatic and/or hydraulic applications other than the above & piston cones. Thus, the invention also relates to a pump for pumping a fluid, the system comprising: - a combination according to any of the above aspects, - a member for engaging the piston from a position outside the chamber - connected to the chamber and comprising a fluid inlet of one of the valve members, and - connected to one of the fluid outlets of the chamber. • In one case, the engagement member can have an outer position and an inner position at which the piston is in its first longitudinal position, at which the piston is in its second longitudinal position. This type of pump is preferred when a pressurized fluid is desired. In another aspect, the engagement member can have an outer position and an inner position at which the piston is in its second longitudinal position, at which the piston is in its first longitudinal position. This type of pump is preferably 159900.doc • 117· 201235565 when there is no substantial pressure required but only fluid delivery is desired. In the case where the pump is adapted to stand on the floor and the piston/engagement member compresses fluid (such as air) by being forced downward, the maximum force can be economically provided at the lowest of the piston/engagement member/handle Location. Therefore, in the first case, this means providing the highest pressure here. In the second case, this simply means seeing the largest area at the lowest position and thereby seeing the maximum volume. However, due to the fact that it is necessary to exceed the pressure of, for example, the pressure in the tire in order to open the valve of the tire, the minimum cross-sectional area not far before the lowest position of the engaging member may be desired to open the valve to the resulting pressure. And the larger cross-sectional area forces more fluid into the tire. Since the pump according to the present invention can use much less work force than a comparable pump based on a conventional piston-cylinder combination, for example, the pump can draw water from a deeper depth. This feature is extremely important, for example, in less developed countries. Moreover, the chamber according to the present invention may have another function in the case where the liquid is pumped when the pressure difference is almost zero. It can be adapted to the physical needs of the user (human factors engineering) by appropriate design of the chamber, for example as if there is a pressure difference: for example, according to Figures 17B and 17A, respectively. This can also be done by the valve. The invention also relates to a piston which is sealed to a cylinder and simultaneously sealed to a wedge cylinder. The piston may or may not comprise an elastically deformable container. The resulting chamber may be of a type having a different cross-sectional area or a different circumference. The piston can include one or more piston rods. Moreover, the cylinder may be cylindrical or may be wedge-shaped on the outside. Moreover, the present invention relates to a shock absorber comprising: -118· 159900.doc

-D 201235565 - a combination of any one of the combined body aspects, - a member for the position of the salvage piston from outside the chamber, wherein the spray member has an external position and a __ (four) position in the material portion The piston is in its first longitudinal position at the position where the piston is in its second longitudinal position. 5H shock absorption|§ Further inclusion, post-production ^^3 is connected to the chamber and contains a fluid inlet for a valve member. Moreover, the shock absorber can include a fluid outlet connected to the chamber and including a member. The chamber and the piston may preferably be characterized as "the cavity containing at least one of the fluids at least substantially sealed" when the piston is moved from the first longitudinal position to the second longitudinal position. Typically the shock absorber will include means for biasing the piston toward the first longitudinal position. Moreover, the present invention relates to an actuator comprising: - a combination according to any one of the combined body aspects, - a member for engaging the piston from a position outside the chamber, - for fluid A member that is introduced into the chamber to displace the piston between the first longitudinal position and the second longitudinal position. The actuator can include a fluid inlet coupled to the chamber and including a valve member.

D Moreover, a fluid can be provided that is coupled to the chamber and that includes a member. Additionally, the actuator can include a biasing piston toward the first longitudinal position or the second longitudinal direction 159900.doc -119 - 201235565 member. The present invention relates to a motor comprising: a combination according to any of the combinations of the above-mentioned combinations. Finally, the invention also relates to a power unit which is preferably moveable, for example, by a parachute, ie M (movable) P (power (unit). Such a unit may comprise any kind of power source Preferably at least one set of solar cells, and a power device, such as a motor according to the invention. There may be at least one service device, such as a pump according to the invention, and/or with a piston self-contained according to the invention in combination with a chamber Any other device that derives excess energy from the low working force of the device. Due to the extremely low working force, it is possible to transport an MPU by parachute, because the structure of the device based on the present invention can be constructed to be more classic than The light weight of the components of the piston-cylinder combination. The various embodiments described above are provided by way of illustration only and are not to be considered as limiting of the invention. And exemplified, and without departing from the true spirit and scope of the present invention, _ β All piston types, in particular those of the container having elastically deformable walls, are sealingly connected to the chamber wall during their movement between the longitudinal positions, meshingly or not connected to the piston type The wall of the chamber is either meshably and sealingly connected to the chamber wall. Additionally, there may be no engagement between the walls, it is possible that the walls are in contact with one another, and this may occur, for example, in a container In the case of moving from the first longitudinal position to the second longitudinal position 159900.doc - 120 - 201235565 in the chamber. The type of connection between the walls (sealed and/or meshed and/or contacted and/or Or not connected) by using the correct internal pressure inside the wall of the vessel to achieve a lower pressure for the sealing connection, a lower pressure for the spray connection and a connectionless (production size container) ( For example, atmospheric pressure, therefore, a container having a confined space may be preferred because the enclosed space can control the pressure inside the container from a position outside the piston. One choice The term is a thin wall of the container which may have a reinforcement extending beyond the surface of the wall such that leakage may occur between the wall of the container and the wall of the chamber. 507 SUMMARY OF THE INVENTION Valve actuation of the present invention The device and its embodiments are the subject matter of the technical solutions 1 and 2 to 17. The valve connector and the pressure valve or the hand pump including the valve actuator of the present invention are the targets of the technical solutions 18 and 19, respectively. The use of a valve actuator in a fixed configuration. The present invention provides a valve actuator comprising: an inexpensive combination of a cylinder in which a piston driving a start pin moves; and a start Pin, which has a simple construction. This combination can be used in a fixed configuration, such as a chemical factory, where the activation pin engages a spring force operated core pin of a valve (eg, a release valve) and is used in a valve connector (eg, Used to inflate the tires). The disadvantages of conventional valve connectors have been overcome by the valve actuators of the present invention. The valve actuator is characterized by a piston having a piston ring that fits into the cylinder, wherein the s-sinus piston is first in its first position from the first 159900.doc • 121 · 201235565 end of the cylinder Scheduled distance. In the second position of the piston, it is spaced from the first end of the vapor red by a second predetermined distance, wherein the second predetermined distance is greater than the first predetermined distance. The cylinder wall includes a conductive passage for allowing gas and/or liquid medium to conduct between the cylinder and the facet section when the piston is in the first position, while the piston is in the second position The conduction of the gas and/or liquid medium between the cylinder and the coupling section is inhibited by the piston. An embodiment of the valve actuator of the present invention according to claim 6 is characterized in that the conduction path from the pressure source to the valve to be actuated includes the displacement of the π cylinder diameter A 'the diameter of the vapor red纟 disposed around the piston of the activation lock in the bottom of the cylinder, when the piston is in the first position, enabling the medium from the pressure source to flow to the open spring force operated spool pin, such as from Schröder valve. The enlargement of the diameter of the cylinder may be uniform, and the cylinder wall may have one or several sections near the bottom of the cylinder, wherein the distance between the center line of the cylinder and the cylinder wall increases, so that # is in the piston position : In the first position, the gas and/or liquid medium can flow freely around the edge of the piston ring. A variation of this embodiment has a valve actuator configuration in which the sparklet has a magnification of twice the diameter. The distance between the magnifications may be the same as the distance between the sealing steps of the sealing member. When three valves of different sizes can be lightly connected, the valve actuator can include a cylinder having three amplifications. However, it is also possible to connect valves of different sizes to a single actuator valve actuator having an enlarged diameter for the cylinder. Thus, now, the number of such amplifications can be different from the number of valves of different valve sizes that can be coupled. Another embodiment of the present invention according to claim 10 is characterized in that the conductive passage of the boring tool of the body of the 159900.doc-122·201235565 valve actuator is provided. The passage forms a passage for the gas and/or liquid medium between the cylinder and the portion of the valve actuator that is connected to the S-valve. The hole of the passage opening of the horse # Α ^ 〇β Μ / fly red is positioned so that

Preferably, when the piston is in the 箆-+ _ L position, the pressurized gas and/or liquid medium flowing from the pressure source to the cylinder can flow through the passage to the valve to be actuated. When the piston is in the second position, it blocks the cylinder so that the flow of pressurized gas and/or (iv) medium to the web towel (4) is possible.

Instead of any type of gas, a mixture of gases and/or liquids can activate the actuating pin and flow around the piston of the valve actuator when the piston is in its first position. The present invention can be used in all types of valve connectors, and valves having a core pin operating with an elastomeric force (eg, a Schrader valve) can be attached to the valve connectors, and in a face-to-face method or connector The number of light holes is beneficial. Additionally, the valve actuator can be consuming, for example, a foot pump, a car pump, or a compressor. The valve actuator can also be integrated into any pressure source (eg, hand pump or exhaustion, regardless of the availability of the fastening member in the inter-connector; the invention is also likely to be used in a permanent construction T-tool The actuator pin of the actuator engages the core pin of the permanently installed valve. 19597 Overview of the Invention In the first aspect, the present invention relates to _,.  a combination of a piston and a chamber, the assembly comprising an elongated chamber by an inner chamber sheet metal w + Aijie, and comprising a piston in the chamber, the piston The chamber wall moves in meshing engagement with at least a first longitudinal position of the chamber and a longitudinal position of a cage, which engages a rigid surface, and the station At # causes the movement, wherein the movement The combination can move relative to the surface. -123· 159900. Doc 201235565 The force provider for enabling relative movement of the portion of the combination can move by itself, and the path of the last mentioned movement does not exactly follow the relative movement of the piston rod, piston and chamber at all times. path. Thus, the force k donor and the system of the combination can provide a flexibility somewhere in the system to avoid damage. When the force provider can associate the combination with the force of the change, and the force provider can also maintain the non-moving portion of the combination toward a rigid surface to enable the relative movement, if the rigid surface Having the function of providing a reaction force for the combination, there may be conflicting damage towards the combination. When the pump is used by the human body, the last mentioned situation can occur while the pump is pressed against the rigid surface (e.g., the floor) by the user's foot. In particular, when a standing person uses a foot pump to inflate a tire, and especially when the floor is not in a horizontal plane. Thus the combination should be movable relative to the rigid surface to follow the path of the force provider. In a second aspect, the problem of incompatibility is particularly important when a chamber is used having a plurality of sections having different cross-sectional areas at the first longitudinal position and the second longitudinal position. And at least substantially continuous different cross-sectional area and circumferential length at an intermediate longitudinal position between the first longitudinal position and the second longitudinal position, the cross-sectional area and circumferential length at the second longitudinal position being less than the first longitudinal direction This is also true in the case of a section at the position where the cross-sectional areas at the first longitudinal position and the second longitudinal position have different sizes but equal circumferential dimensions. In an optimized embodiment for obtaining the highest level of energy reduction, the chamber of the foot pump, for example for tire inflation, has a minimum of 159,900 at its bottom. Doc • 124· 201235565 Possible cross-sectional area and maximum possible cross-sectional area β at its top Therefore, at the smallest cross-sectional area, the maximum torque is related to the displacement from the chamber to the base of the pump. Thus, the combination should be movable relative to the rigid surface for travel along the path of the force provider. In a third aspect, the conjugate includes a pedestal for engaging the conjugate to a rigid surface, enabling relative movement of the piston and the chamber, the conjugate being rigidly secured to a pedestal, The base is moveable relative to the rigid surface. The pedestal can have two morphing surfaces on the rigid surface to ensure stable position of the combination, even when the rigid surface is not flat. The combination can then be rotated about any of the lines between the three engagement surfaces. However, this is a bad solution because the path of the human provider is usually a three-dimensional path. Moreover, when the surface is not in the horizontal plane, the compensation of the positioning of the combined body cannot be obtained by this solution. Moreover, in the case of a foot pump for tire inflation, the user "the foot typically presses the base of the pump against the rigid surface, which may prevent this (4) movement. In a fourth aspect, the combination includes a base for engaging the combination to a rigid surface, enabling relative movement of the piston and the chamber, the coupling being, for example, by elastically deformable The sleeve is flexibly fastened to the seat. This solution, in combination with a pedestal with a three-to-four surface, is the best solution for all needs: the path of the combination can be any path used by the force provider (eg, the user) while the pedestal Standing on the surface 159900. Doc •125· 201235565 is pressed, for example, by the user's foot. Not only can the rigid surface not in the horizontal plane be compensated, so that the combination, rather than the pedestal, is still perpendicular to the water, the user of the foot pump is able to initiate any path during the stroke. After use, the combination automatically returns to its rest position, i.e. perpendicular to the rigid surface. Of course, alternative technical solutions for the bushing are possible, such as a ball write joint held in the ball bearing of the base at the end of the cylinder, the ball being combinable with a spring that limits the combination Deflection, and returning polarization to preset after use "This solution (not shown) may be more expensive than bushing. In the sixth aspect, the combination can be joined to the base by means of an elastically deformable bushing. The bushing is mounted in the bore of the base and the chamber is mounted in the bore of the bushing or vice versa. The combination can be fitted into the base by suitable fittings but cannot be moved in the longitudinal direction. The combination can now at least now rotate in the bushing relative to the base and thus rotate relative to the rigid surface. The deflection of the combination deforms the burnt wall of the liner. The wall thickness of the liner can be much greater than the wall thickness of the chamber, enabling the substantial polarization angle of the chamber. In addition, the fitting may have a feature such that it also maintains the force of the combination relative to the base during the stroke (including the end of the stroke) such that the combination is prevented from being longitudinal relative to the base Pan on the top. In the seventh aspect, the modified bushing can have a protrusion on its top that is attached to the top of the base. This prevents the bushing from moving in the direction towards the base. By combining the other protrusions on the inner side of the bushing or at the outer side of the combined body, the combined body and the bushing are respectively associated with the groove set 159900. The doc 201235565 combination prevents the possible translation of the combination to the base and from the pedestal. In addition, the resiliently deformable bushing can act as a soft load for the combination when the piston and/or the chamber reaches the end of the movement. This feature makes the spring between the handle and the cover on the piston rod redundant in the classic foot pump for tire inflation. In an eighth aspect, the combination includes an elongated chamber bounded by an inner chamber wall and including a piston in the chamber, the piston being at least in the chamber relative to the chamber wall Sealingly moving between a first longitudinal position of the chamber and a second longitudinal position, the combination engaging a rigid surface to enable the movement, wherein the combination includes a piston rod connected by A guiding member (e.g., a cover) of the combination is guided, and the guiding member is movable relative to the chamber. This is also true for piston chamber combinations having different cross-sectional areas and equal or different circumferential dimensions. The guiding member may comprise a gasket having a small hole having a suitable fitting with the piston rod, and the gasket is movable within a larger hole in the cover: the living body is mainly in the combined body Pan in the lateral direction. The loop can be returned to its predetermined position by means of a spring force (e.g., a beak ring between the aperture in the cover and the outer side of the guide member). The size of the hole mentioned last time determines the degree of deflection of the piston rod and how much the configuration of the piston allows it to deflect. If the piston rod is rigidly fastened to the piston, the configuration of the piston determines the degree of deflection. If, for example, a ball joint is applied between the piston and the piston rod, the degree of deflection is determined only by the guiding member. 159900. Doc • 127- 201235565 In the ninth aspect, '4' allows the piston rod to be deflected relative to the longitudinal center axis of the remainder of the combination, and the contact surface of the guiding member may be a clothing line. For example, 'the inner wall of the convex section through the hole in the guiding member. In a tenth aspect, the piston may be rounded so as to follow the life of the piston rod or the connection of the piston to the piston rod may be flexible, rotatable eleventh aspect, the present invention Regarding the knot of a piston and a chamber, wherein the center line of the portion of the handle where σ is opposite to the central axis of the combined body has a phase difference from the central axis. The angle. The user's hand has different positions on the centerline when operating the handle of the pump, depending on how the hand holds the handle. In the case of a classic foot pump, high working force may be achieved by a cylinder having a circular cross section of constant size. If a relatively heavy force is transmitted from the user's arm via the hand attached to the arm, 'when no torque is present, the hand will be best positioned relative to the arm. This can be obtained if the longitudinal axis of the arm passes through the center point of the axis of the handle, wherein the handle is held by the hand attached to the arm. Due to the relatively large size of the force, the grip of the handle should be stable 'this can be done by a hand curve like a loose fist: the sigh of the handle can contain a part with a circular cross section . The size of the sections is variable depending on the distance from the central axis of the piston chamber combination. In a plane perpendicular to the - line in the piston chamber combination, the preferred angle between portions of the handle may be 18 inches. . However, the angle is also 159,900. Doc •128· 201235565 can be different from 180°. Additionally, the angle may be less than 180 in a plane containing the central axis. . In order to prevent the hand from slipping away from this part, a stop can be provided, which can also be used for force transmission. Other options (180. and greater than 180°) can of course also appear. In the case of an innovative foot pump having a chamber, the force can be lower, wherein the cross section of the chamber has a magnitude that varies between the two positions of the chamber in the longitudinal direction. When the right arm of the user transmits a relatively low force via the hand connected to the arm, the hand can be positioned relative to the arm such that a certain moment can occur. The contact area is the area where the hand is released. The handle can be designed to have a section that is delimited by, for example, an elliptical curve. An axis perpendicular to a central axis of the piston chamber combination may be greater than an axis parallel to the axis. In a plane perpendicular to the central axis of the piston chamber assembly, the preferred angle between the two portions of the handle may be slightly less than slightly greater (better!) 180. . These positions of the portion of the handle follow the rest position of the hand. If the handle can be rotated about the central axis of the piston chamber assembly, then two positions can be obtained by one handle design. In order to avoid the presence of torque, the line passing through the center of the two portions of the handle cuts the last mentioned axis in a plane perpendicular to the central axis of the piston chamber combination. The angle can be 180 in a plane containing the central axis of the piston chamber combination. Or smaller, or different from 18〇. . The conical shape of the cylinder provides a substantial reduction in the amount of working force. By special configuration, the shape of the conical cylinder is 159900 in the longitudinal direction of the chamber. Doc • 129· 201235565 can be formed in a manner such that the force on the handle remains constant during the stroke. This force can be changed when the valve is opened later, for example due to the fact that the valve piston sticks to the valve root or there is dynamic friction, for example due to the small size of the cross section of the passage, and therefore by The force emitted by other sources of the shape of the chamber. In addition, the friction of the piston against the wall of the chamber can be changed during the stroke due to contact? The size of the domain changes. The shape of the cylinder shown is in the longitudinal direction in all relevant figures of the present patent application in the manner mentioned above, and the cross-section of the conical cylinder is circular 'this is also shown in the relevant diagram In the formula. The shape is limited to the minimum size of the piston. Accordingly, the present invention is also directed to a pump for a pumping fluid, comprising: - a combination according to any of the above aspects, - a member for spraying the piston from a position outside the chamber, Connecting to the chamber and comprising a fluid inlet of one of the valve members and a fluid outlet connected to one of the chambers. In the event that the kneading member can have an outer position and a telescopic position at which the piston is in its first longitudinal position, at the inner position the piston is in its second longitudinal position. When a pressurized fluid is desired, this type of pump is preferably β. In another case, the spray member may have an outer position and a position at which the piston is in its first: longitudinal position. The piston at the inner position is in its first 铷aa^ longitudinal position. This type of pump is preferred when there is no substantial pressure for the desired but only fluid delivery is required for the & knives. Doc •130.  201235565. In the case where the pump is adapted to stand on the floor and the piston/engagement member compresses fluid (such as air) by being forced downward, the maximum force can be economically provided at the lowest of the piston/engagement member/handle Location" Therefore, in the first case, this means providing the highest pressure here. In the second case, this simply means seeing the largest area at the lowest position and thereby seeing the maximum volume. However, due to the fact that it is necessary to exceed the pressure of the pressure in the tire so as to open the valve of the tire 'at the lowest position of the engaging member, the minimum cross-sectional area is not far before, so that the desired pressure is opened. And the larger cross-sectional area forces more fluid into the tire (see Figure 2B). Further, the present invention relates to a shock absorber comprising: - a combination according to any one of the combined body aspects, - a member for engaging a piston from a position outside the chamber, wherein the spray member has an outer portion a position and an internal position at which the piston is in its first longitudinal position, at which the piston is in its second longitudinal position. ♦ The shock absorber can further include a fluid inlet connected to the chamber and including a valve member. Moreover, the shock absorber can include a fluid outlet connected to the chamber and including a member. The chamber and the piston are preferably formed to contain a void that is at least substantially sealed by one of the fluids. The fluid is compressed as the plug moves from the first longitudinal position to the second longitudinal position. Typically, the shock absorber will contain a bias for 159900 towards the first longitudinal position. Doc •131· 201235565 The components of the plug. Finally, the invention also relates to an actuator comprising: - a combination of any one of the combined body aspects, a member for engaging the piston from a position outside the chamber, - for A member that introduces fluid into the chamber to displace the piston between the first longitudinal position and the second longitudinal position. The actuator can include a fluid inlet coupled to the chamber and including a valve member. Also 'may provide-connecting to the chamber and including the fluid output of the valve member D. Additionally, the actuator may include means for biasing the piston toward the first longitudinal position or the second longitudinal position. [Embodiment] 19617 DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings, in which: Figures 1 to 3 discuss the limitation of the extension of the wall of the piston. This situation includes a limitation of the extension in the longitudinal direction when the piston is subjected to the pressure of the cavity to the middle and allows expansion in the lateral direction when moving from the second longitudinal position to the first longitudinal position. The extension of the wall of the bar type piston in the longitudinal direction can be limited by several methods. This limitation can be made by reinforcing the walls of the container using, for example, fabric and/or fiber reinforcement. This restriction can also be made by the expansion body (which limits the expansion of the expansion body) located inside the chamber of the container when the expansion body is connected to the wall of the container. Other methods can be used, for example, the two walls of the container are 159900. Doc •132·201235565 chamber-to-pressure management, pressure management of the space above the container, etc. The expansion of the wall of the actuator can be dependent on the type of extension & limit used. In addition, the retention of the piston that moves over the piston rod during expansion can be guided by a mechanical stop. The positioning of the stop can depend on the use of the piston chamber combination. This can also be the case for guiding the container above the piston rod when expanding and/or experiencing an external force. All types of fluids can be used: a combination of a compressible medium and an incompressible medium, a compressible medium only, or an incompressible medium only. Since the change in the size of the container can be substantially expanded from the smallest cross-sectional area (eight of which has its production size) and expanded at the maximum cross-sectional area, the chamber in the container and, for example, the first enclosed space in the piston rod Connectivity can be necessary. In order to maintain the pressure in the chamber, the first enclosed space may also be pressurized during the change of the chamber of the container. Pressure management for at least the first enclosed space may be required. Figure 1A shows a longitudinal section of a chamber 186 having a concave wall 185 and an inflatable piston containing a container 208 at the beginning of the stroke (= = the first longitudinal position in the chamber I%) and at the end of the stroke (= first longitudinal position in chamber 186) container 208'. The central axis of the chamber 186 is 184. The container 208 exhibits its production size with a fabric reinforcement 189 in the outer skin 188 of the wall 187. During the stroke, the wall i 87 of the container expands until the stop configuration stops the movement during the stroke, which may be the fabric reinforcement 189 and/or the mechanical stop 196 external to the container 208 and/or another stop Stop configuration. And thus the expansion of the bar 208 is stopped. Depending on the dust force in the chamber 186, the longitudinal extension of the wall of the container can still occur due to the pressure in the chamber 186. Doc -133 - 201235565 The main function of the firmware is to limit this longitudinal extension of the wall (8) of the container. During the stroke, the internal pressure of the container 2〇8, 2〇8• can be maintained. This pressure is dependent on the change in volume of the container, 2, 8, thus depending on the change in the circumferential length of the section of the chamber 186 during the stroke. It is also possible that the pressure changes during the stroke. It is also possible that the pressure changes during the stroke, depending on or not depending on the pressure in the chamber 186. Figure 1B shows a first embodiment of an expanded piston 208 at the beginning of the stroke. The wall 187 of the container is formed by the flexible material outer skin 188 and the fabric reinforcement 189 which is allowed to be stretched. The flexible material may be, for example, a rubber type or the like. The direction of the fabric reinforcement with respect to the central axis 184 (= braid angle) is different from that of 54. 4 [The change in the size of the piston during the stroke does not necessarily result in the same shape as drawn. Due to the expansion, the thickness of the wall of the container can be the thickness of the wall of the container produced as at the end of the stroke, the second longitudinal position. There may be a *permeable layer just inside the wall 187. It is tightly squeezed into the lid 191 at the top of the container 208, 208| and the lid, 192 at the bottom. The details of such covers are not shown and all types of assembly methods may be used, and such methods may be able to adapt themselves to accommodate varying thicknesses of the walls of the container. Both covers 191, I92 can be translated and/or rotated above the piston rod 195. . Such movement can be performed by various methods such as, for example, different types of bearings not shown. The lid 191 in the top of the container can be moved up and down. Outside the bar 208, a stop member 96 on the piston 195 limits the upward movement of the container 208. The cover 192 in the bottom can only be moved downwards, since the stop member 197 prevents upward movement, and this embodiment can be used in a piston chamber device having a pressure in the cavity 186 below the piston. Other configurations of the stop are at 159900. Doc -134.  201235565 Other pump types (such as dual working pumps, vacuum pumps, etc.) may be possible and depend only on design specifications. Other configurations for enabling and/or limiting the relative movement of the piston relative to the piston rod may occur. The wall 185a of the chamber 186 is parallel to the central axis 184. It is positioned substantially at the first longitudinal position at the end of the stroke. The tuning of the sealing force may comprise a combination of the incompressible fluid 205 and the compressible fluid 206 inside the container (both of which are also a possibility), but the container The chamber 209 can be in communication with the second chamber 21, and the second chamber 210 includes a spring-operated piston 26 inside the piston rod 195. Fluid can flow freely through the aperture 201 through the wall 2〇7 of the piston rod. It is possible that the second chamber is in communication with the third chamber (see Figure 12), but the pressure inside the container may also depend on the pressure in the container 186. The container may be inflated via the piston rod 195 and/or by communication with the chamber 186. The domes or the like 202, 203 in the cover in the top and bottom of the cover seal the covers 191, 192 to the piston rod, respectively. A cover 204 (shown as a thread assembly at the end of the piston rod 195) secures the piston rod. A comparable stop can be located elsewhere on the piston rod depending on the desired movement of the wall of the container. The area of contact between the wall of the container and the wall of the chamber is 198. Figure 1C shows the piston of Figure 1B at the end of the pump stroke, at the end of the pump stroke, the piston has its production size. The cover 191 in the top moves from the stop 196 by a distance a'. The spring force operated valve piston 126 is moved a distance b to indicate that the bottom cover is adjacent to the stop member 197, and when there is pressure in the chamber 192, the bottom cover 192 presses the stop member 197. The compressible fluid 206, and the non-compressible fluid 205'. The contact area 198 between the container 2〇8 at the second longitudinal position and the wall of the chamber. 159900 parallel to the central axis 184 of the chamber 186. Doc •135- 201235565 Wall 185b. It is located approximately at the second longitudinal position at the end of the stroke. Figure 2A shows a longitudinal section of a chamber 186 having a concave wall 185 and an inflatable piston comprising a container 21 7 at a first longitudinal position of the chamber and a container 217 at a second longitudinal position. The container 2丨7, showing its production size, has a fiber reinforcement 219 in the outer skin 216 of the wall 218 (according to the "grid effect"). During the stroke, the wall 218 of the container expands until a stop configuration stops the movement during the stroke, which may be the fiber reinforcement 219 and/or the mechanical stop 214 inside the container and/or another stop. Configuration. And thus the expansion of the wall 218 of the bar 217 is stopped. The primary function of the fiber reinforcement is to limit the longitudinal extent of the wall 218 of the container. During the stroke, the pressure inside the vessels 21, 21 7' can be kept constant. This pressure is dependent on the change in volume of the hoppers 21, 217' and therefore on the change in the circumferential length of the wear surface of the chamber 186 during the stroke. It is also possible that the pressure changes during the stroke, depending on or not depending on the pressure in the chamber 186. The contact area 2n between the container 217 at the first longitudinal position and the wall of the chamber. Figure 2A shows a second embodiment of an expanded piston 217 at the beginning of the stroke. The wall 218 of the container is formed by stacking a flexible material outer skin 216 (which may be, for example, a rubber type or the like) with a fiber reinforcement 219 that allows the container wall 218 to expand, and thus the fibers The direction (= braiding angle) of the center axis 184 may be different from 54.44. Due to the expansion, the thickness of the wall of the container may be less than (but not necessarily very different from) the thickness of the wall of the container as produced at the end of the stroke (= second longitudinal position). An impermeable layer 190 may be present inside the wall. It is pressed tightly into the lid 191 at the top of the containers 217, 217' and into the lid 192 at the bottom. These covers are not shown 159900. Doc • 136– 201235565 Details and all types of assembly methods are available, which may be able to adapt to the varying thickness of the wall of the container. Both covers 191, 192 can be translated and/or rotated over the piston rod 195. "The movement can be performed by various methods (e.g., different types of bearings not shown). The cover 191 in the top can be moved up and down until the stop 214 limits this movement. The cover 192 in the bottom can only be moved downwards, since the stop member 197 prevents upward movement, and this embodiment can be used in a piston chamber device having the pressure in the chamber 186. Other configurations of the stop may be possible in other pump types (such as • dual working pumps, vacuum pumps, etc.) and only depend on the specifications. Other configurations for enabling and/or limiting the relative movement of the piston relative to the piston rod may occur. The tuning of the sealing force can include a combination of the incompressible fluid 205 and the compressible fluid 206 inside the container (both of which are also a single possibility) 'but the chamber 215 of the container 217, 217' can be coupled to the second chamber 210 In communication, the second chamber 210 includes a spring force operated piston 12 6 inside the piston rod ι95. The fluid can freely flow through the hole 2 〇 1 through the wall 2 〇 7 of the piston rod. It is possible that the second chamber is in communication with the third chamber (see Figure ι), but the pressure inside the container may also depend on the pressure in the container 186. The container can be inflated via the piston rod 195 and/or by communication with the chamber 186. The O-rings or the like 202, 203 in the cover in the top and the bottom of the bottom seal the lids 191, 192 to the piston rod, respectively. The piston rod 2 (shown as a thread assembly at the end of the piston rod 195) is fastened to the piston rod. The wall 185a of the chamber 186 is parallel to the central axis 184. It is located approximately at the first longitudinal position at the end of the stroke. Figure 2C shows the piston of Figure 2B at the end of the pump stroke, at a stroke of 159900. At the end of doc -137· 201235565, the piston has its production size. The cover 191 is moved from the stopper 214 by a distance C'. The spring force operated valve piston 126 moves a distance. The bottom cover 192 is shown adjacent to the stop member 197. If there is pressure in the chamber 186, the cover 192 presses the stop member 197 » compressible fluid 2〇6, and the incompressible fluid 205° at the second longitudinal position of the container 217• Contact area 21 与 with the wall of the chamber I%. The wall 185b of the chamber 186 is parallel to the central axis 184. It is located approximately at the second longitudinal position at the end of the stroke. 3A, 3B, and 3C show an inflatable piston including a container 228 at the beginning of the stroke and a container 228' at the end of the stroke. The production size is the production size of the piston 228 at the second longitudinal position in the chamber 186. This configuration of the piston may be identical to the piston configuration of Figures 2A, 2B, 2C except that the reinforcement includes any type of reinforcing member that may be bendable and may be in abutment that does not intersect each other. The pattern of the "column". This pattern may be one of a pattern parallel to the central axis 184 of the chamber 186, or one of the portions of the reinforcing member may be in a pattern passing through the plane of the central axis 184. FIG. 3B shows wall 218 having skins 222 and 224. The stiffener 223 is a contact area 225 between the container 228 at the first longitudinal position and the wall of the chamber. Impervious layer 226. Figure 3C shows the contact area 225* between the container 228' and the wall of the chamber at the second longitudinal position. Figure 8D shows a top view of pistons 228 and 228' having reinforcing members 227 and 227', respectively. Figure 3E shows pistons 228 and 159900, respectively, having reinforcing members 229 and 229. Doc • 138· 201235565 228' top view. 4 shows the non-moving expandable piston 228 inside the chamber 186 having a center parallel to the center of the chamber 186 at a position where the piston 228" and the wall 185 of the chamber 185' The wall 185a of the axis 184, but there is no pressure differential between the sides of the piston in the cavity to the center. The portion 185 of the chamber that is further from the first location is at an angle to the central axis 184. The midpoint (center) 1〇〇1 projection 1000 of the elastically deformable wall of the piston on the central axis ι84 » Fig. 5A shows the piston of Fig. 4, which is not instantaneously in the wall 185 having a conical shape The chamber 186 moves inside, wherein the piston begins to expand, and the movable cover 191 moves toward the non-movable cover 192. The contact surface 225' is increased, and now located at the center 丨〇〇2 and 丨〇〇3, respectively, of the elastically deformable wall of the piston, the protruding portions of which are respectively at the central axis 1〇〇4 (old) and 1〇〇5 (New on. Distance f’. The moving direction of the movable cover 191 is 1〇〇6. The force 1007 from the wall 187 of the piston to the wall 185 of the chamber 186. Distance g'. Figure 5B shows the piston of Figure 5A 'the piston does not move instantaneously and thereby expands such that the contact area 225 of the piston wall 187 with the wall 185 of the chamber 186 is at the second longitudinal position of the contact surface 225" As the position increases, the movable cover 191 is not currently moving. The contact surface 225" is the point around the midpoint (center) of the midpoint (center) of the elastically deformable wall of the container. The centers of the elastically deformable walls of the piston are 1008 (old) and 1009 (new), with projections 1010 (old) and 1011 (new) on the central axis 184, respectively. Distance f. The force 1012 from the wall 185 of the piston wall 187 to the chamber. The direction of movement of force 1〇12 is 1013. The movement of the movable cover 191 is 1014» 159900. Doc • 139- 201235565 Figure 5 C tf Figure 5 B piston 'The piston does not move instantaneously and thereby expands so that the contact surface 225 '" of the piston wall 187 with the wall 185 of the chamber is in contact The second longitudinal position of the region decreases, and the contact area of the piston wall with the wall of the chamber increases at a first longitudinal position of the contact area, and the movable cover is not moving. The centers of the elastically deformable walls of the pistons 1015 (old) and 1016 (new)' have projections 1 〇 17 (old) and 1 〇 18 (new) on the central axis 184, respectively. The direction of movement 1019 of the reaction force 1020 from the wall 185 of the chamber to the wall 187 of the piston. The direction of movement of the wall 187 of the piston 102 Figure 5D shows the piston of Figure 5C in which the non-movable cover 192 is momentarily moved from the second longitudinal position to the first longitudinal position, thereby moving the piston in the same direction. Contact area 225''... is much smaller than 225', 225', of Figure 5C. Distance h’. Projecting portions 1022 of the center 1023 of the elastically deformable wall of the piston on the central axis 184, respectively. The moving direction of the movable cover 191 is 1024 ’ and the non-movable cover! The direction of movement of 92 is 1〇25, so the direction of movement of the entire piston. Leak 1026, which occurred at a point in time. Figure 5E shows the piston of Figure 5D with the piston movement reduced due to the increased contact area 225""". A projection 1 〇 27 on the central axis 184 of the center 1028 of the elastically deformable wall of the piston. The movable cover 19 is moved in the direction 1029. The direction of movement of the wall of the piston is 1〇3〇 and 1〇31. 6A shows an expandable piston 898 that is meshed or/and sealingly moved 900 in a conical chamber 899 that includes reinforcing (not shown) walls 9 that are embedded in the non-movable cover 9 and the movable cover 904. 1. The cover 9〇4 is slidably movable over the piston rod 902, and the piston rod 9〇2 is hollow and contains the enclosed air I59900. Doc •140· 201235565 and connected to the space in the piston 898. A mixture of fluid or fluid is present in the piston. The chamber is closed at both sides of the piston, has spaces 906, 907, and may contain a mixture of fluid or fluid at one or both sides of the piston 898. Contact area 905 between wall 901 of piston 898 and wall 897 of chamber 899. The presence of fluid at the sides of the piston can cause the piston to move in a manner different from the desired mode. Figure 6B shows the piston 898 of Figure 6A in meshing or/and sealingly moving 900 in a conical chamber 896 having spaces 908 and 909 at respective sides of the piston 898. Tube 911 is in a first longitudinal position in wall 895 of conical chamber 896, tube 911 allows space 908 to communicate with ambient atmosphere 910, and tube 912 fits into wall 895 of conical chamber 896, tube 912 allows Space 909 is in communication with the surrounding atmosphere 910. A contact area 905 between the wall 901 of the piston 898 and the wall 897 of the chamber 896. Figure 6C shows the piston 898 of Figure 6A in meshing or/and sealingly moving 900 in a conical chamber 894 having spaces 908 and 909 at respective sides of the piston 898. Tube 913 is in a first longitudinal position in wall 893 of conical chamber 894, tube 913 allows space 908 to communicate with the interior of tube 915 (the interior of tube 915 is in communication with tube 914) to which tube 914 fits In the wall 893 of the 896, the tube 914 is in communication with the space 909 of the conical chamber 894. The contact area 905 between the wall 901 of the piston 898 and the wall 893 of the chamber 896 Figure 6D shows the piston 892 meshingly moving in a conical chamber 899, the conical chamber 899 being in each of the pistons 892 There are spaces 906 and 907 on the side. The space 906 and the space 907 are connected to each other via a pipe 918. Doc • 141· 201235565 The tubes 918 are assembled in the covers 891 and 890, respectively. The contact area 9〇5 between the wall 901 of the piston 898 and the wall 897 of the cavity 899. Figure 6E shows a piston 89 that can be meshedly moved in a conical chamber 899. The chamber is closed at both sides of the piston, has a space of 9 〇 6, 9 〇 7 and can be at one side of the piston 898 or both The mixture contains a fluid or a fluid at the side. There is no contact area between the inner wall 922 of the conical chamber 899 and the outer wall 923 of the piston 924, but instead there is a gap 920 between the wall 922 and the wall 923, thereby allowing the fluid 921 to be at the piston 8 The movement moves in the opposite direction of 9〇〇. Figure 7D is a 3D pattern and showing a reinforcing matrix of fabric material that allows the walls of the containers 208, 208 to elastically expand and contract as they move in a sealed manner in the chamber 186. The fabric materials can be elastic and placed on top of each other in separate layers. The layers can also be woven and placed with each other. The angle between the two layers can be different from 54. 44'. When the material types and thicknesses of all layers are the same, and even if the number of layers is the same, the expansion and contraction of the walls of the container may be equal in the XYZ direction when the stitch lengths in each direction are equal. When the expansion of the stitch lengths ss and tt in each of the directions of the substrates becomes large, the shrinkage of the stitches Μ and U will become small. Because the material of the yarn can be elastic, another device that stops the expansion, such as a mechanical stop, may be necessary. The stop member can be the wall of the chamber and/or be shown as a mechanical stop on the piston rod, as shown in Figure 7B. Figure 7E is a 3D pattern and shows the reinforced matrix of Figure 7D that has been expanded. It is greater than the stitch length ss and the stitch length ss of U, and tt. The result of the shrinkage can result in the 159900 shown in Figure 7D. Doc •142· 201235565 The matrix shown. Material = 3 dimensional pattern and showing the reinforcing matrix of the fabric material, which is made of elastic yarn (but elastically bendable), and is:

= above or on each other. It is possible that the glandular system is the extra length of each ring: when the container is in its production size, the extra length is 'when located at the second longitudinal position of the chamber: The upward stitch distances ss, ·, and π, when the wall of the container expands, the 'non-elastic material (but elastically f-curved) can limit the maximum expansion of the wall 187 of the container 217. It may be necessary to stop the movement of the bar 217 above the piston rod 195 by, for example, the stop 196 so that the seal can be maintained. The lack of this stop 196 gives the possibility of forming a valve. Figure 7G is a 3D pattern and shows the reinforced substrate of Figure 7F that has been inflated. More than the stitch length ss " and U" stitch spacing ss, " and tt,". The result of the shrinkage can lead to the matrix shown in Figure π. Figure 8 shows a combination, in which the piston contains an elastically deformable container 372, the container 372 moves within the cylindrical wall 374 and the tapered wall 373 (e.g., shown here around the center axis 37〇) in the chamber 375. The piston is suspended from at least one of the piston rods 371. The display container 372 372, at a second longitudinal position of the chamber (372,) and at a first longitudinal position (372). All of the solutions disclosed in this document may also incorporate the following piston types: wherein the circumference is constant The chamber of the cross section may be a solution to the jamming problem. Figure 9A shows a longitudinal section of a chamber having a convex/concave wall ι85 and an inflatable piston 'the inflatable piston containing the container 258 at the beginning of the stroke and 158900.doc • 143· 201235565 End of the container 238, container 258, showing its production size. Figure 9A shows the longitudinal section of the piston 258, the piston 8 has a wall 25 ΐ and a reinforcing skin 252, a wall 251 and a reinforcing skin 252 borrow A plurality of at least elastically deformable support members 254 are rotatably secured to a common member 255 that is coupled to the pistons 258, 258, outer skin 252. These members are in tension and depending on the hardness of the material, It has a particular maximum extension length that limits the extension of the piston skin 252. The common component 255 can slide over the piston rod 95 along with the sliding member 256. For the remainder, the pistons 2, 8, 208 The construction is equivalent. The contact area is 253. Figure 9C shows the longitudinal section of the piston 258'. The contact area is 253. Figure 9D shows the longitudinal section of the piston 258" with the contact area 253. The piston is elastically deformable. The center of the wall 25 7 is 1 〇 2 〇. The protruding portion of the center point 1020 on the central axis 丨〇 22. Figure 10A shows a piston chamber assembly having a chamber 186 having a centerline 184 'the cavity The wall 185 of the chamber 186, wherein the pressurized ellipsoidal piston 217' (as described in Sections 2, 7, 653 and ι 966 of the present patent application) moves from the first longitudinal position 2000 (2〇) 〇3) To the first longitudinal position 2001 » at the first longitudinal position 2〇〇1, the piston 217' having been expanded into the piston 217 has a spherical shape while having a solid space of the enclosed space 21〇. The situation means that when the first longitudinal position 2 到达 is reached, the pressure inside the piston is reduced. The shape of the piston 217 can also be at the first longitudinal position, which is a round body (not shown), such as It is described and illustrated in Section 19660 of this patent application, and this situation will not affect the magnitude of the internal pressure of the piston 159900.doc 201235565. The position 2004 of the valve 126 does not change during this operation so that the volume of the enclosed space 210 remains unchanged. Arrow 2005 shows a stage below the operation shown in Figure 10B or Figure 10C (where the arrow is 2011). The piston 217 at the second longitudinal position, position 2025, wherein the wall of the chamber 186 is parallel to the central axis 184 at a position 2026 of the piston 217 at the first longitudinal position, wherein the wall of the chamber 186 is parallel to the center Axis 184. When in the first longitudinal position, the shape 2027 is the piston 217 in the event that the piston (delay) begins to decompress. The shape and size 2028 is the piston 217, which is approximately one-half of the return stroke, in which case the piston 217" has just emerged from the wall 185 of the chamber 186 (due to the delayed decompression when the piston 217 'When engaging the wall 185 of the chamber 186 (and not escaping the wall 185), the same shape and size 2028 of the piston 217' can be located closer to the second longitudinal position than when the piston 21 7" moves to the second longitudinal position Figure 10B shows valve 126, valve 126 has contracted from its position 2004 (2006) to a position further away from the piston 217. Enclosed space 21 0. The result is enclosed space 210 'The volume is greatly reduced, so that the internal pressure of the piston 217 becomes substantially the pressure at which the piston is produced (for example, atmospheric pressure), and the size and shape are substantially the piston in the second longitudinal position 2〇〇〇 but now unstressed The size and shape of the time, which means that when returning from the first longitudinal position 2〇〇^ (2008) to the second longitudinal position 2〇〇〇, the piston 217" may not engage and/or may engage the chamber 186 wall 185, but does not seal the cavity Wall 185 of 186. Wall 2024 of the piston. When the piston 217 moves from the first longitudinal position 2〇〇1 (2〇〇8) to the second longitudinal direction 159900.doc -145- 201235565 position 2000, it may be relatively slow The internal pressure drop is obtained such that the piston 21 7B can still have an ellipsoidal shape that is larger than the shape of the 217 at the second longitudinal position (10) during the movement such that the piston 2ΐ7β" engages and/or does not engage during the movement 2008 Wall 185. As a comparison: the situation is further away from the second longitudinal position when the piston is moved (2〇〇3) (sealed and/or meshed) from the second longitudinal position 2000 to the first longitudinal position 2001 The same size of the βH piston 2 1 7B" The pressure drop may also have been obtained at the first longitudinal position. When the piston 217", 217, returns to the second longitudinal position 2, the enclosed space 210 The position of the valve 126 in 'changed from 2007 to 2004 (arrow 2〇〇9), so that the enclosed space 21〇, again becomes the initial volume of FIG. 1A, so that the piston 217· has its initial Pressure. Arrow 2〇1〇展Figure 10 shows the next stage of operation shown by A Xin. Figure 10C shows an alternative solution for changing the internal pressure of the piston 217, and will be considered in conjunction with Figure 10A, in which case the valve bore 26 is lacking and modified. To allow for the presence of an entry/exit configuration 2020, for example, see Figures 210A through 210F (inclusive) and Figures 211A through 211F (inclusive) of Section 65 3 of this patent application. The pressurized piston 217' moves from the second longitudinal position 2000 (2003) to the first longitudinal position 2001, as described in Figure 10A, see above. No addition of fluid or removal of the Chiang fluid from the enclosed space 210 occurs. The arrow 2011 shows that the decompression in one stage of the piston 217'' shown in Fig. 10B is obtained by removing the necessary amount of fluid from the enclosed space 210: arrow 2020. When the piston 217 returns from the first longitudinal position 2001 (arrow 2021) to the second longitudinal position 2 〇〇〇 159900.doc - 146 - 201235565, sufficient fluid is added (arrow 2022) to the enclosed space 21〇 , thereby creating the piston 217 'arrow 2023 does not show the next stage shown in Figure 10A, resulting in the piston 217, the wall of the piston 2024 » should emphasize that the combination of the two techniques mentioned above can be used for pressure management of the piston Additional solution. It is also possible that the pressure drop from piston 217 or 2〇8 to / tongue plug 217 or 208" respectively can be a gradual pressure drop, for example, computerized, only the wall of chamber ι86 is engaged during the return of wall 2024 of the piston during return. 185 or under the condition that the wall 185 of the chamber 186 is not sprinkled at all. The wall 185 of the chamber 186 at the second longitudinal position and the first longitudinal position in the pattern i 〇 A 鲁 to 1 〇 F may not be parallel to the central axis. There are no channels shown in Figure 4, Figures 5A through 5E (included). The process shown in Fig. 10A, Fig. 10B or Fig. 10D, Fig. 10E (so-called E (enclosed) S (space) V (volume change) τ (technical)) is used for Fig. 1F, Fig. 11G (crank axis) And in the motor according to the invention shown in Figures 13F, 13A, 14A to 14D (inclusive) (rotation). Processes shown in Figures 10A, 10C or 10D, 10F and 210A through 210F (included) and Figures 211A through 211F (inclusive) (so-called C (consumption) T ( Technology)) for use in Figures ha to iid (inclusive) (crankshaft) and in Figures 12A to 12C (inclusive), Figures 13A to 13D (inclusive), according to the present invention In the motor. In Fig. 10D and Fig. 10E, a similar process as shown in Fig. iA, Fig. ιοΒ' differs in that the piston is a sphere type 208. In Fig. 10D, Fig. 10F, a similar process as shown in Fig. 10A, Fig. 1A, 'the difference is that the piston is a spherical type 2〇8. 159900.doc -147- 201235565 Figure 10G shows the BB section of Figure 12C (and the BB section can be partially seen in Figure 12A) and the motor in which the piston of the actuator piston chamber combination is moving while the chamber is not On the move. The motor includes a chamber 960 that includes four sub-chambers 961, 962, 963, and 964 that are each located continuously around the same central axis 965, respectively, with a chamber 960 having A shaft 966 passes through the center 967 of the chamber 960. Within the sub-chambers 961, 962, 963, and 964, respectively, a piston 968, the piston 968 is shown in two important positions, that is, at the first rotational position of the sub-chamber 964 (with maximum Position 968' at diameter) and position 968" at a second rotational position of subchamber 961 that is continuous with subchamber 964 such that the first rotational position of subchamber 964 is closest to The second rotational position of the subchamber 961 (in which the chamber has the smallest diameter). The actuator piston 968 rotates clockwise about the shaft 966, and there are four holes 970 shown for mounting the chamber 960 to the shaft 966. Figure 10H shows the B-B section of Figures 13A and 13B. The motor is of the type in which the chamber of the actuator piston chamber combination is moving and the piston is not moving. The motor includes a chamber 860 that includes four sub-chambers 861, 862, 863, and 864 that are continuously located around the same central axis 865, respectively, with a chamber 860 having A shaft 866 passes through the center 867 of the chamber 860. In the sub-chambers 861, 862, 863 and 864, there are five pistons 868, 869, 870, 871 and 872, respectively, and the five pistons 868, 869, 870, 871 and 872 are respectively positioned at one not 159900. .doc -148· 201235565 At the same rotational position, the sub-chambers 861, 862, 863 and 864 are at an angle α = 72 to each other. . Each piston includes a piston rod 873, 874, 875, 876, and 877, respectively. The pistons 868, 869, 870, 871, and 872 are of the "spherical sphere" type and are shown to have different diameters. The chamber 86 is rotated clockwise about the shaft 866 and the sub-chambers 861, 862, 863 and 864 have a second rotational position and a first rotational position in a clockwise direction of rotation, for the chamber The 860 is assembled with the four holes 878 shown on the shaft 866. The motor according to Figures 10G and 10 can include a chamber 860, at least a portion of which can be parallel to a central axis of the chamber (not shown). 19615 Revision - Regarding the pressure management system of Figures 11F, 13F and 13A, which depends on the system of the two-way actuator (for example, Figure UF References 1〇56 and 1〇57) 'When the change in direction can cause a loss of pressure Whether or not the repressurization system is necessary, this pressure loss may be caused by the "consumption" of the fluid (which may release the fluid to the atmosphere during the direction change) or may also be due to a pressure drop (see Figure 13E). The repressurization system is similar to the repressurization system shown in the previous figures (e.g., Figures 11A, 11B, and 12A). It is possible to develop a system that does not "consume" fluid and may only "consume" pressure. In these diagrams UF, Figure 13F, it is assumed that pressure is currently present so that only a specific volume of pressure reservoir May be necessary. The pressure should preferably be low (e.g., 10 to 15 bar) and high pressure (e.g., 300 bar) depending on the mud. The system can include a classic cylinder in which the two-way piston is located. On each side of the piston there is one of the cylinder inlets 159900.doc - 149 · 201235565 and the outlet so that the inlet valve on one side of the piston is in communication with the outlet valve at the other side. Therefore, the total on both sides of the piston

Source (for example, solar photovoltaic cells, * W body. Any pressure is consumed. It is used to control the electricity of the valves, and the accumulator can be connected to the main axle by continuous power, for example. Volt and / or generator) to charge. This situation reduces the amount of energy that this motor still needs. Assume that a pressure reservoir has been loaded while the motor is being produced. Instead of a two-way actuator, an electric stepper motor controlled by a computer can be used. This motor can react sufficiently accurately and quickly to the control pulses from the computer. Or 'here, the addition to the piston rod 8〇5 not shown in the container piston 81〇 in the container piston 810 can be used as described in the preferred embodiment of FIG. 11F shown in FIGS. 13F with reference to 1093 and 1094. Holes 'However, such holes have been shown in Figures 2B, 2C (reference 201) and should be present in Figure 11F. The addition to the piston rod 805 in the container piston 810 is not shown in the container piston 810 as described for the preferred embodiment of Figure 13F. However, such holes have been shown in Figures 1B and 1C (Ref. 201). And should be present in Figure 13F. With respect to the pressure management system of FIGS. 11A, 11B, and 11C, when the actuator piston is coupled to the spindle shaft by the crankshaft, the fluid in the piston of the pirate piston is decompressed and thereafter borrowed. The system is pressurized, wherein the two knives in the piston are sequentially connected and disconnected from the re-pressurizing pump and a pressure sump (Fig. 11A, Fig. 11B, Fig. 11β), and the following remarks are made.

Only: When the decelerating actuator piston is moved from the first to the longitudinal position to the second longitudinal position when reaching the pivot point at the farthest second longitudinal position, the pressure reservoir (eg, FIG. 11B, reference 314) Communicating with the actuator piston such that the piston is pressurized immediately when in the second, most longitudinal position. At that time d exists between the following (transiently) via two holes (one hole in the crankshaft and - the hole in the connecting rod). The pressure reservoir, via the crankshaft a confined space surrounding the enclosed space and the piston rod, and a hole in the piston rod in the container, the hole in the piston rod in the container continuously communicates between the space inside the container and the enclosed space . This situation means that during the stroke from the second longitudinal position to the first longitudinal position: the enclosed space of the piston has a temporary strange volume, in which case: 5 stomach: due to the increased volume of the container (From an ellipsoid having a smaller circumference to an ellipsoid/ellipsoidal sphere having a larger circumference/sphere having a small diameter to a sphere having a larger diameter), the inside of the container: the pressure continuously decreases as it moves. When the first longitudinal position is reached, the internal pressure of the Λ, ^ . y 谷 可 can be reduced, but may not become atmospheric. The sound & gamma value is the first longitudinal position of the daring, the return point before the return point _ at the back (four), # set, can be sent between the following: 纟以·. The container in the connecting rod: 0 Μ The hole 'passes the space between the two holes' and the first part of the crankshaft: I (the corresponding point between 159900.doc 151- 201235565) The core axis is such that one hole is in the connecting rod and the other hole is in the crank shaft. The pump is in communication with the second enclosure space and at that time, aspirate fluid from the vessel to depressurize the vessel. The second enclosure space can be constantly pressurized by constant open communication with the pressure reservoir. It is also possible to control this connection by means of a valve. Addition of the description of the preferred embodiment of Figures 11A, 11B, and 11C. The holes in the piston rod 8〇5 in the container piston 81〇 are not shown in the container piston 810, however, such holes have been shown in Figures 2B and 2C (refer to Figure 2A and should be present in Figure 11A, Figure 11B and Figure lie. The pressure management system of Figures 12A, 12B, 12C, ι3, and 13B is in the condition of a circular chamber (the chamber is a cavity having a central axis around) Similar to the same pressurization system mentioned in the crankshaft solution (Fig. ii A, Fig. i ^ B, Fig. UD), a similar solution can be effective in the round nine chambers, but it is adjusted and adjusted. In the moving piston and the non-moving chamber (Fig. 12A, Fig. 12B, Fig. 12), the spherical piston may include a confined space through which the perforated space can be The space inside the container is in communication, and at the other end, the enclosed space can be in communication with a second enclosed space that may be located in the screw. The last mentioned case may be in communication with a two-way valve in the housing, the housing Can be built around the rod ° separator valve can be T valve, the common part of the T valve and the second The enclosed space is connected. One of the non-shared parts can be connected to a pressure storage tank (eg 'Ref. 814) (high pressure) and the other of the non-shared parts 159900.doc -152- 201235565 (lower pressure) and The pump (eg, reference 818) is in communication. Control of opening and closing the minute valve can be performed by a computer that is opened by the enclosed space and a second enclosure in the spindle The position of the spindle shaft is monitored by comparing the opening of the space. The control can also be performed by a crankshaft that communicates with the spindle shaft, because in Figure 12A and Figure 2, the number of single = chambers is 4 in the spindle shaft. There should be 4 inlets/outlets to the second enclosed space, and there should also be 4 inlets/outlets to the helium valve, or there may be 4 valves. The valve (low pressure end) and pressure reservoir can be located ( For example, a pump (e.g., reference 818, 826) is added between reference 814) to raise the pressure a little above the pressure in the pressure reservoir. All of this configuration makes this solution less than optimal, for example, From the second enclosed space in the spindle The transition to the second enclosed space in the main shaft can cause leakage. In the case where the piston does not move and the chamber is moving (Fig. 13A, Fig. 13B), there may be, for example, 5 pistons, one sub-cavity a piston in the chamber, each having the same central circumferential axis, while all of the sub-chambers are continuously positioned with each other and in communication with each other. Each piston and a valve are moved with the piston above and the chamber is not The manners mentioned in the case of movement are connected in the same manner. The pressurization system can be similar, the only difference being that there are 5 τ valves, which can be opened/closed at different points in time. This is because the position of each piston in the same sub-chamber can be different. Instead of a piston pump, a centrifugal pump (Fig. 。) can be used. The efficiency of a centrifugal pump may be lower than the efficiency of a piston spring with a conical shaped chamber. The addition of the preferred embodiment of FIGS. 12A to 12C, 13A to 13F, 159900.doc-153.201235565, does not show the hole in the piston rod 805 in the container piston 810 in the container piston 810, however, These holes have been shown in Figures 1B, 1C (reference 201) and should be present in Figures 12A-12C, 13A-13F. Addition of the description of the preferred embodiment of Figure 12C. From 1074 to the return channel 11 50 of the pump 1151, the outlet is connected to the pressure reservoir 1075 by a passage 11 52 . Pump 1151 can be coupled (not shown) to spindle shaft 966 and/or to an external continuous energy source, such as solar energy (not shown). Addition of the description of the preferred embodiment of Figures 12A-12C (inclusive), Figures 13A-13F (inclusive). The holes in the piston rod 805 within the container piston 810 are not shown in the container piston 810, however, such holes have been shown in Figures 1B, 1C (reference 201) and should be present in Figures 12A-12C' Figure 13A To Figure 13F. Addition of the description of the preferred embodiment of Figures 13A, 13B, and 13E. The valve box 1160 includes 5x T valves 1161 through 1165 (inclusive) that are open to the following: from the pressure reservoir 814 via the piston rods 873, 874, 875, 876, 877 to the pistons 868, 869, 870, 871 The connection [829] of each of 872 (see Fig. 13C), or to the repressurization pump 818 and indirectly to the channel 826 [817]. The pressurized return passages [825] and/or [828] from the pumps to the pressure reservoir 889 are returned to 115 〇 from the inlet 74 to the pump 1151, and the outlet is connected to the pressure reservoir by the passage 1152. 1075. Pump 1151 can be coupled (not shown) to spindle shaft 966 and/or to an external continuous energy source, such as solar energy (not shown). Figure 11A schematically shows a total system for a ("green") motor, 159900.doc - 154 - 201235565 meeting all of the requirements as set forth in the [Prior Art] section of the present invention. On the illustrated crankshaft_, there is a u-shaped axle _, and the pumping rods 802 and 803, the anti-gravity is equipped with a piston rod 8〇5, on the other side of the piston cup 805, connected to Expansion piston _, expandable piston

On the left side, the L" is shown as moving from the first to the longitudinal position to the second longitudinal position (with arrow) _, and on the right side "Rj t is shown as moving from the second longitudinal position to the first longitudinal position (with In the middle of the arrow, the piston 806 can be spray-moved in the chamber m having the inner wall 8〇8. The chamber has a cross section with a continuous different cross-sectional area and a different circumference, and the chamber has an inner wall _ Having a circumference that is smaller than the first longitudinal position at the second longitudinal position. The piston 8〇6 is produced such that the circumferentially unstressed production is approximately 纟 at the second longitudinal position of the chamber. The size of the circumference of the wall 808. The piston 8〇6 is connected to the piston rod 805' by the cover 8〇9 and the flexible wall 81〇 of the piston 806 includes the reinforcing member 8ι, and by the slidable cover 812 Connected to the piston rod 8〇5, the slidable cover 812 is slidable over the piston rod 805. When the piston 8〇6 is at the second longitudinal position, and via the enclosed space 813 via the crankshaft 8〇〇 a second enclosed space 815 of the shaft 8〇1) and a pressure source (for example, The pressure reservoir 814) is in communication such that upon pressurization of the piston 806 by the fluid 822, the piston 8〇6 will begin to move from the second longitudinal position to the first longitudinal piston position, thereby causing the U-shaped shaft 801 Rotating around the bearings 802 and 803. This movement changes the direction of movement of the piston 8〇6 to the opposite direction, that is, from the first-longitudinal piston position to the second longitudinal piston position. The enclosed space of the piston 8〇6Η ] can then be connected to a third enclosed space 816 in the crankshaft 800 (shaft 801) 159900.doc - 155 - 201235565, the crank axle 800 (shaft 801) connected to the turbine via a channel [817] A piston pump 818 (which may also be a rotary pump, such as a centrifugal pump) is coupled to the crankshaft 820 (having a u-shaped shaft 821) by a piston rod 819. The crankshaft 820 can be coupled to a crankshaft 80〇, such that rotation of the u-shaped shaft 8〇1 causes rotation of the U-shaped shaft 821. Due to this communication, the pressure of the fluid 823 inside the piston 806 is reduced, so the circumference of the wall 808 is reduced. So that the piston 806 can be moved from the first longitudinal piston position to the second longitudinal piston The fluid 823 is at a reduced pressure (relative to the pressure of the fluid 822 when the piston is pressurized at the first longitudinal position), after which the fluid 822 is pressurized to fluid 827 by the thirsty wheel pump 818. (The pressure of fluid 827 is of course still less than the pressure of fluid 822) and the fluid 827 is delivered directly to the pressure reservoir 814 via passage [824], or preferably the fluid 827 is conveyed to the other via passage [825]. Piston pump 826, thereafter, pressurizes fluid 827 into fluid 822 in pump 826, and thereafter delivers fluid 822 to pressure reservoir 814 via passage [828]. Fluid 822 is delivered from pressure reservoir 814 to second enclosed space 815 via passage [829]. Piston pump 826 is electrically driven by motor 830 via another crankshaft 831. The motor 83A can be coupled to an electrical reservoir, such as an accumulator (or condensator or capacitator reservoir type) 832 that is coupled to the solar cell 833. The electric motor 830 can be used as a starter motor for rotating the crankshaft 800. This operation can be performed by a clutch 836 (not shown). The crankshaft 8A can be coupled to a flywheel 835 (not shown) and a gearbox 837 (not shown) that can use fluid dynamic bearings to reduce friction. A bearing 833 for the crankshaft 821 of the piston pump 818. The alternator 850 is in communication with the spindle rod 852 and is charged to the battery 832 via a connection 159900.doc • 156-201235565. The configuration of the auxiliary power source 85 is shown in Figure 15A, Figure 15B, Figure 15C or Figure 15E. Fig. 11B schematically shows a control device for the motor of Fig. ua. The electric starter motor 830 includes a clutch (not shown) that couples the shaft 803 to the anker of the electric motor when the starter motor is required. The electric switch 838 can turn the starter motor 830 on and off by connecting the starter motor 830 to a battery ("accumulator") 832. The battery ("accumulator" 832 is charged by the solar battery 832. . When the pressure in the pressure reservoir 814 meets a certain maximum limit, the motor 830 will also be stopped and the pressure management is performed by the pressure sensor 839. The motor can also be started without the use of the starter motor 830, but only by the pressure relief valve 840 in the open passage 829. Opening the pressure reducing valve 838 more causes the crankshaft 801 to rotate more rapidly, and tightening the pressure reducing valve 838 downward causes the crankshaft 801 to rotate more slowly. Closing the pressure relief valve 83 8 will completely stop the motor. The governor 841 is in communication with the pressure reducing valve 838. The alternator 85 is in communication with the spindle shaft 852 and charges the battery 832 via the connection. Configuration 851 of the auxiliary power source is shown in Figures 15A, 15B, 15C or 15E. Figures 11A through 11F (inclusive) focus on a motor having an elongated cylinder and a piston in communication with the crankshaft in accordance with a consumption technique. Figure 11C shows the actuator piston pressure management of Figures 11A and 11B. At the point in time when the piston reaches the final second longitudinal position from the first longitudinal position of the chamber, thus the second enclosed space of the compressed crankshaft is activated immediately after the direction of movement of the piston is reversed. 822 (via the hole in the crankshaft and the hole at the end of the piston rod) is connected to the enclosed space of the piston rod 159900.doc -157· 201235565 and thereby also activates the interior through the hole and the piston The communication between the volumes to pressurize the piston to the maximum pressure rating. Due to its pressurization, the piston will begin to move to the first longitudinal position' thereby rotating the crankshaft and closing the holes to stop the communication. This movement is attributed to the increased internal: The product reduces internal pressure due to the fact that: (4) The figure piston begins to transform itself into the shape of the sphere. When the 'longitudinal position' is reached, the medium pressure rating remains in the enclosed space within the piston and piston rod. When the piston first reaches the first longitudinal position on its way back to the second longitudinal position, the enclosing space in the piston rod will begin to pass through the end of the piston rod, therefore, immediately after reversing the direction of movement of the piston. The holes are in communication and the third enclosed space 823 in the crankshaft containing the holes is in communication. The pressure inside the piston and the enclosed space drops to a certain minimum value (e.g., atmospheric rating) such that the shape of the piston changes from a sphere to an ellipsoid. Due to the inertia of the crankshaft (or the driving force of another piston chamber combination using the same crankshaft), the deflated piston will move to the second longitudinal position and the process will all begin again. The communication between the enclosed space of the actuator piston and the second enclosed space and the third enclosed space in the crankshaft respectively may cause the piston to have to be stopped at a particular longitudinal position so as to be able to It is necessary to move the pressurized fluid only by opening the pressure reducing valve when it reaches the piston. The situation may be only a problem when there is only a uniform dynamic piston chamber combination on one of the crankshafts on a shaft, where the piston may stop at the first longitudinal position and may be due to inertia. Return a little on the way to the second longitudinal position. The holes of the enclosed space may not be able to communicate with each other, and the starting may be performed by using a starter motor only. 159900.doc -158· 201235565. The pressure drop in the piston can be caused by suction in the third enclosed space 823, caused by a piston pump 818 that absorbs fluid from the passage [817]. The pressure drop in the channel [817] may occur a little before the actuator piston has its direction of motion reversing from approaching the longitudinal position to the second longitudinal position, such that when enclosing the space and the third enclosed space When the holes are open, fluid can be drawn from the enclosed space of the actuator piston. In other instances, the preset angle between the crankshaft 801 of the actuator piston 810 and the crankshaft 821 of the piston pump 818 may differ from zero. Spindle rod 852. Figure 11D shows the assembly of the piston rod 8〇5 and the u-bend shaft 1 of Figure 11 and shown at a particular point in time with the piston rods 8〇5 and 1; the curved shaft 801 is rotated over each other. On the u-shaped bending shaft 8〇1, a piston rod 805, bearings 1100, 1100, and 11〇〇, and an O-ring 11〇4 between the piston rod 8〇5 and the shaft 8〇 are assembled. , 1104', 11〇4,, and 11〇4,,,. The enclosed space 813 communicates with the third enclosed space 816 (having a fluid 823) via a (pre-prepared) hole 11〇2. The second enclosed space 815 having the fluid 822 is in communication with the current blind hole n〇1 and is therefore currently not in communication with the enclosed space 813. A separator 11〇3 separates the second enclosed space 815 from the third enclosed space 816. At another point in time, the current hole 1102 becomes a blind hole, and the current blind hole 11〇1 becomes a hole. The hole such as the hole 1101 and 11 〇2 are not connected to the enclosed space 8丨3 at the same time. FIG. The details of the joint between the piston rod and the connecting rod are shown. Figure 11F shows the suspension of the crankshaft shown in Figures 11A and 11B and the details of the passage inside the crankshaft of the 159900.doc-159.201235565. Figures 11G through 11W (including) focus on a motor having at least a thin '9 / flying cylinder and a piston connected to a cam shaft according to the enclosed space "ESVT". Figure 11 (} and Figure 11H show the basic technique for the two variants of the pressure reservoir, which allows the pump that controls the enclosed space to be operated by a two-way actuator. Clearly, the difference is not the same. The power line separates the use of power generated by the auxiliary power source. Figures 111 and 1 show a cylinder motor and a two-cylinder motor, respectively, in which the main part of the motor has been made. The components to be constructed (for example, the shaft and, for example, the wheel) Groups and belts, the main structural elements are in communication with each other. The main pumps that control the volume of the enclosed space are respectively driven by actuators (Fig. UI, Fig. _, crankshaft (Fig. 11 Κ, Fig. 11L) or camshaft ( Figure 11Μ, Figure 11Ν) to supply power. Due to the different sizes of the rings, the type of power, the conical cylinders can have different sizes for each power type. The auxiliary power source is only referred to by reference numerals. Figure IIP and Figure UQ, Figure 11R (including) focus on the configuration of the respective map 11K, Figure 11L (crank axis) and Figure 11M, Figure 11N (camshaft), wherein the auxiliary power source is configured according to Figure 15x, wherein Combustion motor (its use, for example) The h2) generated by the electrolysis from the conductive Hao is directly in communication with the main pump that controls the volume of the enclosed space. The fact is that the combustion motor directly drives the power line (ESVT pump), the crankshaft/camshaft, instead of first generating the drive power. The electric motor 'this case means that the efficiency is 4 times efficiency. Each figure shows a different type of cooling for the combustion motor. The fluid heated by the combustion motor (eg 'air') can be used for force σ heat purposes, For example, for heating a personal compartment of a car. 159900.doc • 160 - 201235565 Figures 11S-11W (comprising) show specific details for several of the construction elements of Figures 11A through 11R (inclusive). Figure 11G Schematic The basic configuration of Fig. 11a is shown, which has a u-shaped shaft 801, a piston rod 805 and an expandable piston 806. One end of the shaft can be connected to an electric starter motor 830, and the electric starter motor 830 can be self-accumulating 832 obtains its energy 'The last mentioned case may be by solar cell 833 or any other preferred continuous (or optionally non-sustainable) power source. At the other end 'shaft 801 can be connected to Wheel 83 5 (not shown), clutch # 836 (not shown), and optionally gearbox 837 (not shown). The second enclosure space 822 is in constant communication with the actuator 1〇5〇. The actuator 1050 adjusts the pressure of the enclosed spaces 822, 805, and 823 by changing the volume of the sum of the enclosed spaces 822, 805, and 823 such that the piston changes volume according to Figures 10A through 10F. The pressure reducing valves 1〇51 and 1〇52 can control the speed and direction of the other actuator 1053 (the piston 1059, the chamber 1060) by the pressure reducing valves 及51 and 1052, and the other actuator 1053 controls Actuator 1050. The pressure reducing valves 1〇51 and 1〇52 control the Π〇54] by the rotational position of the shaft 801 so that the piston 8〇6 can expand and contract at the correct time point due to the pressure change. Pressure reducing valves 丨〇5丨 and 丨〇52 may be in communication with pressure source 890 [829], and pressure source 890 may have been pressurized by fluid 1063 when the motor is being produced. The other side of the enclosed space 815 can be in constant communication with the enclosed space 805 of the piston 806. The first enclosed space 823 is in constant communication with the actuator 1056, and the actuator 1〇56 adjusts the basic volume of the sum of the enclosed spaces 822, 815 and 823, thereby adjusting the speed of the motor. The enclosed space 805 is also constantly connected to the third enclosed space 823 159900.doc -161 - 201235565 and the third enclosed space 823 and the other actuator 1 〇 55 (piston 1061, chamber) 1〇62) Constantly connected. The function of this actuator 1055 controls the pressure adjustment of the sum of the enclosed spaces 822, 805 and 823. This adjustment sets the power of the motor. There is also another actuator 1056, which can control the position and speed of the actuator 1055. The pressure reducing valves 1〇57, 1〇58 can be connected to the governor 841. Pressure relief valves 1057, 1058 can be in communication with pressure reservoir 890 in the fluid [829]. The pressure relief valves 1052, 1058 can preferably be controlled by fluid 1063 and, as appropriate, electrically or electronically, and connected [1064] to the accumulator 832. Both actuators 1050 and 1055 can be of the type wherein the pistons 1059, 1061 can be sealingly moved in the chambers 1〇6〇, 1〇62, respectively, with a continuous change from the first longitudinal position to the second longitudinal position. The cross-sectional area of the cross-sectional area of the size 'the first longitudinal position is smaller than the cross-sectional area of the second longitudinal position. The connection of the control actuators 1050 and 1055 to the second enclosed space 822 and the third enclosed space 823 can be effectively protected from leakage by a stirrup ring. The parent current generator 850 is in communication with the spindle rod 852 and charges the battery 832 via the connection. The configuration 85 1 of the auxiliary power source is shown in Figure 15A, Figure 15B, Figure 15C or Figure 15E. Figure 11H shows the configuration of Figure 11G 'where the repressurization pump cascade for pressure reservoir 890 is shown' to repressurize the reservoir, and the repressurized pump cascade is cascaded with the pump shown in Figure 11A. the same. The alternator 85 is in communication with the main shaft 852 and charges the battery 832 via the connection. The configuration of the auxiliary power source 851 is shown in Figures 15A, 15B, 15C or 15E. The pump 831 can also be in communication with a flywheel (not shown) and/or a regenerative braking system (not shown). I59900.doc •162· 201235565 Figure 111 to Figure 11R (inclusive) show several configurations of a one-cylinder motor and two-cylinder motors. One of the objectives is to show a clear division of the delivered power and the power used, which is also schematically illustrated in Figure 15. Another goal is to show the difference between the pressure reconstruction of the actuator piston by the wire, by the camshaft or by the crankshaft, the wire, the camshaft and the crankshaft being connectable to the delivered power. In order to enhance the efficiency of the delivered power, Figs. 11A to 11R show a small combustion motor directly communicating with the camshaft or the crankshaft, which preferably uses H2 (derived from the electrolysis of Ηβ) as a power source. Several configurations of this combustion motor are shown. Another objective is to show how the control components of the pressure of each cylinder can be combined with or not incorporated into more than one cylinder motor. 'It is necessary to first find out how the subsequent cylinders will be related to each other under the condition of the crankshaft combined below. Work: See Figure 7A, Figure 17B to Figure 17H (inclusive) where the power stroke of one of the two cylinders of the same motor is simultaneously with the return stroke of the other cylinder (series power), while In Figures 18A through 18G (inclusive), the power strokes of the two cylinders of the same motor are running simultaneously (parallel power). Thereafter, it is inferred which pressure control members (eg, ESTV systems) can be combined for the two cylinders or which pressure control members (eg, ESTv pumps) are not combined, and whether the power lines can be combined (eg, camshafts, crankshafts) ). Figure 111 shows a partially made (8 〇〇) motor whose configuration is based on the configuration of Figure 11H. Only new issues will be dealt with here. An actuator 1〇55 (piston 1061, chamber 1〇62) that controls the speed of the motor is sealingly mounted (by a ring-shaped ring m〇) to the shaft 852 by bolts 1114, bolted to the bearing retainer 1112 and the main frame of this motor 5〇〇〇 (only 159900.doc -163· 201235565 is shown as a shadow). Bearing 1113 is mounted into bearing retainer 1112. The bearing and seal arrangements previously mentioned are located at the sides of the actuator centerline 1111. The top 1130 of the chamber 1062 of the actuator 1056 has been mounted to the motor main frame 5000. The configuration of the communication between the enclosed space 823 of the shaft 852 and the chamber 1062 can be seen in the figure where the actuator 1056 has been partially made, and the actuator 1056 includes a piston 1115 having two ring-shaped rings 1116. These last mentioned conditions are sealingly connected to the wall 1117 of the cylinder 1118. The pressure reducing valves 1057 and 1058 are related to each other in such a manner that when one valve is opened more, the other valve is simultaneously closed more. Spaces 1119 and 1120 in the cylinder 1118 are on either side of the piston 1115. The space 1119 and the space 1120 are in communication with the pressure reducing valve 1〇58 and the pressure reducing valve 1057, respectively. The chambers are additionally in communication with one another via a valve actuator arrangement 1121 and 1122, respectively, shown in Figure 304, and if necessary, the chambers are additionally controlled according to Figure 211E or Figure 211F. The valve actuator arrangement 1121 and the valve actuator arrangement 1122 are located in opposite directions from one another. The chamber 1118 of the actuator 1056 has been mounted to the motor main frame 5A. More details can be found in the picture. The actuator 1050 is sealingly and rotatably coupled to the main draw rod 852, and the actuator 1050 is sealingly mounted (by the stirrup ring 23) to the shaft 852 by bolts 1124. The bolt 1124 is coupled to the bearing retainer 1125 and The main frame of this motor 5000 (shown only as a shadow). Bearing 1126 is mounted to bearing retainer 1125. The bearing and seal configurations previously mentioned are located at the sides of the actuator centerline 1133. See Figure 11V for a detailed suspension of the actuator 1050. The configuration of the communication between the enclosed space 822 of the shaft 852 and the chamber 1〇6〇 can be found in Figure 159900.doc • 164 - 201235565. Instead of actuator 1053 and pressure relief valves 1051 and 1052, the actuator 1050 is powered using a separate crankshaft 1128 by controlling the connection to vapor red (800) [1054]. The timing is controlled via a synchronous toothed belt 1129. The timing belt 1129 is coupled to the shaft 852 via a crank axle pulley 1130 mounted on the shaft 852 via a crank axle pulley 1131. The axle 1132 includes the crank axle 1128. The timing toothed belt 1129 includes teeth (preferably flad) to avoid slippage (and thus change timing). The shaft 1132 is rotatably mounted in the motor main frame 5000 (not shown). Figure 11J shows a two-cylinder motor that is not based on the portion of Figure 111, which shows the specific details of combining two crankshafts and has the benefit of a construction element for multiple similar tasks. In the two-cylinder motor, there are not many cases mentioned last time. This is because the two pistons are not selected in the same longitudinal position at the same time. In other instances, the control of each governor actuator and/or ESTV pump for each of the two cylinders can be interconnected. There may be only one pump for repressurization purposes. First of all, when there are 3 or better 4 and even 4 or more cylinders in a Ma Yuda,

There are opportunities to combine the inlet/outlet of the governor actuator with the inlet/exit of the ESTV pump so that the total number of actuators and pumps can be reduced /J, Figure 11J shows a two-cylinder motor' Each of the two actuator pistons operates in an elongated π cylinder, each using a crankshaft on one of the main motor shafts, 90 relative to each other. In position, the crankshafts are coupled to each other, each crankshaft including a confined space spaced apart from each other and continuously in communication with each of the pistons 159900.doc-165-201235565. The governor is used to drive a two-way actuator piston, wherein the control of each governor is in communication with each other. The ESTV pumps (each piston-ESTV pump) each use a two-way actuator piston, and the control of the pumps is in communication with each other. The two-way actuators are powered by a pressurized fluid that is held under pressure by a pressure reservoir. The sump is pressurized by a pump that is powered by an electric motor. The motor is powered by a "continuous" battery that is powered by an auxiliary power source: see Figure 15A. 15B, 15C, 15E, and 15F. The two crankshafts on the main motor shaft are connected to each other by a connector that can be slightly flexible 'to compensate for the timing difference of the shape of the actuator pistons (attributed) Repressurization of the pistons). The left side of Figure 11J shows the proportionally enlarged left side of Figure 11J. The right side of Figure 11J is shown on the right side of Figure 11J. Figure 11K shows a cylinder motor 'which uses a crankshaft for driving the estv pump' while the governor still uses the actuator piston. Figure 11L shows a two cylinder motor using a combined crankshaft for each of the ESTV pumps, with the control of each of the governors being in communication with one another. The left side of Figure 11L is shown on the left side of Figure L. The right side of Figure 11 is shown on the right side of Figure 11L. The figure shows a cylinder motor based on the concept of the concept shown in Figure 11H, wherein the ESvt pump for the actuator piston chamber combination is now powered by a camshaft by means of a camshaft The battery-powered electric motor drives the 'rate controller' to be a two-way 159900.doc-166-201235565 actuator that communicates with the governor. The pump for repressurizing the pressure reservoir is powered by a separate electric motor powered by a battery; the auxiliary power source is according to Figures 15A, 15B, 15C, 15E, 15F, etc. At least one of the sources can charge the batteries. Figure 11N shows a two cylinder motor based on the portion of Figure 11M with a camshaft for the ESVT pump' a camshaft for each actuator piston chamber junction. The dedicated rate control benefit (per 'actuator piston-rate controller) is in communication with each other; the pump for repressurizing the pressure reservoir is powered by a separate electric motor powered by a battery; auxiliary power source According to Figures 15A, 15B, 15C, 15E, 15F, at least one of the power sources can charge the batteries. The left side of Fig. 11N shows a scaled up view of the left portion of Fig. 1N. The right side of Fig. 1N shows a scaled up view of the right portion of Fig. 1N. Figure 11 shows a cylinder motor based on the concept of the concept shown in Figure 11K, wherein the ESVT pump of the actuator piston chamber is powered by a crankshaft directly from the gas ( For example, the air) cooling combustion motor (using the Η" electrolysis obtained by electrolysis) is driven by the auxiliary power; the pump that repressurizes the pressure reservoir is additionally directly used by the combustion motor The speed controller is powered by a two-way actuator powered by a battery; the battery according to Figure (10) is charged by an alternator mounted on the main motor shaft. The heat generated by the combustion motor can be used, for example, to heat the interior of the vehicle. Figure IIP shows a two-cylinder motor based on the section of Figure 11 where the ESVT pumps (each actuator piston chamber έ 丞 丞 至 至 结合 结合 结合 结合 ES ES ES ES ES 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 159 The crankshaft is powered by a crankshaft that is driven directly by an auxiliary power from a forced liquid-cooled combustion motor (using h2 obtained by electrolysis of H2, which is powered by a battery); The repressurized pump is directly driven by the combustion motor; the rate controllers (each actuator piston chamber combined with a rate controller) are powered by a two-way actuator, such The rate controllers are in communication with one another and are powered by a battery; the battery according to Figure 15D is charged by an alternator mounted on the main motor shaft. The heat generated by the combustion motor can be used, for example, to heat the interior of the carrier.

I. The left side of Figure 11P shows a scaled up view of the left part of Figure 11 p. The right side of Fig. 11P shows a scaled up view of the right portion of Fig. 11P. Figure 11Q shows a cylinder motor based on the portion of the concept shown in Figure ι, wherein the ESvT pump of the actuator piston chamber combination is powered by a camshaft that is directly forced by the camshaft A gas (such as an 'air) cools the combustion motor (using H2 obtained by electrolysis of H2, which is powered by a battery) to drive; the pump that repressurizes the pressure reservoir directly uses the combustion The motor is driven; the rate controller is powered by a two-way actuator powered by a battery; the battery according to Figure 15D is powered by an alternator mounted on the main motor shaft

To charge. The heat generated by the combustion motor can be used, for example, to heat the interior of the carrier. β N Figure 11R shows a two-cylinder motor based on the portion of Figure 11Q, wherein the ESVT pumps (each actuator piston chamber combination) The Esvt pump is powered by a camshaft that is forced to cool the combustion motor directly from the gas (eg, 159900.doc -168-201235565 eg air) (using the & The electrolysis system is driven by the auxiliary power of the battery; the pump for repressurizing the pressure storage tank is directly driven by the combustion motor; and the rate controller (each actuator piston chamber assembly 1) The rate controller is powered by a two-way actuator that is in communication with each other and powered by a battery; the battery according to Figure 15D is connected by an alternating current mounted on the main motor shaft The motor is charged. The heat generated by the combustion motor can be used, for example, to heat the interior of the carrier. The left side of Fig. 11R shows a scaled up view of the left portion of Fig. 11r. The right side of Fig. 11R shows a scaled up view of the right portion of Fig. 11r. Fig. 11S shows details of the joint of the base of the piston chamber assembly 1〇61 of Fig. 11 to Fig. 11R with the spindle shaft of the motor. Figure 11T shows details of the joint of the connecting rod of the actuator piston according to Figures UI through 11R with the crank shaft on the spindle shaft of the motor. Fig. 11U shows details of the joint of the base of the piston chamber assembly 1〇6〇 of Fig. 11 to Fig. 11R with the spindle shaft of the motor. Figure 11V shows the mechanism for driving the pump of Figures 11H through 11R and its base. Figure 11w shows the connection joint between the two crankshafts of the flying cylinder motor according to Figs. 11J, 11L, 11N, IIP, and Fig. 11R. Instead of the toothed belt at the power side of the motor according to Figs. 11D to 11W, the pump is driven, and the geared belts can be exchanged very well with gears. Figure 12A shows a configuration 800 of the motor according to Figure 11B, wherein the piston chamber combination is connected via a crankshaft with a spindle rod, and in this figure, the configuration 8' is replaced with configuration 800', configuration 8〇〇, comprising a fixed chamber, wherein 159900.doc • 169·201235565 The piston rotates clockwise according to FIG. 10A or FIG. 12B, and wherein the suspension of the piston is shown in FIG. 12C. A "black box" is shown which is used to communicate with the inlet of the waste reducing valve 840 via the passage [..] and is used to achieve a pressure reducing valve via the passage [81 7] to the outlet of the pump 818. The 840 is controlled by the governor 841. Figure 12B shows the motor 'where the actuator piston chamber assembly is moving" while the chamber is not moving. The motor includes a chamber 96A, and the chamber 96A includes four sub-chambers 961, 962, 963, and 964, which are respectively located continuously around the same central axis 965, respectively. Chamber 960 has a shaft 966 that passes through the center 967 of the chamber 960. In the sub-chambers 961, 962, 963 and 964, respectively! Piston 968, which is shown in two important positions, namely, position 968 at a first rotational position of sub-chamber 964 (having the largest diameter), and is in a continuous position with sub-chamber 964 Position 968" at the second rotational position of subchamber 961 such that the first rotational position of subchamber 964 is located at a second rotational position closest to subchamber 961 (in which the chamber has Minimum diameter). The actuator piston 968 rotates clockwise about the shaft 966, and there are four holes 967 shown for mounting the chamber 960 on the shaft 966. Figure 12C (consumption) shows the alpha·α of Figure 12B. A cross section, which has a non-movable chamber 960, and a movable living room s cut, Guji 968 and 968,. The enclosed space iQ7 of the pistons 968, 968, · (the same piston of two different sizes) is called at the shaft (10) where the enclosed space 1〇7〇 is deleted by being located in the enclosed space The two ring-shaped rings 1071 on both sides are sealed. The enclosed space is in communication with the second enclosed space 1072 of the shaft 966 159900.doc 201235565, wherein the second enclosed space 1072 terminates in the outer casing 1073, wherein the T valve 1074 is present, and the T valve 1074 is controlled. The entry from the pressure reservoir 8丨4 via the passage [829] and the fluid 822 of the pressure relief valve 840. This fluid 822 controls the internal pressure of the pistons 968' and 968'. From these pistons 968' and 968', the exit is via the channel [817] to the cascade of pumps (rotational translation). The electrical signal 1076 is in communication with the electrical/electronic control unit 1A 77, and the electrical/electronic control unit 1077 controls the τ valve ι 741 in the housing 1〇73 via the signal [1〇78]. Rotation of the shaft 966 thereby controls the damper valve 〇74, and thus the pressure in the pistons 968, 968''. Signal [891] is from pressure source 1〇75 to control unit 1〇77. The flange 1079 connects the chamber 960 to the suspension 1〇80, and the suspension 1〇8〇 is mounted to the shaft 966. With 1〇81. There may be a pump, such as, for example, Reference Up and/or 8261 of Figure UB, but not shown in this figure, the pump is in communication with the pressure source (7). The pump can be in communication with the shaft 966. The pump can also be in communication with the flywheel and/or regenerative braking system 1082. Figure 12D (enclosed space) shows the AA section of Figure 12B with the immovable chamber 960, and the movable pistons 968, and 968,. The piston, 968" enclosed space 1〇7〇 terminates at the shaft where the enclosed space is divided by two. Sealed by a ring. The enclosed space 1〇7〇 communicates with the shaft %: the second enclosed space 1072 in which the second enclosed space assists in the outer casing, wherein the piston chamber is combined, the piston chamber The combination urn controls the pistons 968, and 968, (two different sized internal forces of the same size. The piston chamber combination can be combined with the fluid 889 of the power source 1075 via the (10) 。. 159900.doc • 171· 201235565 The electrical signal [1076] is in communication with the electrical/electronic control unit i〇77, and the electrical/electronic control unit 1077 controls the piston chamber assembly 1074 within the housing 1073 via signal [1078]. The rotation of the shaft 966 thereby controls the piston The chamber combines the body 1074, and thus the force in the piston 968', 968". The signal [891] from the pressure source 1075 to the control unit 1 〇 77. has a fluid with a reduced pressure (relative to the fluid 889 The return channel 1〇5〇 is returned to the power source 1075 via the chestnut cascade repressurization system (translation and/or rotary pump) (see Figure 12A). The pump 1151. The flange 1079 connects the chamber 960 to The suspension is 1〇8〇, and the suspension 1〇8〇 is mounted on the shaft 966” belt 1081. There is a pump, such as, for example, reference 82A and/or 826' of Figure 13B, but not shown in this figure, the pump is in communication with a pressure source 1 〇 75. The pump can be in communication with a shaft 966. The pump can also The flywheel and/or regenerative braking system 1082 is in communication. The motor according to Figures 12A and 12B can include a chamber 960, at least a portion of which can be parallel to a central axis of the chamber (not shown). The motor shown in Fig. 10, wherein the crankshaft arrangement 800 is exchanged with the rotary motor of Fig. 10A. Fig. 13A shows the motor of Fig. 13 wherein the piston pumps 818 and 826 are exchanged by a rotary pump (e.g., centrifuged fruits 821' and 826). Figure 13C shows the BB section of Figure 13B, and the motor is of the type in which the chamber of the actuator piston chamber combination is moving and the piston is not moving. The motor comprises a chamber 860 comprising four sub-chambers The chambers 861, 862, 863 and 864 are respectively located continuously around the same central axis 865 with respect to each other, and the chamber 860 has a chamber 860 through the 159900.doc -172· 201235565 Center shaft 867 shaft 866. In the son In chambers 861, 862, 863, and 864, there are five pistons 868, 869, 870, 871, and 872, and the five pistons 868, 869, 870, 871, and 872 are each located at a different rotational position. The sub-chambers 861, 862, 863, and 864 are at an angle α = 72 to each other. . Each piston includes a piston rod 873, 874, 875, 876, and 877, respectively. Pistons 868, 869, 870, 871, and 872 are of the "spherical sphere" type and are shown to have different diameters. The chamber 860 rotates counterclockwise about the shaft 866 and the sub-chambers 861, 862, 863 and 864 have a second rotational position in a clockwise direction of rotation and a first rotational position 'is present for the chamber 860 Four holes 878 are shown mounted on the shaft 866. Figure 13D shows the Α-Α cross section of Figure 13C. The chamber 860 has a slit 879 surrounding the flange 861 of the chamber 860, wherein the strip 883 can be mounted in the slit 879. The chamber 860 is mounted on the shaft 866, and the shaft 866 has a flange 880 due to the recesses. The piston rods 873, 874, 875, 876 and 877 are fitted inside the outer casing 882. Fig. 13A shows a cross section C-C' of Fig. 13A and another cross section of the outer casing 882 in the view. Piston rods 872, 873, 874, 875, 876 are coupled to a pressure distribution center 884, wherein each piston is coupled to a computer 885 operated pressure relief valve system 8 8 6 'the pressure relief valve system 8 8 6 is given to the piston rods The necessary pressure for each of them, signal 887 gives the rotational position of the shaft 866 to the computer 885, and the computer 885 determines the pressure of each of the pistons by signal 888. The pressure to the piston rods 872, 873, 874, 875, 876 is controlled by the passage 890 from the pressure reservoir 889' and by the signal 891 to the computer 885. The fluctuating pressure changes in the enclosed space of each piston are handled by 159900.doc • 173-201235565, respectively, and are adjusted electronically by the same computer 885 for each piston. There may be a pump (e.g., reference 821, and/or 826 of Figure 13B), but not shown in this figure, the pump is in communication with a pressure source 1〇75. The pump can be in communication with the shaft 966. The pump can also be connected to a flywheel and/or a regenerative braking system. Figure 13F unintentionally shows an alternative solution for a motor repressurization system that now resembles the repressurization system of Figure 1F. Each enclosed space (e.g., 1 〇 9 〇) of each piston is in communication with a piston chamber combination 873, 872, 874, 876, 875, and the piston chamber assembly 873 includes an actuator piston 1091. The position of the actuator piston 1〇91 in the chamber 1〇92 is controlled by the position of the cam wheel set 1093, the cam wheel set 1〇93 can flip the cam 1094' and the cam 1〇93 is mounted on the shaft 866. Note: Cams and wheels are shown schematically as 'this is because each wheel set should have a different distance to one of its associated pistons, and the wheel set should be displayed laterally (partially). The pressure inside the enclosed space 1090 can be adjusted by: another piston chamber combination 1055 (which is similar to 1055 from Figure 11F), and another control actuator 1056 (e.g., 1056). And pressure reducing valves 1〇57' and 1058' (such as 1057, 105 8), while the other governor 84Γ (such as 841). The pressure reservoir 889 is in communication with the pressure reducing valves 1057, and 1058 [1095]. There may be a pump (e.g., reference 821, and/or 826 of Figure 13B), but this drawing has not been shown 'the pump is in communication with the pressure source 1075. The pump can be in communication with the shaft 966. The pump can also be connected to a flywheel and/or regenerative braking system. The motor according to Figures 13A, 13B and 13C can include a chamber 860, at least a portion of which can be parallel to a central axis of the chamber (not shown). 159900.doc • 174- 201235565 FIG. 4A shows the change in pressure and magnitude of the actuator piston woo located in the chamber 17〇1, the chamber 1701 having a central axis 1702, and a piston 17 mounted on the piston rod 1704. 3 (when moving from the second longitudinal/second circular position I· to the first longitudinal/first circular position 17〇6). The actuator piston 1 has been pressurized to, for example, a force of 2 bar at the second longitudinal/second circular position 1705. The piston 1700 includes a confined space 17〇7, and the enclosed space 17〇7 includes a pump portion 1708. The pump portion 17〇8 of the enclosed space 17〇7 and the rest of the enclosed space 1707 are separated by the piston 17〇3 when the actuator appeals the piston 1700 in the second longitudinal/second circular position Π05 has been pressurized to 3 k above and until the pressure is reduced to (for example) V2 bar when moving from the first longitudinal/first circular position 17〇6, the actuator piston 17〇9 is The first longitudinal/first circular position now has a much larger diameter than the piston at the second longitudinal/second circular position 1705. To deflate the actuator piston 17〇5 to atmospheric pressure (position 1713), wherein the piston 17〇3 is contracted away from the actuator piston 1709 in the event that the crankshaft returns toward the second longitudinal position. : Move 1710) and release % Baru overpressure in the enclosed space 17〇7. The diameter of the actuator piston 1711 is increased to a production size that is slightly smaller than the diameter of the actuator piston 1700, which is within the cavity to the wall (not shown in this figure). The two longitudinal positions 1705 have been pressurized to 3" 2 bar. The piston 1703 is further retracted (moved 1712) away from the actuator piston 1711 such that a pump stroke 1716 toward the second longitudinal position 1714 can occur, pressurizing the actuator piston to 37/2 bar, when in the crank In the condition of the shaft, the actuator piston returns to the first longitudinal position (1715). 159900.doc • 175· 201235565 FIG. 14B schematically illustrates the process of FIG. 14A over time, and the process is shown in sub-chamber 1720, which is positioned around the central axis 1721 around the central axis 1721. The line extends, and the other is the timeline. The subchamber 1720 typically moves in the direction of arrow 1740, while the actuator piston 1 722 is not moving. However, in this figure, the subchamber is not moving and the piston 1720 is moving. The piston 1722 is located at the second longitudinal/circular position and the fluid 1723 inside the actuator piston has been pressurized to (e.g., 372 bar). Pump 1724 includes a piston 1725, a piston rod 1726, a chamber 1727, and a cam wheel set 1728. The cam wheel set 1728 is placed on the cam surface 1729^. The piston 1725 is positioned at a second longitudinal position (1730) of the pump 1724. When the actuator piston 1722 moves from the second longitudinal/circular position to the first longitudinal/circular position in the sub-chamber 1720, the position of the piston 1725 remains unchanged, wherein the pressure of the fluid 1723 is reduced to 72. Bar (actuator piston 173 2). When cam surface 1729 maintains its height, cam wheel set surface 1728 remains in its position. Retracting the piston 1725 from position (1730) to position (1731) gives the actuator piston 1733 an internal pressure (overpressure) and reduces its diameter to its production size. This situation is the result of the following operation: _ Cam surface 1729 tilts cam surface 1734 at an angle a relative to cam surface 1729 such that cam wheel set 1728 becomes further away from the actuator piston 1733. Cam wheel set 1738. Thereafter, the translation of the cam wheel assembly port is directly returned at the end point 173 5 and returned to the actuator piston 1733, which further turns to the actuator piston 1736. When the cam wheel set 173 8 returns to the initial surface 丨 729, over the inclined cam surface 丨 739, the inclined cam surface 1739 has an angle β (> 90.) to the cam surface 1729. I59900.doc

• 176- 201235565 The actuator piston 1737 belongs to this position of the cam wheel set 1728. It should be emphasized that the reduction in the diameter of the actuator piston can be stepped during a very small period of time to keep the actuator piston in contact with the wall 1740 of the chamber 1 720. Figure 14C shows the configuration of Figure 14B, which enables the injection of the beta cam wheel set 1740 in the fluid to actuator piston when the actuator piston is in the second circular position, now flipping the hose 1741, the hose 1741 The chamber 1744 includes a wall 1742, and a fluid or fluid mixture 1743. The hose 1741 has an outlet 1745 to the enclosed space 17 46 of the actuator piston 1747 that is temporarily closed and only when the actuator piston 1747 is in the second position (Fig. 14β reference numeral 173 7) The enclosed space 1746 of the actuator piston 1747 is open, wherein the fluid in the hose 1741 can be repressurized. The description of Figure 14D1 shows a classic pump. Figure 14D1 shows a chamber 1749 in a wheel set 1751 having a central axis 1750 with the wheel set 1751 rotating counterclockwise about the shaft 1752, the shaft 1752 being fitted with a roller bearing 1753. The chamber contains four identical sub-chambers 1754, 1755, 1756 and 1757. The passage 1750 includes five fixed identical pistons 1758, 1759, 1760, 1761, and 1762, each of which has a different diameter and internal pressure at a different circular position from each other. Each piston has a pump portion 1763, 1764, 1765, 1766, and 1767 that is fixed to each of the pistons 1758, 1759, 1760, 1761, and 1762. In the center. Each of the pumps has a piston rod 1768, 1769, 1770, 1771, and 1772'. The piston rods 1768, 1769, 1770, 1771, and 1772 are contained above a camshaft 1778 of 159900.doc-177.201235565. One of the cam wheel sets 1773, 1774, 1775, 1 776 and 1 777 is operated. The camshaft 1 778 includes four identical lower portions 1779, 1780, 1781 and 1782, wherein one of the pistons 1758, 1759, 1760, 1761 and 1762 needs to be repressurized and only before a piston needs to be repressurized. Actuator piston 1761 shows the use of the lower portion of the pump (dashed line 1761'). Figure 14D2 shows an elongated conical pump instead of a pump with an inline cylinder. Figure 14E shows a section of the rim with its suspension on the disc brake plate mounted on the chamber housing with a circular cavity in the chamber housing to 'show in section' where the group according to Figure 14D State, the spherical piston is in the first circular position. The interior of the piston is in communication with a confined space that is mounted in a housing that is itself mounted on a portion of the carrier frame. The size of the enclosed space is adjusted by a pump having a conical chamber with the end of the conical chamber running above the cam profile. The cam profile is driven by an auxiliary electric motor that rotates the cam and rotates about the same main motor shaft independently of the motor. A roller bearing for the chamber suspension on the main motor shaft and a roller bearing for the cam profile are shown. "The main motor shaft is also mounted on the carrier frame. The pressure controller ("by wire drive") according to the configuration of Figure 16 is connected to a passage containing the enclosed space of the actuator piston, which is in communication with a governor located at the distal end. Figure 14F shows an enlarged detail of a section of the piston in the first circular chamber of Figure 14E. The piston (having a wall having a reinforcement according to Figures 2A, 8a, 208F or 209A to 209C) (for example, by sulfur 159900.doc -178 - 201235565) on the piston rod On the fixed end (left side) and the movable end (right side), the piston can slide slidingly on the piston rod. The piston rod is slidably sealed in a cylinder t mounted in the housing (see Fig. 14G), and the housing is mounted on the carrier frame. This sliding makes it possible to adapt the position of the piston so that it is at the center of the section of the chamber (at all circular positions). Figure 14G shows an enlarged detail of a section of the piston in the circular chamber of Figure 14G when the piston is in the second circular position. Figure 14H shows the configuration of Figure 14E with a gearbox (e.g., planetary gear type) built into the rim of the wheel set and between the brake plate and the circular chamber. Figures 15A-15E show several auxiliary power sources that work with the motor. Carefully choose the power line. Figure 15A shows an h2 fuel cell that delivers electricity to a motor that drives an ESvt pump. Although today (February 2011) this solution is extremely costly, the following information is available on the Carbon Trust web site, and there is a technological breakthrough that makes it possible to use Hz fuel cells in automotive motors in the future. Another difficulty is that the storage of H2 is difficult and energy unfriendly. Figure 15B shows a solution to the & storage problem solution, because Η; 2 is stored as & and via electrolysis And detached. Since the feasibility study shows that the current energy is required to be lower than 丨〇〇/q to drive, for example, a car, a Η2〇 alternator is generated and used in a combustible motor that can cause rotation to generate an electric 'electric drive electric motor to drive ¥1' pump. The problem here is that the last mentioned process has an efficiency of only 25%. The 〇2, which is detached at the electrolysis of the conductive HaO, can be used in a combustible motor, so that the combustion is still more efficient (turbo effect) 159900.doc -179- 201235565 。. The H2 脱离 which is detached from the combustion process in the combustible motor can be reused to obtain h2 ^ ° by electrolysis. Figure 15 C shows that the process of supplying hydrogen by the current supply is 1 〇 〇% An effective and much smaller crankshaft directly drives the ESVT pump solution with the shaft of the combustible motor. Figure 15D shows an equivalent solution as in Figure 15C in which the crankshaft has been exchanged by a rotating ESVT pump, which makes the process still more efficient. Here H2 is derived from both electrolysis and solar voltaic cells. Figure 15E shows a solution for a large capacitor used as a power source for an ESVT pump. The big advantage is that the electric grid can be charged in a few minutes, and in the case of capacitors and suitcases, the car can travel for example 5 km. Figure 15A schematically shows a tank 1600 of H2 (1601) that can be cooled using electricity via electrical communication [1602] and that has been connected to the exterior (1604) of the motor by the tank 16〇〇 The channel [1603] is full. The tank 16 is connected to the % fuel cell 1606 via a channel [1605], wherein H2 is converted to power the starter battery 832B (short term, high current) or service battery 832C (long term, medium current) via electrical communication [1607] Electricity. This channel [16〇5] contains a one-way valve 1608 (not shown). The starter battery 83 2B is in electrical communication with the starter motor 830 [1609], and the service battery 832C is in electrical communication with the pump 826 of the motor [1610] » the motor further includes a pressure tank 814 in communication with the pump 826 and with the piston actuator arrangement 800 . The spindle shaft 852 of the motor is in communication with an actuator 850 that charges the service battery 832A (long-term, medium current) via electrical communication [1611]. The battery is in electrical communication with the cooling of the can 1600 [1602]. Battery 832A through battery 832C (inclusive) is referred to as a single block having reference numeral 832 and is self-operating charged in other figures of this patent application by 159900.doc .180-201235565. The solar volt battery 833 additionally charges the battery 832. A pressure reservoir 814 is inflated by pump 820/826. The piston actuator module of the motor is 8 turns. Figure 15B schematically shows a (conductive) H2(R) (16U) canister 1612 that has been filled with a channel [1614] that connects the canister 1612 to the exterior (1604) of the motor. The tank 1612 is connected via a passage [1615] to a tank 1616 where the electrolysis 1617 of the water (1613) occurs. The outlet [1622] of the slot 1616 is in communication with the combustion motor 1620. The combustion motor 1620 is in communication with its spindle rod 1621. The Lu channel [1622] includes a one-way valve 1618 (not shown, the motor 1620 burns H2 generated in the slot 1605, causing motion - here the rotation of the shaft i 62. The shaft 1621 is electrically The starter motor 1623 is in communication with the alternator 1624. The alternator 1624 charges the battery 832B (high current, short term) for the starter motor 1623 or the battery 832C (medium current, long term). The main shaft 852 is in electrical communication 1625. The battery 832A (ten-high current, long-term) is charged by the alternator 850. The battery 832A is powered via electrical connection [1626] for electrolysis 1616 in the slot 1616. Battery 832C imparts power to the pump 826 via the electrical communication [1627], while battery 832B respectively imparts power to the starter motors 1623 and 830 via electrical communication [1628]. The batteries (832) have been self-operating charged. Photovoltaic battery 833, which additionally charges battery 832. Pressure reservoir 814 is inflated by pump 820/826. Battery. Motor piston actuator module 800. Battery has up to Figures 11A, 11B, 11C, FIG. 11F, FIG. 11G and FIG. 12A and FIG. 13A, FIG. 13B are output electrical connections according to other functions of the motor of function 851 159900.doc •181· 201235565 in the drawings [1614]. Self-fuel cell The bypass [1616] to the output electrical connection [1614] directly imparts power to the functions. Figure 15C schematically shows the process of repressurizing the pump cascade 826 or 83 1 in accordance with the process of Figure 15B. The pump 1625 is additionally in direct communication with the spindle shaft 1623 of the combustible motor 1620 via a crankshaft 1624 and a piston rod 1626. In addition to the alternator 850 in communication with the spindle rod 1623, the photovoltaic solar cell 833 also charges the battery 832. 832 is electrically coupled to the motor via electrical communication [1614]. The outlet of pump 1625 of motor function 826 is in communication with the motor according to Figures 11A, 11B, 11C, 11F, 11G or 12A, 13A, 13B. The inlet 1623 of the pump 1625. The starter motor 830. Figure 15D schematically shows, in principle, the equivalent process of the process of Figure 15C where the piston pump 1 625 has been exchanged by a rotating system 1627 by means of a shaft 1628 The motor 1620 is connected The rotary pump 1627 is in communication with the motor function 800", motor function 82A via passage [825] and is in communication with the pressure reservoir 814 of Figure 13B via passage [828]. The starter motor 830 is in communication with the shaft 1628' and via Wire [1642] derives its power from battery 832. The battery 832 is charged via the wire [1641] by the photo solar cell 833' and the alternator 850 and is in communication with the shaft 1628. The battery 83 2 is connected to the motor function 800" and the motor function 820 by wires [1629]. Light solar cell 833 provides H2 directly to motor 1620 via channel [1640]. This system may preferably be used with the configuration shown in Figures 13F, 14B, C, and D. Beta may be a particularly preferred embodiment in accordance with the motor type of Figure 14D. 159900.doc •182· 201235565

Figure 15E schematically shows a capacitor 1630 for immediate storage of electrical 1631 that has been filled with electrical leads [1632] that connect the capacitor 163 to the outside of the motor (1603). The capacitor 163 is connected to the other motor of the function 851 according to the functions in the drawings in FIGS. 11A, 11B, 11C, 11F, nG and 12A and FIGS. 13A and 13B via the channel [1633]. Features. These functions include shafts 852, 866, 1621 that are in communication with the alternator 85. The battery 832 is electrically connected to the alternator 850 via a wire [1613]. The battery 832 is additionally charged H by the photovoltaic solar cell 833 for charging purposes. The capacitor 163 is connected to the battery 832 by a wire [1634]. Figure 16A shows the proportionally increasing two-way actuator of Figures 11G-11R. The two-way actuator includes two passages from the outside to the inside of the cylinder, each of which is connected to a regulator controlled by a governor (decompression reading), and the two regulators are connected to each other, so that the speed regulation The controller can control two regulators. There are two overflow passages connected to each of the two sides of the inner piston. Figure 16B shows a prior study of the two-way actuator of Figure 16A. It is inferred that the more rapid reaction system is that the piston contains an overflow channel. It is also inferred that the regulators each need to have a stop function for their flow. Moreover, the overflow channels need to have (1) automatic opposite valve functions (for example, according to the diagram and (2) check valves. Figures 17B to 17H show multiple cylinder motors based on a two cylinder configuration based on Figure 17B For the two-cylinder configuration, the ffii7 configuration is based on one of Figure 17 A, $^ έ. Several π-cylinder configurations. In Figure 17Β, two cylinders are shown 'which are combined simultaneously in time—the cylinder's power stroke and the other cylinder I59900.doc 201235565 (not powered) return stroke. This situation is carried out by the crankshaft configuration of two identical piston chamber combinations, wherein the second longitudinal position of one cylinder j is the first longitudinal direction of the second cylinder The same geometrical level of position. The two actuator pistons are in communication with one another via a crankshaft (which may include two connected sub-crankshafts for each actuator piston), wherein the connecting rods of the actuator pistons Positioned 180 degrees from each other. As a result, the motor always delivers power, and this configuration can be used in a single-machine dual-steam red motor, or for multiple (>2) cylinder motor commands, via existing sub-crankshafts. Connected child The enclosed space of the arbor communicates with each added steam rainbow. The flywheel can be redundant, which can reduce the weight of the carrier. The second cylinder can be used for the second of one of the actuator pistons. The enclosed space is in communication with the third enclosed space of the other of the actuator pistons to combine the ESVT pumps into a pump that is contained by an external (away from the crankshaft) passage In the crankshaft, the enclosed space is divided by a filler at a connection point of the sub-crankshafts, and the filler may be located between the second enclosure space and the third enclosure space There may be valves (e.g., by using a valve actuator according to Figure 21A) that open and close the connection between the ESVT pump and the second enclosed space or the third enclosed space Each connection may have a check valve or a check-out function. The valves may be controlled by the pressure of the ESVT pump and/or by a tappet that is connectable to the camshaft, the camshaft being connectable to the main auxiliary power line ( For example, the auxiliary combustion motor is connected. In this configuration of the actuator piston, At a point in time when the respective pressures of each of the actuator pistons are increased and decreased, it is highly probable that the ESVT pumps are combined into one pump. Changing the speed in the cylinders 159900.doc •184- 201235565 Degree/pressure sub-crank rm 4. ^ ^ The piston chamber combination of each of the enclosed spaces in the glaze can be used only for _徊, 士土, ^^, flying cylinders. The piston chamber combination is adjusted by the voltage of the two-way actuator, and the voltage regulator moves the piston chambers to each of the combined bodies, and the hollow pistons are hollowed out, and Thus in communication with the external governor. However, one of the two piston chamber combinations can be missing and can be exchanged by the same configuration of the X-knife d ESVT pump. The configuration is susceptible to damage to the fault function, which is the reason why the configuration shown in the figure (including) is better. Instead of the toothed belt at the power side of the motor that drives the pump, the gears can be exchanged very well with the gears. The description of the preferred embodiment is made by the reference numerals of Figures 17A through 17H (inclusive).

Figure 18A to Figure 18G (inclusive) show multiple cylinder motors based on the two-flux configuration. The two-cylinder configuration is based on the dual-steam configuration of Figure 18A. The dual-cylinder configuration of Figure A is based on Figure 1. 〇A' Figure 1A is a one-cylinder configuration of Figure 17A. Two cylinders are shown in Figure 18A, which simultaneously combines the power stroke of each cylinder. The two actuator pistons are via a crankshaft (which can The two sub-crankshafts are connected to each other, wherein the connecting rods of the actuator pistons are positioned to be mutually squatted. This situation is performed by the configuration of two identical piston chamber assemblies, one of which The second longitudinal position is at the same geometrical level of the second longitudinal position of the second cylinder. Therefore, the return stroke is not powered, and this configuration can be combined with other configurations (including motors larger than 2 cylinders) for return Stroke 159900.doc -185. Filling the power gap at 201235565 can be directed to the two steam red via the third enclosed space of one of the actuator pistons and the third of the actuator piston Enclosed space connection to combine ESVT pumps into a fruit, the enclosed space is included in the crankshaft. The enclosed space is not divided by a filler at a joint point of the crankshaft, and the filler will generally be located in the second enclosed space and Between the third enclosure spaces. If another group of actuator pistons are connected via a crankshaft connected to the crankshaft, the filler may be necessary at the junction, but each group The group of ESVT pumps can be connected by passages. Instead of the toothed belt at the power side of the motor that drives the pump, the gears can be exchanged very well with gears. The motor, which consists of two The movement of the cylinders in which the (1) enclosed space system (4) of each of the above-mentioned cylinders (the) enclosed space system (4) is connected with the existing sub-crankshafts and the cylinders added therein: the stroke system Simultaneously with the return stroke of the existing cylinder, the power balance occurs in the motor. The combination of the two cylinders is where the connecting rods are in phase (n) of each other, and the chamber is about its first longitudinal position and The second longitudinal position has "what . The description of the preferred embodiment is made with reference numerals s of FIGS. 18A through 10 (inclusive). Ct crankshaft design - multiple uses of the assembly show based on one of the cylinder motors of Figure 11B, Figure uc, which has entered and exited two knives, the auxiliary power source (for example) was selected as a burning horse 1599 〇〇.doe 201235565 The combustion motor burns H2 from the electrolysis of h2o. Figure 19B shows a two-cylinder motor based on Figure 19A, wherein the two cylinders are mirrored with respect to a centerline of the connection of the sub-crankshafts such that the third enclosed two (outlet) is connected via two sub-crankshafts Connected to each other, and the first enclosed space (inlet) communicates with each other externally (by a check valve), and wherein the crankshaft (consisting of two sub-crankshafts) is designed such that each actuator piston The power stroke moves in the same (〇) direction (simultaneous) (according to the principle of Fig. 18A). When more than two cylinders are required in the motor according to this principle, more cylinders may be added such that, for example, another second enclosed space may be connected to the unused end for connection to the added cylinder The enclosed space around the two makes the two-cylinder motor appear. The third enclosed space of the added cylinder that is still free at the time can be connected to the third enclosed space of another added cylinder so that the motor can function with 4 cylinders. The closed end of the now shown passage of the sub-crankshaft may need to be open. Fig. 19B1 shows an enlarged view of the left side of Fig. 19B. Figure 19Br shows an enlarged view of the right side of Figure 19B. Figure 19C shows a two-cylinder motor based on Figure 19A in which a comparable enclosed space (here a third enclosed space) is connected to each other via a sub-cranking shaft, while the second enclosed space is gathered externally (by a check valve)' and wherein the crankshaft (consisting of two sub-crankshafts) is designed such that the power stroke of each actuator piston is in the same (18〇0) direction (different time) ) Move (according to the principle of Figure 18A). Fig. 19C1 shows an enlarged view of the left side of Fig. 19C. 159900.doc •187- 201235565 Figure 19Cr shows an enlarged view of the right side of Figure 19C. Instead of the toothed belt at the power side of the motor that drives the pump, the gears can be exchanged very well with the gears. 19620 DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 21A shows a so-called constant maximum force chamber 1° chamber wall having a wall portion 2 of a longitudinal wear at a first longitudinal position of a piston (not shown) parallel to the central axis 3. Portion 4 has a convex wall with a longitudinal section of the chamber 1. The transition section 5' of the longitudinal section of the outer wall of the chamber is from the convex wall portion 4 to the concave wall portion 7. The wall portion 6 at the second longitudinal position of the piston (not shown) is not parallel to the central axis 3 of the chamber 1. The common boundary 9 of the longitudinal section 1 腔 of the chamber 在 at the longitudinal position, wherein the 1 bar overpressure has been reached by the piston (not shown) moving from the first longitudinal position to the second longitudinal position. Common boundaries 11, 13, 15, 17, 19' 21, Uh between longitudinal section portions 12, 14, 16, 18, 20, 22, 24, 20, 28, 30 of the chamber 1 at longitudinal positions And 27' wherein the overpressure of 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 bar in excess of atmospheric pressure in, for example, the advanced bicycle air pump has been reached by a piston (not shown). For a 10 bar (overpressure) pump, the inner walls of the longitudinal section portions 28, 29, 30, 31, 32, 33, 34, 35 and 6 are convex, while the inner wall of the longitudinal section 7 is concave (at 6 Between overpressure and 7 bar overpressure). If the mathematical equations are followed blindly, the dashed line shows the outer shape of the chamber (36, 37, 38)' for design purposes, so that the chamber is prevented from being lighter. This adaptation itself has no effect on the maximum working force, since it is at the beginning of the hyperbolic function (the working force on the piston due to the shape of the chamber in the longitudinal direction) from the first longitudinal piston to the second longitudinal piston 159900 .doc •188· 201235565 Measurement). Due to the total length of the chamber compared to the total length of the chamber, the size of the wall and the size of the strangeness are also the same for the outer wall of the longitudinal section (not numbered). See WO/2008/025391. Due to the residual volume of the stroke volume of the conical chamber below the piston and the maximum value of its pressure (10 bar in this figure), the longitudinal positioning of the common boundaries can be mathematically determined. It is characterized in that the distance between the common boundaries that follow each other calculated from the first longitudinal position of the piston to the second piston position decreases as the overpressure rating is higher. The height of the respective walls of the longitudinal section portions 28, 29, 30, 31, 32, 33, 34, 35, 6 and 7 is also the case. The position of the wall at the common boundary is based on the selected value of the maximum working force 'in this case it is 25 kg force. The result is the characteristic shape of the chamber (WO/2008/025391). Figure 21B shows the shape of the 10 bar (overpressure) chamber of Figure 21 (continuous line) and the shape of the 16 bar (overpressure) chamber (dashed line) of the same length for the chamber. If the transition size of the inner diameter of the portion 3 将 will give a problem with the size of the piston, the recalculation of the size of the chamber can be performed by increasing the maximum value of the working force by increasing the maximum value of the overpressure. This situation will make, for example, the reference number 3〇 larger in diameter. The wall thickness is substantially uniform over the length of the chamber, but at the concave portion 7, the thickness may be a little greater than the wall thickness of the remainder of the wall. If the maximum overpressure is greater than 10 bar (for example, 16 bar), another recalculation can be performed. This can be achieved by selecting a higher maximum working force so that the circumference of the cross section can become larger. This situation means that the corneal outer wall of the chamber may be closer to the second longitudinal position before the circumference reaches its minimum defined by the type of piston to ensure that the piston will not get stuck. At approximately the first longitudinal position, the calculation will follow 159900.doc 201235565 words, the size of the chamber will become too large, and the person can define its shape at the first longitudinal position to make the circumference smaller The reason for this may be the same for other common boundaries. The task of optimizing the chambers required for the hand pump can be performed in a similar manner to the methods described above. A problem to be solved is that the minimum size of the circumference of the inner chamber wall (depending on which pistons are executable) and the maximum circumference of the exterior of the chamber at the first longitudinal position of the user holding the handle A good compromise and the maximum workforce specified. Figure 22A shows the bottom portion of the chamber of the advanced bicycle pedal pump, in which the bottom portion of the chamber 1 of Figure 21 can also be seen. Chamber! Mounted on the base 41. The flexible gasket 42 mounts the chamber 1 to the base 41. A hose 43, which is connected to the outlet 44 of the pressure expansion groove 49, does not have a check valve. (schematically depicted) the piston 45 includes a piston rod 46. A check valve 47 is located at the bottom of the piston rod. The check valve 47 is in communication with the outside atmosphere (48) and is open to the chamber 1 to fill the chamber when the piston 45 is moved from the second longitudinal position to the first longitudinal position. Room 1. An expansion pressure tank 49 having a chamber 56 is shown that includes an inlet check valve 50 that communicates with the hose 43 via an outlet 44 when the inlet check valve 50 is open. The cross section of the outer wall 51 of the expansion pressure groove 49, and the inner wall 52. An expansion pressure groove 49 is fitted between the top end 53 and the bottom end 54 of the groove 49. The top end 53 of the expansion pressure groove 49 is sealed to the wall of the chamber 1 by a stirrup 55, and the top end 53 and the bottom end 54 are sealed to the wall 52 of the expansion pressure groove 49 by the seal threads 58 and 59, respectively. For extremely high pressures (eg, 16 bar), and in situations where the piston has difficulty sealing to the inner chamber wall, this situation is the preferred embodiment. This configuration 159900.doc • 190·201235565 avoids self-convex The seal on the transition section of the profiled wall to the section of the longitudinal section of the concave wall, see Figure 23 shows the maximum force of 1 () bar __ strange force chamber (9) except the following Outside with the map! The same specification of the chamber: it needs to ensure that the ink-receiving-type piston does not need to move at the second longitudinal piston position - the inner wall 81 of the chamber at the first longitudinal piston position should be selected and displayed parallel to the chamber The central axis. The convex walls 82 from the longitudinal section of the common boundary 83 and 84 (corresponding to the overpressure of the bar and the overpressure of 7 bar, respectively) are parallel to the chamber 8. The transition of the central axis of the "dark wall 81" has a smaller concave subsection 86.1, 86.2 and between the common boundary 84 (which corresponds to a common boundary 88 of 7 bar overpressure up to 10 bar overpressure). A particular internal concave shape 86 of 86·3. The shape of the inner wall of the chamber and its outer wall may no longer correspond to each other. The outer wall between the common boundary 84 of the overpressure of 7 bar and the common boundary 88 of the overpressure of 1 bar is still convex and the inner wall is concave. This difference in shape makes it possible to increase the wall thickness of the different shapes with respect to the remainder of the wall thickness of the chamber, the chamber having its weakest point at different shapes: from the concave inner wall portion to parallel to the center of the chamber A transition of the inner wall of the axis. The outer wall 89 of the chamber positioned at the inner wall of the chamber at the central axis of the chamber may be selected to be linear, but not necessarily parallel to the central axis. This can be done for good shape purposes. This is because the curved shape gives a certain visual tension. The transition from the concave inner wall to the inner wall of the chamber parallel to the central axis of the chamber can be smoothly performed so that the piston can pass through the transition without jamming. 159900.doc -191- 201235565 Figure 24 shows the base 7〇 of an advanced foot pump for, for example, tire inflation. The replaceable cushion 71 holds the conical chamber 80 of Figure 3 in place. The inner wall 81 of the chamber 80 is parallel to the central axis 85 of the chamber 8''. Inflatable piston 73. Closed space 66. Tube 65. Inlet check valve 75. Exit check valve %. Hose 77. Measuring spaces 78, 79 (inside the hose). Valve connector 67 (not shown). The space 68 inside the valve connector 67 is also part of the measurement space (not shown). Figure 25 shows a chamber 1 〇〇 which is a 1 bar overpressure chamber of chamber 1 of Figure 21 . Its second longitudinal position ends with a common boundary 27. The bottom of this chamber is screwed onto the bottom portion 101, which corresponds to the longitudinal section 30 of Figure 21 . The threads connecting the two portions of the chamber are the tube threads 2, which result in a close connection. The outlet 104 is in the bottom ι 3 of the chamber portion 100, and the hose nip 105 is screwed into the outlet 1〇4. The chamber portion 1〇〇 contains a piston 1〇6 which has been schematically depicted. The piston 1 〇6 comprises a hollow piston rod 丨〇7, the hollow piston cup 107 comprising a check valve 1 〇 8 'the check valve 1 〇 8 opens the space 109 ' between the piston and the bottom 1 〇 3 and thereby allows the atmosphere to be 48) The air enters the space 1〇9. A hose 11 equipped with a hose clamp 11 is attached to the hose connector 1〇5. The hose is connected at its other end to, for example, a valve connector 67. A hole 112 in the hose 11〇. 19630 Round Chamber Design DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 30A shows the circular chamber of Figure 12B with the piston moving in a non-moving chamber. The circular subchamber 961 has a center point 980 closest to the circular point 960 in the quadrant 982 earlier than the quadrant 983 for the surrounding section line 981 159900.doc • 192 · 201235565 980 'where the line 981 Placed in quadrant 983. A radius line 987 between the circle center 980 and the circular section line 981. The wrap section 984 of the circular subchamber 961 furthest from the center point 967 of the circular chamber 960 has a center point 985 in a quadrant 986 that is later than the quadrant in which the line 984 is placed. A radius line 988 between the circle center 985 and the circular section line 984. This situation can be established for all other sub-chambers 962, 963, and 964. In other preferred embodiments, the surrounding profile lines can be circular hatching. Figure 30B shows the circular chamber of Figures 13C and 14D with the piston not moving and the chamber moving. Here is the design of the same circular chamber and sub-chamber as the design of Figure 30A. Figure 31A shows Figure 14D' showing a section X-X of the chamber 1749, and section X-X through the central axis 1750. Figure 31B shows a scaled up detail of section X-X of chamber 1749 of Figure 31A. Chamber wall 1785 is shown in section X-X. Wall 1785 includes conduits 1786, 1787, 1788, 1789, 1790, 1791, 1792, 1793, 1794, 1795, 1796, and 1797, respectively, which have openings toward chamber 1749. Preferably, there is substantially no conduit at the section where the section X-X conforms to the farthest from the center 1750 of the circular chamber 1749. From the section at the section 'around the circumference of the chamber 1749, there is an increase in width from both sides of the line of the section χ_χ (1786/7/8/9/90/91 and 1796/5/4/3/2/1) Pipeline: Pipe 1791 has the largest width. The conduits are intended to reduce the size of the contact area of the wall 1785 of the chamber 1749 with the piston such that the piston is manipulated via the circular chamber in the direction of the circular chamber and a suitable propulsive force is obtained, the piston inside the chamber 1749 Around the circumference of the contact area with wall 1785, 159900.doc •193- 201235565 The propulsive force can be attributed to the pipes and equal β 圊32Α. The wall of the display chamber is located at the center circle at the center of the plane orthogonal to the base circle. Intersect in the circle. Figure 32 shows a section of the boundary of the piston. Figure 32C shows the lid geometry. For the area of the lid and the internal volume, only the values α and /^ are required. See equation, the radius of the virtual sphere is given in (2.3). Figure 32D shows a piston with an end cap. Figure 32A shows a piston with an end cap inside the transparent Fermi chamber. Figure 32F shows the pure contact area between the piston and the chamber visible inside the transparent chamber wall. Figure 32G shows the area of contact between the piston and the chamber. Figure 32 shows a section of the wall of the chamber. The chamber reaction force is marked by gray (1800). The total force on the cross section is orthogonal to the chamber wall. For the cross section, the value is the force proportional to the (variable) longitudinal length of the displayed section and the internal pressure of the piston. The local reaction force from the chamber wall is orthogonal to the longitudinal extent of the section, which is again linear over the distance from the center of the center circle (i.e., the origin). As in a tube of constant radius, the first stage varies in length around the section. This length is linearly dependent on the distance to the origin. The local forces change correspondingly and thus coordinate the local forces to drive the complete wall and thus the piston for pure rotation about the origin. Fermi structure. The generator circle has a orthogonal plane as shown at each point. The chamber wall intersects each of the orthogonal planes having a center at the generator circle. The chamber wall is "conical" when the radius of the circle is selected on an orthogonal plane to have a linear (or only increased) value according to the length of the arc of the generator circle along 159900.doc • 194-201235565. Figure 321 shows a section of Figure 32H with additional cross sections to provide an open view. Figure 32J shows Figure 32H, and the red (1801) vector is the component of the gray force (1800) in the longitudinal direction. Figure 32K shows Figure 32J' with additional cross-section to provide an open view. Figure 32L shows Figure 32J, in which the actual sliding force along the wall is shown in blue (1802), which is obtained by projecting a red (1801) vector orthogonal to the chamber wall. Figure 32M shows Figure 32L with additional cross-section to provide an open view. 19640 DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 40A shows a longitudinal section of a pump 1500 having a piston 1501 at a first longitudinal position of the chamber 1506. The piston 1501 includes a U-shaped support member 1502, an O-ring 1503, and a flexible portion. The water impermeable layer 1504 (the last mentioned case is supported by the foam 1505). The support member 1502 is rotatably secured to the piston rod 1507 by a suspension 1508 that includes a shaft 15 10 . The pull spring 1509 is secured to the piston rod 1507 above the shaft 15 10 and the other end is closer to the support member 152 of the 〇 ring 153. The horizontally positioned spring 1511 supports an O-ring 1503. The water impermeable flexible sheet 1504 comprises a layer 1512 having a stiffener 1514 (shown only in Figures 40B, 41D, 41E) which is vulcanized onto the layer 1513 without reinforcement. The central axis 1518 of the chamber 1506. The angle α between the line 159900.doc - 195-201235565 connecting the center of the shaft 1510 and the center of the 〇 ring 1503 with the central axis 1518. The water impermeable flexible sheet is unstressed by the loading of fluid from chamber 1506 which is perpendicular to the central axis 1518 of chamber 1506. Figure 40 shows that the watertight flexible sheet 丨5〇4 is vulcanized in the Ο ring 1503. The layer 1513 without reinforcement and the layer 1512 with reinforcement 1515 are vulcanized on top of each other. The support member 1502 and the horizontal spring 1511 are vulcanized on the dome ring 1503 and the layer 15 13 of the water impermeable sheet 1504. The end of the support member 1502 has a small curved flat surface 1516 that matches the shape of the beak ring 1503 during production. The stirrup ring 1503 is extruded onto the wall 1517 of the chamber 1506. Figure 40C shows a longitudinal section of the piston of Figure 40 at a second longitudinal position. Piston rod 1 507, central axis 1 5 18 of chamber 1 506, and wall 1517. The support member 1502 rotates about the axis 15 10 . The foam 1505' is extruded. Pull the spring 1509' longer. The stirrup ring 1503 is increased in size and is still squeezed to the wall 1517 of the chamber 1506. The impervious sheet 15〇4 is increased in thickness while the horizontal magazine 151 is pressed together. The angle β between the line connecting the center of the shaft 151 Ο and the center of the Ο ring 1 503 with the central axis 丨 5 丨 8 . α = 43 ° β = parallel to the central axis * The foam may comprise a stiffener that is rotatably secured to the piston rod. Figure 41A shows a top view of the piston 1501 of Figure 40 and a section of the chamber 1506 viewed from the first longitudinal position. Wall 1517 of chamber 1506. Piston rod 1507. The suspension 1501 of the support member 1502 is 151 〇. Pulling spring 1509 of support member 1502. 159900.doc • 196-201235565 Figure 41B shows details of the suspension of the support member 15〇2 of the shackle 1503 and the lying spring 1511 of the piston 1501 of Figure 40A. A small curved flat surface 1516 at the end of the support member 1502 vulcanized to the 〇-shaped ring 1503. The end 1519 of the branch member 1502 has a recess 1521 that is sized and shaped to match the size and shape of the horizontal spring 1511. At the boundary 1520 of the spring 1511, the spring is only partially shown at the end of the support member 15〇2. Figure 41C shows a section of the chamber 1506 of Figure 4-8 with the piston 1501 at a second longitudinal position. The suspension of the support member 1502 is 15〇8. Figure 41D shows the helical reinforcements 1 522, 1 523, 1524 of the flexible, water impermeable sheet 1504, which is flexible. These spirals are drawn substantially concentrically about one another about a central axis 15 18 of the chamber 15 0 6 at a distance. Other configurations (e.g., two layers with stiffeners that can intersect each other at a small angle) may be possible but not shown. Figure 41E shows another stiffener configuration, i.e., a more or less resilient reinforcing member 1525 that is concentrically centered about the central axis 1 5 1 of the chamber 1 506. 42A shows a longitudinal section of a piston 1530 at a first longitudinal position, the piston 1530 including a support member 1502, a domed ring 1503, and a flexible, water impermeable sheet 1531 (the last mentioned case is centered with the chamber 1506) Axis 1518 is at a particular angle). The sheet 1531 is vulcanized (1532) on the piston rod 1507. The angle α between the line connecting the center of the shaft 15 10 and the center of the ring 1503 with the central axis 1518. The flexible, water impermeable sheet 1531 has an angle a with the central axis 1518 of the chamber 1506. Figure 42 shows the details of the suspension of the flexible building block 1 531, the vaulted building member 1507, the Ο ring 15 03 and 159900.doc • 197- 201235565. The top layer 丨 533 contains reinforcements (such as the stiffeners of Figures 41D-41), while the bottom layer 1534 does not have reinforcements. The angle α » 180ο-α«110 between the line connecting the center of the shaft 15 10 and the center of the ring 1503 with the center axis 15 18 . (>90〇) Figure 42C shows a longitudinal section of the piston 1530 of Figure 42 at a second longitudinal position. The angle ζ between the flexible impervious sheet 153 1 and the central axis 1 5 1 8 of the chamber 1506. 180°-ζ«95° (>90°) 19650 Description of the Preferred Embodiments FIG. 50 shows the holder 1224 and the reinforcing members 1208, 1209, and 1210 in the holder 1224, respectively, in the three rows of holes 1240, Top view of the suspension in 1241 and 1242. Small curved ends 1220, 1221 and 1222, respectively. Please note that the longer the 'reinforcing members 1208, 1209, and 1210, respectively, the longer the smaller curved ends 1220, 1221, and 1222, respectively, and the longer the reinforcing members. A hole 1243 of a piston rod (not shown). Central axis 1244. The foam 1240 of the piston 1200. Figure 51 shows the piston 1200 of Figure 50 constructed in a pump 1201 having a chamber 1202 and a top portion 1203 and shown at a first longitudinal position 1204 of the chamber 1202. Bearing 1206 is in top portion 1205 where piston rod 1207 moves. A bearing 1206 is assembled in the top portion 1203. Chamber 1202 is a force independent of the type of pressure (see 19620). The wall 1207 of the chamber 1202. All of the stiffeners 1208, (dotted lines 1209) and 1210 have free ends of increased diameters 1211, (121 2) and 1213, respectively. The water impermeable layer 1214 is closed to the piston rod 1207 by a 159900.doc -198 - 201235565 clip 1215, and at the top 1216 of the piston 1200, the foam can be in the chamber 1202 at the uncompressed side 1202' Fluid communication. Reinforcing members 1208, (1209) and 1210 having bends 1217, (1218), 1219 and having small curved ends 1220, (1221) and 1222, respectively. The small curved ends 1220, (1221) and 1222 can be respectively pressed by the adjusting member 1223, the adjusting member 1223 can be rotated within the holder 1224, and the holder 1224 is sealed to the piston rod 1207 by the ring 1227. The adjustment member 1223 is rotatable within the holder 1224 and sealingly coupled to the water impermeable layer 1214. The piston 1200 is mounted to the piston rod 1207 by a retainer 1224, the retainer 1224 is mounted within the spring ring 1225, and the clip 1215 is mounted to the spring ring 1226. The central axis 1243 of the chamber 1202. FIG. 52 shows the bend 1218 of the stiffener 1209. The increased diameter 1212 of the stiffener 1209. The chamber 12〇2. End 1221. 19660 DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 60 shows an elongated container-type piston 1400 in the chamber 14''''''''''''''' The chamber is of the type that the force on the piston rod is approximately uniform during the stroke. The shape of the piston at the second longitudinal position is a "starting" ellipsoid 1403 after being pressurized from the unstressed model, wherein the shape is a generally cylindrical shape (see Figs. 61 and 62). The shape of the piston near the first longitudinal position is the final ellipsoid 1404, which is almost a sphere 1405 (dashed line). The piston 14 其 in between has a shape of a sugar round body. The details of the ellipsoid at the longitudinal position rather than the sphere of the sphere are the same. Fig. 61 shows a container-type piston 1400 which is not unstressed and which may have the shape of a rounded body or a sphere when subjected to stress 159900.doc 201235565. The non-movable cover 142 is at the bottom of the figure and has a gland 1421 for a beak ring (not shown) that is tensioned on a piston rod (not shown). More or less a recess 1422 for a gland of a 〇-shaped ring (not shown) that pulls the bottom of the piston 14〇〇 through a hole 1432 on a bolt (not shown) that locks the piston rod The bottom of (not shown). The movable cover 1423 is on top of the figure and the cover 1423 is movable on a piston rod (not shown). A gland 1424 for a stirrup ring (not shown) that tensions the piston in the top of the piston 1400. Covers 142A and 1423 have recesses 1425 and 1426, respectively, for vulcanizing the flexible walls 1427 of the container piston 1400 on the covers 142A and 1423, respectively. The wall 1427 is shown in the figure as having two layers: a reinforcement layer 1428 and a layer that acts as a cover 1429 for the reinforcement layer 1428. The dashed lines show possible third layers 1430 and 1431 on top of the other layers 1428 and 1429, respectively, which are present only at the locations where the two layers 1428 and 1429 are vulcanized on the covers 1420 and 1423, respectively. Central axis 1433. The wall 1427 of the piston 1400 is generally parallel to the central axis 1433. The reinforcing strips 1440 are laid in a parallel pattern parallel to the central axis 1433. When there are two layers, the pattern 1441 is reinforced. Figure 61 shows both covers 1420 and 1423 of Figure 61, respectively. At the outer side there are rounded transitions 1434 and 1435 from the flexible wall 1427 to the wall 1427 which are respectively vulcanized on portions 1425 and 1426 of the covers 1420 and 1423, respectively. At the inner side of the flexible wall 1427, there is a rounded transition section 1436 and 1437, respectively, just before the flexible wall 1427 meets the portions 1425 and 1426 of the covers 1420 and 1423. When the piston is stressed by inflation, these transitions 1436 and 1437 provide a stable transition of the wall. 159900.doc • 200· 201235565 207 DESCRIPTION OF THE PREFERRED EMBODIMENTS Figure 100 shows a so-called dynamometer diagram. This figure schematically shows the adiabatic relationship between the pressure p and the pump stroke volume ν of a conventional single stage one-way working piston pump having a fixed diameter cylinder. The increase in operating force applied per stroke can be read directly from the map and in quadratic relationship with the diameter of the cylinder. The pressure enthalpy and therefore the operating force F normally increases during the stroke until the valve of the body to be inflated is open. Figure 102 shows a schematic diagram of a piston pump in accordance with the present invention. It shows a graph of the pressure P being similar to the pressure of a conventional pump but with different operating forces and depending entirely on the selected area of the cross section of the pressurized chamber. This situation is entirely dependent on the specification', for example, the operating force should not exceed a certain maximum value or the amount of operating force fluctuates according to the human engineering requirements. This situation is particularly desirable where the manually operated pump is only transporting the medium without significant changes in pressure (as in the case of, for example, a water pump). The longitudinal section and/or cross-sectional shape of the pressurized chamber can be any type of curve and/or line. For example, it is also possible that the cross section is increased by increasing the pressure (Fig. 1〇2B). An example of the operating force is the dashed line 1 or 2. The different wall possibilities labeled 1 and 2 correspond to lines 1, 2, which are mentioned earlier in the figure. The A section is for a pump that only moves the piston, and the b section is for a pump that only moves to the chamber. The combination of two movements at the same time is also possible. Figure 102B shows an example of a dynamometer of a piston pump without a chamber having a cross section that is increased by increasing the pressure. Figures 103A, 103B, i3C, and 103D show details of the first embodiment. The piston moves in the pressurized chamber, and the pressurized chamber contains a cylindrical and conical portion having a circular cross-section of 159900.doc •201 - 201235565, and the circular cross-section has an increased pressure in the gaseous and/or liquid medium. The diameter when the taste is reduced. This situation is based on specifications where the operating force should not exceed a certain maximum. The transition between the various diameters is gradual and there is no discrete step. This situation means that the piston can easily slide in the chamber and adapt itself to the altered area and/or shape of the cross-section without loss of sealing capability. If the operating force needs to be reduced by increasing the force, the cross-sectional area of the piston is reduced and the length of the circumference is also reduced by the reduction. The reduction in circumferential length is based on compression or loosening of the degree of germination. The longitudinal section of the piston member has a trapezoidal shape that is lower than a variable angle to the wall of the pressurized chamber (e.g., such that the helmet is deflected rearwardly. The size of the sealing member is in three dimensions during each stroke. The upper portion of the piston member (e.g., the disk or integrated rib in the sealing member) that is positioned on the non-receiving side during the pump stroke of the piston is protected from deflection under pressure. The «part (for example, a spring washer with a material section) can also be mounted on, for example, the pressure side of the piston. This situation tends to the sealable portion of the piston. If the pump has not been used for a while and the piston member The situation has been compromised for a period of time. By moving the piston rod, the side of the trapezoidal section of the sealing portion of the piston member is pushed axially and radially so that the sealing edge of the piston follows the pressurized chamber The diameter is reduced. At the bottom of the stroke, the 'at the center' chamber becomes higher at the bottom to reduce the static chamber H. The piston rod can be guided mainly in the cover that locks the pressurized chamber. The Α is sealed in both directions to the wall of the chamber, so that the piston rod, for example, comprises an inlet passage with a spring-operated valve that closes in the event of an overpressure in the chamber. 159900.doc -202 201235565 in the absence of a loading section, this separate valve may be redundant. In the pump design according to the invention, the part of the pump is optimized for the working force. The inner diameter of the pump is long in the pump chamber The main beta file is larger than the inner diameter of the existing pump. As a result, the inlet volume is higher, although the volume of the remainder of the chamber is lower than the volume of the remainder of the existing pump. This ensures that the pump can pump faster than existing pumps. Pumping, while maximizing the required operating force is significantly reduced and below the level reported by the consumer as comfortable. The length of the chamber can be reduced 'making the pump practical even for women and adolescents. The stroke volume is still high The stroke volume of the existing pump.

The pressurizing chamber 1 has a wall portion. Piston rod 6. Figure 103A shows a piston pump having a pressurized chamber 1, a cross-section of different areas of portions 2, 3' 4 and 5, with a cover 7 having walls 2, 3, 4 and 5 blocking the piston member and guiding the piston rod 6 Transition sections 16, 17 and 18 between sections. The longitudinal center axis 19 of the chamber 1. Piston 2 at the beginning of the pump stroke and piston 20 at the end of the pump stroke. Figure 103B shows the sealing portion 8 and the loading portion 9 made of an elastic material (for example, a spring washer having sections 9A, 9 2 and 93 (not shown in other sections)) and two attached to the locking member 11 The support portion 1 of the piston member of the piston rod 6 between the portions 〇〇 the piston rod 6 has an inlet 12 and a valve 13. The angle between the sealing portion 8 of the piston member and the wall 2 of the pressurized chamber. Sealing edge 37. The distance a is the distance from the sealing edge 37 to the central axis of the chamber 1 in the cross section at the beginning of the stroke. Figure i 3c shows the outlet passage 14 in the member 15 which reduces the volume of the static chamber. The angle h between the sealing portion 8 of the piston member and the wall 5 of the pressurized chamber. The distance a' is the distance from the sealing edge to the central axis of the chamber ^ 159900.doc -203· 201235565 at the end of the stroke. It is shown that the distance ai is approximately 41% of the distance a. Loading part 9·. Figure 103D shows a longitudinal section of a chamber of a foot pump (multiple"6〇爪至^^mm, length 500 mm) in accordance with the present invention, wherein the cross section is selected such that the operating force remains substantially constant and according to the person Choose from engineering needs: For example, as shown in the figure: 277 N. You can also choose other force sizes. This situation only gives a quantitative starting point for the foot pump according to the invention, since the constant operating force can be incorrect in human factors engineering. For comparison, the existing low-pressure foot pump ("*32 mm, length 470 mm" section is shown in dotted lines" and the existing 咼 pressure foot pump ("section 27 mm, length 550 mm" section is shown in dotted lines" is clear It is shown that both the foot pumps according to the present invention have a larger stroke volume than existing pumps, thus charging the tires faster and with lower operating forces. The chamber according to the invention can be adapted to human engineering requirements throughout the stroke.

104A, 104B, 104C, 104D, 104E, and 104F show details of the second preferred embodiment. The sealing portion of the piston member is made of an elastically deformable material supported by a support member rotatable about an axis parallel to the central axis of the chamber. As a result of this movement, the greater the area of the support sealing member, the higher the pressure in the chamber. The loading portion of the support portion initiates movement of the support member. The loading portion in the form of a flat spring can be resized in a direction perpendicular to the centerline of the chamber. The spring becomes harder and harder 'the higher the pressure in the chamber. It can also be a spring on the axis about which the branch member rotates. By reducing the diameter of the sealing portion, the sealing portion increases its length. This case is the case of an elastically deformable material 159900.doc-204-201235565 (similar to, for example, rubber) which can be compressed only a little. Therefore, at the beginning of the stroke, the piston rod extends out of the sealing member. If other materials for the sealing portion are selected, the length of the sealing portion may remain the same or may be reduced by reducing its diameter. Figure 104A shows a piston pump having a pressurized chamber 21, a pressurized chamber Chamber 21 has portions of different cross-sectional areas. The chamber has cooling ribs 22 on the high pressure side. The chamber can be formed by (ejection). Piston rod 23. A cover 24 guides the piston rod. Piston 36 at the beginning of the pump stroke and piston 36' at the end of the pump stroke. Figure 104B shows the elastically deformable seal portion 25 (not made) secured to the piston rod 23 by the member 26. A portion 27 of the piston rod 23 extends beyond the sealing portion 25. The support portion 28 is suspended from a ring 29 that is secured to the piston rod 23. The support portion 28 is rotatable about the axis 30. The loading portion 31 includes a spring that is secured to the piston rod 23 in the bore 32. Seal the edge 38. Figure 104C shows that portion 27 of piston rod 23 is almost covered by an elastically deformable sealing member 25' which is resiliently deformable and has now increased in length and reduced in diameter. Sealing edge 38,. In the illustrated rib section, the distance a' between the sealing edge 38 and the central axis of the chamber is approximately 40 〇/ of the distance a. . Figure 104D shows a section A_a of Figure 104B. The loading portion 31 is secured at one end in the bore 32 of the piston rod 23. Support portion 28 and ring 29. The support portion is blocked by the stop surface 33 (not drawn). The support portion 28 is guided (not drawn) by the guiding member. 159900.doc -20$. 201235565 Fig. 104E shows a section BB of Fig. 4〇4C. The support member 28 and the loading member 31 move toward the piston rod 23. Fig. 104F shows an alternative to the loading member 31. The replacement includes a spring 35 on each axis 30. Fig. 105A, Fig. 1〇5Β, Fig. i〇5C, Fig. 105D, Fig. 105E, Fig. 105F, Fig. 105G, Figure l〇5H show details of the third embodiment, which is a variant of the first embodiment. The sealing portion comprises a flexible, water-impermeable membrane for gaseous and/or liquid medium. This material can be in three directions The size is changed without folding. The sealing portion is mounted in a ring that is sealed to the wall of the chamber. The ring is loaded to the wall by a loading member (for example, a magazine in the circumference). And the spring is further supported by a support member rotatable about an axis secured to the piston rod. The support member can be loaded by a spring. Figure 105 shows a piston pump of a longitudinal section analogous to the piston pump of Fig. Longitudinal section. Piston 49 at the beginning of the pump stroke and Piston 49* at the end of the pump stroke. Figure 105B shows a piston member at the beginning of the stroke comprising a sealing member 40 (e.g., a stressed sheath) secured to a sealing member 41 (e.g., a beak). Loaded by a spring 42 located on the circumference of the sealing member 41 and the sealing member 4A. The central axis 39 of the spring 42. The ring 41 and/or the spring 42 can be attached to the piston rod 45 and positioned perpendicular to The support member 43 that rotates on the axis 44 of the central axis is supported by a support member 43 that is in a (compressed) pump stroke in a _ mode (four), which is supported by the individual portion 43. (4) The members 4(), μ and the circumference of the loading member U can be loaded by the spring 46. The angle between the wall of the chamber 2 and the support member 201235565 member 43. The piston rod 45 does not have an inlet or a valve. A form of support ring and/or load ring can be mounted as an alternative to spring 42 in the 〇 ring (not shown) to seal edge 48. Figure 105C shows the piston member at the end of the stroke. Sealing member 4〇, 41' 4 〇, 41 thicker than the beginning of the stroke "spring 46, in The angle β2 between the wall 5 and the support member 43 at the end of the stroke. The distance a between the sealing edge 48 and the central axis 19 of the chamber in the illustrated section is approximately 22% of the distance a at the beginning of the stroke. » Smaller distances (eg, 1 5%, 1 〇%, or 5%) are possible and depend only on the configuration of the suspension of the piston on the piston rod. Therefore, this situation is true for all other embodiments. Figure 105D A section CC of Fig. 105A having a support member 43, a shaft 44 and a bracket 47 is shown. Fig. 105E shows a section DD from Fig. 5Α. Fig. 105F shows two positions of the piston ι 18 of Fig. 1 〇 5G and the piston 118' of Fig. 5 中 in the chamber. Figure 105G shows a piston made of a composite of materials. The composite comprises an outer layer 110 of elastic impervious material and a fiber m. The fiber structure causes hemisphericality when it is under internal pressure. This shape stabilizes the piston movement. As an alternative, the sealing member may comprise a liner, a fiber and a cover (not shown). If the liner is not taut, add an impervious skin (not drawn). All materials at the compressed side of the piston follow the specific environmental requirements of the chamber. The outer skin is mounted in the sealing portion 112. In the outer skin and the sealing portion, the spring force ring 113 can be mounted and elastically deformed in its plane' and the loading of the reinforcing ring 114 can be enhanced. Sealing edge 117. 159900.doc • 207· 201235565 Figure 105H shows the piston of Figure 1〇5G at the end of the pump stroke. If there is still a full overpressure, the hemisphere has been compressed into a shape that is overpressured (e.g., reduced after release of the medium, then shape 110, as a result). Fig. 10 6 A, Fig. 1 0 6 B, Fig. 1 〇 6 C exhibition + potential m life _ Team exhibition is not the details of the fourth embodiment. The piston member comprises a rubber tube having a reinforcement (e.g., in the form of a woven or rope wrapped around it). The neutral angle between the tangent of the reinforcing coil and the centerline of the hose (= so-called braid angle) is mathematically calculated to be 54. 44: Assuming the elongation without reinforcement, the hose under internal pressure will not change Size (length, diameter). In this embodiment, the diameter of the piston member decreases with respect to the reduced diameter of the cross-section of the chamber under increased pressure. The braided horn deer is wider than the neutral angle. The shape of the major portion of the longitudinal section of the pressurized chamber is generally conical due to the behavior of the piston member. At the end of the stroke, the piston member increases its diameter and its length decreases as the compressed medium has been removed from the chamber. The increase in diameter is not a practical issue. From the piston to the wall of the pressurized chamber, the sealing force should be increased by increasing the pressure. This situation can be achieved, for example, by selecting the braid angle to reduce the diameter of the piston slightly below the cross section of the chamber. The twisting is reduced. Therefore, the 'weaving angle can also be chosen to be less than the neutral angle and /: :: as the neutral angle... In general, the choice of the neutral angle depends entirely on the setting of the grid and thus the braiding angle can be Wide and / or smaller and / or neutral angle. It is even possible that the braid angle changes everywhere in the piston. Another possibility is that the same section of the plug has the same and / or the same Weaving angles. Any type of reinforcement material and or reinforcement pattern can be used. The mouth and mouth layer can be placed anywhere in the longitudinal section of the piston. The number of pockets and/or covers can be more than one. The piston member can also contain 159900.doc -208· 201235565

Loading and supporting members, such as those previously shown. In order to be able to accommodate a larger change in the area of the cross section of the chamber, a slightly different configuration of the piston member is necessary. The conical shape now contains fibers under tension. These fibers are spiraled together at the top of the conical shape near the piston rod and at the open side of the conical shape at the bottom of the piston rod. These fibers can also be fastened to the piston rod itself. The pattern of fibers is designed, for example, such that the higher the tension of the fibers, the higher the pressure in the chamber of the pump that compresses the medium. Other patterns are of course possible, depending only on the specifications. These patterns deform the conical outer skin so that it fits itself into the cross section of the chamber. The fibers may be interspersed on the lining or interspersed in the passage between the lining and the cover, or the fibers may be integrated into the two or both of the β. It is necessary to have a loading member so that there is no pressure under the conical shape yet In case of case, obtain a proper seal to the wall. Loading components (e.g., spring force members in the form of rings, plates, etc.) can be built into the skin, for example, by being inserted into the forming process. The suspension of the circle (4) on the piston rod is superior to the previous embodiment in that the piston is now loaded by tension. Therefore, more balance and less material are needed. The piston sheath and cover may be made of an elastically deformable material that conforms to specific environmental conditions, and the fibers may be elastic or rigid 'made of a suitable material. Figure 106A shows a longitudinal section of a pump having a chamber 60. The wall portions 61, 62, 63, 64, 65 are two cylindrical members 61, 65 and conical 62, 〇, 64. Transition sections 66, 67, 68, 69 between the sections. At the beginning of the pump stroke / tongue plug 59 and piston 591 at the end of the stroke. Figure 106A shows the piston member 50 (the hose with the reinforcement 51). The hose is fastened to the piston rod 6 by means of a clip 52 or in a similar manner. The piston 6 has ribs % 159900.doc -209 - 201235565 and ribs 57. The ribs 56 prevent movement of the piston member % relative to the piston rod (4), and the (four) member 57 prevents the movement of the shirt member from the piston rod 6 away from the shame 7. Other configurations of the fitting may be possible (not shown in the outside of the hose). The projection 53 is sealed against the wall 61 of the chamber 6 by a stiffener 51. The hose comprises a lining 55. As an example, Display cover 54. The shape of the longitudinal section of the piston member is an example. Sealing the edge brother. The figure shows the piston member at the end of the stroke, which puts the gaseous and / or liquid medium under pressure. The piston member can make the diameter change only through the diameter Designed in such a way as to change (not shown) Figure 106D shows the piston 189 of the crucible 106E and the piston 189 of Figure 106F at the beginning and end of the pump stroke, respectively, in the chamber of Figure 106A. Figure 106E shows A generally expansively shaped piston member having a apex angle ει which exhibits no overpressure at the side of the chamber. The piston member is mounted on the piston rod 18 在 at its top. Conical Opened on the compressed side of the piston, the cover 181 includes a sealing portion shown as a protrusion 182 having a sealing edge 188 and an inserted spring force member 183, a fiber 184 as a support member, and a liner 185. The member 183 provides The loading of the cover is such that the projection 182 seals the wall of the chamber without overpressure on the side of the chamber. The fibers 184 can be located in the channel 186, and the channels ι86 are shown as being placed over the cover 181 and the liner 185. The liner 185 may be impervious to water, otherwise a separate layer 2〇9 (not shown) at the pressure side is mounted to the liner 185. The fibers are mounted to the piston rod 18 in the conical top 187 and / or mounted to each other. The same is true at the bottom end of the piston rod 180. Figure 106F shows the piston member at the end of the stroke. The apex angle is now £2, and 159900.doc -210-201235565 is shown in the section t seal edge The distance a between the 188 and the central axis i9 of the chamber is now approximately 44% of the distance a at the beginning of the stroke. Fig. 107A, Fig. 7B, Fig. i〇7C, Fig. i〇7D, Fig. 7E shows the details of a fifth embodiment of the pump having a piston 4 that is constructed to have a very high degree of relaxation and another composite structure comprising a base material that is extremely elastic in all three dimensions. The piston itself is not tensioned, By virtue of, for example, flexibility on the pressure side of the piston member Tightening is performed. The axial hardness is achieved by a plurality of integrated reinforcing members which are placed in the cross section to optimally fill the pattern of the cross section, and the distance between them is reduced, and the diameter of the cross section is smaller. In most cases it means that the pressure in the pressurized chamber is high. In the longitudinal section of the piston, the stiffener is laid at several angles between the axial direction and the direction of the surface of the piston member. The higher the setting, the more the angles are reduced and closer to the axial direction. Therefore, the force is now transmitted to the support member (for example, a washer) connected to the piston rod. The piston member can be mass-produced and inexpensive. And, where necessary, the sealing member in the form of the flexible film can be injection molded with the base material in one operation (e.g., the reinforcement can be joined together at the top), which makes handling easier. It is also possible to make the film by "burning" the film in the base material during or after injection molding. This situation is particularly convenient if the base material is a thermoplastic. The hinge should not "burn". Figure 107F, Figure i〇7G, Figure 107H, Figure 1〇71, Figure i〇7j, Figure 107K, Figure! 07L, 107M show an embodiment of a chamber and a sixth embodiment of a piston that fits the chamber. The sixth embodiment of the piston is a variant of one of Figures iA7A, 107B, Figure 7C, Figure 107A, and Figure 1A. If the cross-sectional area of the piston and/or the change in the direction of movement between the two pistons in the direction of movement is continuous but still large such that this causes a leak, then the other sections are made Minimizing changes in parameters is advantageous. This case can be illustrated by using, for example, a circular cross section (fixed shape): the circumference of the circle is D, and the area of the circle is V4 Z) 2 (d = diameter of the circle). That is, the decrease in D will only give a linear decrease in the circumference and a second decrease in the area. It is even possible to maintain the circumference and only reduce the area. If the shape is also fixed (for example, about a circle), there is a certain minimum area. The high-order numerical calculation of a shape as a parameter can be performed by using the following k-and-Frequency series expansion method. The cross section of the pressurized chamber and/or the piston can have any form and this can be defined by at least one curve. The curve is closed and can be roughly defined by two unique modular parameterized Four-Frequency expansion methods. A Four-Frequency expansion method is for a standard function: /(x) = + cos(pX) Sin (px) where 2 S = — f /(jc)cos(px)c6c dP = ^ I f(x)sm{px)dx 〇<χ<2π9Χ€Ν

The weighted average of the CO·? weighted average of p>09peR, /?== indicates the level of the triangle fineness. Figures 107F, 107K show examples of such curves by using different parameter sets 159900.doc • 212-201235565 in the following formula. In this real money, only two parameters have been used. If more coefficients are used, it is possible to find the best curve that meets other important requirements, for example, as a curved transition, the curve of the curved transition has a certain maximum radius and/or (for example) may not be given under the given premise The maximum value of the tension in the sealed portion that exceeds a certain maximum value. As an example: Figures 107L, 107M show the best convex and non-convex curves to be used for the possible deformation of the bounded domain in the plane under the constraint that the length of the boundary curve is fixed and its numerical curvature is minimized. By using the starting area and the starting boundary length Φ 纟 ' it is possible to expect the smallest possible curvature for a certain desired target area. The pistons shown in the longitudinal section of the chamber have been drawn primarily for the condition that the boundary curve of the cross section is circular. That is, the shape of the longitudinal section of the piston may be different in the case where the chamber has a non-circular cross section according to, for example, Fig. 107F, Fig. 1〇7Κ, Fig. 10, and Fig. 107M. All types of closed curves can be described by this formula, for example, a c-shaped curve (see PCT/DK97/00223, Figure 1Α). The characteristic of these curves is that when the line is drawn from the mathematical pole in the profile, the line will intersect the curve i less than once. The curves are symmetrical toward the line in the profile and can also be produced by a subsequent single-Frequency series expansion method. When the curve of the cross section is symmetrical with respect to the line passing through the mathematical pole in the section, the piston or chamber will be easier to produce. "These regular curves can be roughly defined by the single-Fourth series expansion method ^ = ~J^Y, CP c〇s(px) p霣l where 159900.doc 213- 201235565 9 c/> = — £ f{x)cos{px)dx

〇 ^ jc < 2π, χ e N p > 0, p € The weighted average of R, P = the level of the triangle fineness. When drawing a line from a mathematical pole, the line will always intersect the curve only once. The particular formed sector of the cross section of the chamber and/or piston can be roughly defined by the following formula: /W = cos(3px) f( JCJ=r〇-ia.2«l^n2fjJx cP=~ilf (x) cos (3px) dx π

0 < x < 2n,xe N p > 0, pg R eP=f(x) The weighted average value, P = represents the level of the trigonometric fineness and wherein the cross section in the polar coordinates is roughly expressed by the following formula: + a. sin (12ψ) where r〇^〇, a>0, m>0,meR, n>0,neR, 0<φ<2, and where 214- 159900.doc 201235565 r = start pin circle The limit of the "petal" in the section, r〇 = the radius of the circular section around the axis of the starting pin, a = the scaling factor for the length of the "petal", r max = VQ + am = used to define the "petal" The parameter of the width n = the angle of the parameter furnace = delimiting curve used to define the number of "petals".

The inlet is placed near the end of the stroke due to the nature of the sealed portion of the piston member. These particular chambers can be produced by injection molding and, for example, also by the use of so-called superplastic forming methods, which are heated and forced by force in the tool cavity or by the use of tools to move the air pressure. Come and press. Figure 107A shows a piston pump having a pressurized chamber 7A having a cylindrical portion 71 in a longitudinal section, a transition portion 72 to a continuous concave f-curved portion 73, to an almost cylindrical portion. Another transition 74 of 75. Piston members 76 and 76 are shown at the beginning and end of the pump stroke, respectively. At the end of the outlet passage 77, a check valve 78 can be installed (not shown) showing the piston member % comprising the elastomeric material 79 which imparts a substantially conical shape to the longitudinal section of the piston at low abrasive forces. The material 79 also functions as a loading member. The bottom portion includes a radially (four) sealing member 80, which also functions partially as a loading member. The member is composed of reinforcing members 81 and 82, wherein the reinforcing phase is mainly cut to the pressurized chamber The sealing edge 83 of the piston member of the wall of the chamber 70, while transferring the load from the sealing structure (4) and the base material 79 to the support member 84 (e.g., gasket) that is itself supported by the piston 159900.doc -215·201235565. 8〇 is still slightly folded in this position of the piston member 76 such that the more the load 85 seals the sealing edge 83, the greater the pressure is in the chamber 70. The stiffeners 82 are joined together at the top by the joints. In this position 70, the stiffener 81 and the stiffener 82 have an angle therebetween and are at an angle to the central axis 19, wherein substantially parallel to the central axis 丨9 of the pressurized chamber 70. The surface and center of the piston 76 Angle (1) between the axes 19. Figure 107C shows the piston member 76 at the end of the stroke. The sealing members are folded together and the resilient material 79 is squeezed together causing the stiffeners, 82 to point generally parallel to the central axis 19. The angle between the surface of the piston member % and the central axis 19 is positive, but almost zero. On the cross section shown, the distance a between the sealing edge 83 and the _ heart axis 19 is at the beginning of the stroke. The sealing member 8 is at a distance of 39° from a. Fig. 107D shows a cross section E_E of the piston member 76, which shows the folding of the basic elastic material 79, the reinforcing member 81 and the reinforcing member 82, and the sealing member 8〇. 87. Piston rod 6. Fig. 107E shows the piston member 76, cross section F_F, which shows the basic elastic material 79, the stiffener 81 and the stiffener 82, and the folding of the sealing member 8 π. Clearly shows the elastic material 79 squeezed Pressing together. Tuqing shows the difficult side of the chamber, where the area is reduced in a specific step, while the circumference remains constant - these areas and circumferences are defined by two unique modular parametric Four-Frequency expansion methods, Four-degree expansion The method is for a standard function. In the upper left, the section of the starting surface of the series is used. The set of parameters used is shown at the bottom of the figure. This series shows the reduction of the cross section 159900.doc -216- 201235565 area. The bold figure in the middle shows the decreasing cross-sectional area of different shapes, wherein the cross-sectional area of the 乍 in the upper left corner is taken as the starting area size. The area of the shape of the lower right cross-section is about 28% of the area of the upper left. Figure 107G shows the chamber 162 The cross-sectional area of the longitudinal section 'chamber 162' is changed by maintaining a circumference along the central axis. The portion of the piston 163^ chamber having a cross-sectional area of different cross-sectional areas of the wall portions 155, 156, 157, 158. The transitions 159, 160, 161 between the wall portions show the sections G-G, Η-Η and I-Ι. The section G-G has a circumferential section, and the section η·η 152 has an area of between about 90% and 70% of the area of the section G-G. Fig. 107A shows a cross section Η-Η 152 of Fig. 107G and shows the section G-G 150 as a dotted line as a comparison. The cross-section Η-Η has approximately 90% to 70 of the area of the section G-G. / area between 〇. Make the transition segment ι51 smooth. The smallest portion of the chamber having about 5% of the cross-sectional area of the section G-G is also shown. Fig. 1071 shows a cross section of Fig. i 〇 7G and as a comparison, the cross section of the G-G ° section ΐ_ι has an area of about 7〇% of the area of the section g_G. The transition section 153 is made smooth. The smallest part of the chamber is also shown. Fig. 107J shows a variation of the piston of Figs. 107A to 107C with a section H-H from Fig. 7A. The piston is now made of an elastic material which is also impervious to make the individual sealing members unnecessary. The distances 〇 and d are different and by this the piston is deformed on the same cross section H_H. Figure 107K shows a series of cross-sections of a chamber in which the area is reduced in a particular step and the circumference remains constant. The area and circumference are defined by two unique modular parametric Four-Frequency expansion methods, a The series expansion method is for a standard function. In the upper left is the section of the initial section of the series. The set of parameters used by 159900.doc •217· 201235565 is shown at the bottom of the figure. This series shows the decreasing area of the cross section, but it is possible to increase this area by keeping the circumference constant. The bold numbers in the figure show the decreasing cross-sectional rain products of different shapes, with the cross-sectional area in the upper left corner as the starting area size. The size of the cross-sectional area at the lower right is about 49% of the starting area at the upper left. Fig. 107L shows a convex curve optimized for a fixed length boundary curve and the smallest possible curvature. The formula of the minimum rate radius corresponding to the curvature of the maximum curvature of the graph shown in Fig. 7 is as follows: r~ ~ML~ sfL2 ~{4π A,) Determine by the following formula by the following formula: y = ~4^2 ~4π Aj where r ~ minimum radius of curvature L = boundary length = constant A1 = starting domain area The reduced value of Aq is taken as an example from Fig. 103D: corresponding to the area of the disk having a radius of 30 and the boundary length, the domain area Ag = (30) 2 and the boundary length L = 6 〇 = 188 5. The length is required.胄, but the area is reduced to the value to be specified ~. The final configuration should have the area Αι=(19/2)2=283·5. The convex curve with the smallest possible curvature of the boundary curve is as follows: =1.54 啼=0.65 ^ = 89.4 159900.doc -218- 201235565 The curves on the graph are not to scale and the diagram only shows the principle. The curve can be further optimized by exchanging straight lines from the curve, which can improve the piston to Wall seal. Figure 107M shows a fixed-length boundary curve and the smallest possible curvature . The best of the corresponding non-convex curve shown in FIG Shu 〇7L FIG largest curvature of the formula-based minimum radius of curvature as follows:

The length specified by X is determined by the following formula:

Γ = minimum radius of curvature L = boundary length = constant

Al = the non-convex curve with the smallest possible curvature of the reduced value boundary curve of the starting domain area A (the intermediate linear hyperbola has significant modifications): r = 6.3 =1/γ = 0·16 Jc = 42 The curves on the graph are not to scale and the diagram only shows the principle. Figures 108A, 108B, 108C show a seventh embodiment of a pump wherein the piston member constructed as a further composite structure comprises a compressible medium within the enclosed chamber, for example, a gaseous medium similar to, for example, air (the following is also the case) Possible: only for an incompressible medium such as a liquid medium similar to water, 159900.doc 219-201235565 or a combination of a compressible medium and an incompressible medium, which is constructed, for example, as a reinforced hose. The following situations may be possible: the lining, reinforcement and cover at the pressure side of the piston member are different from the lining, reinforcement and cover of the non-pressurized side, where the outer skin can be deposited as a preformed outer skin, thus being pumped This shape is maintained during the stroke. It is also possible that the outer skin consists of two or more parts that are pre-formed by itself, one part being on the uncompressed side of the piston member and the other part being on the pressure side (see part X of Figure 1〇8B). , each part γ + ζ). During the pump stroke, the two parts are hinged to each other (see XY and ZZ of Figure 108B). The sealing edge is adapted in the cross section to the cavity to cause a change in the cross section of the piston at the sealing edge of the piston, and this situation can result in a change in the volume within the piston. This change in volume can impart a change in the pressure of the compressible medium and can result in a varying sealing force. In addition, as the compressible medium transfers the load on the piston to the piston rod, the compressible medium acts as a support portion. Figure 108A shows the longitudinal section of the pressurized chamber 90 including the continuous convex curve 91 and the piston 92 at the beginning of the pump stroke and the piston 92' at the end of the pump stroke. The high pressure portion of chamber 90 includes an outlet passage 93 and an inlet passage 94, each having check valves 95 and 96 (not shown). For low pressure applications, check valve 95 can be removed. Figure 108B shows the piston 92 directly sulphided onto the piston rod 97. The piston 92 comprises a compressible medium 1 〇 3 in the lining 99, a reinforcement 1 〇〇 and a cover 1 〇 β β skin 99, 1 〇〇, 1 〇1 The portion X is preformed because the portion X and the portion of the ridge and the ridge are tied to the pressed portion of the piston member 92. The hinge χ γ is shown between the portion X of the outer skin and a portion of the ridge. Part X and the pressure chamber 9〇 159900.doc -220· 201235565 The heart axis 19 has an average angle %. The portions γ and z are connected to each other and have an intermediate angle 7ι which is selected such that the force will be directed primarily to the piston rod. The angle between the portions Y· and Z· is selected such that the higher the force in the chamber, the more perpendicular this portion is to the central axis. Hinge 22: is between one and a half of part Z. Sealing the edge 102. Figure 108C shows the piston at the end of the stroke. The portion of the outer skin χι has an angle Κ2 with the central axis, while the portion X, and Υ· have an intermediate angle κ2, and a substantially unaltered angle γ between γ, and Ζ'. Part 2 - the angle between the halves is substantially zero. The distance a between the sealing edge ι 2 and the central axis 19 of the chamber in the cross section shown is approximately 40% of the distance & . Sealing edge 1〇2· and compressed medium 1〇3. Figures 109A, 109B, 109C, 1〇9D show details of a combination of a first embodiment of a pressurized chamber having a fixed size and a piston of a variable size. The piston is an inflatable body that fills the cross section of the chamber. During the stroke, the piston can be constantly changed in size on the sealing edge and near the sealing edge. The material may be a composite having an elastically deformable liner and a member similar to, for example, a fiber (e.g., glass, butterfly, carbon or aramid), fabric, filament, or the like. Depending on the fiber structure and the total resulting loading on the piston, the piston is shown to have a small internal overpressure 'which can result in a generally spherical or substantially elliptical curve form (like the "rugball" form) or any intermediate shape and other shapes. . For example, a reduction in the cross-sectional area of the chamber causes the size of the inflatable body to decrease in that direction 'and a three-dimensional reduction is also possible due to the fiber architecture, which is based on the fibers being layer-by-layer independently of each other. The "grid effect" of the cut. The cover is also made of an elastically deformable material suitable for the specific environmental conditions in the chamber. 159900.doc •221· 201235565. If the pad and the cover are both permeable to water, a separate balloon may be used in the body. This is because the body contains gaseous and/or liquid media. If the pressure in the body is greater than the external pressure, for example, the fiber building members can only impart strength by themselves, since these supporting members are less subject to tensile forces. This pressure condition may be preferred for obtaining a suitable seal and life. Since the pressure in the chamber can be constantly varied, the pressure in the body should be the same and slightly higher, or always high at any point in the pump stroke by being held constant. The final solution can only be used for low pressures, since the / tongue plug may otherwise get stuck in the chamber. For higher pressures in the chamber, a configuration may be necessary such that the internal pressure changes accordingly to a higher change in the pressure in the chamber. This situation may be achieved by a number of different configurations - load regulation members - based on the principle of varying the volume and/or pressure of the medium within the piston and/or changing the temperature of the internal medium, other principles are also possible, Such as, for example, the correct selection of the material of the piston skin (eg, a particular rubber type) (where the modulus defines deformability) or the correct selection of the relative amount of the compressible portion of the volume within the inflatable body, and Compressibility β Here, an incompressible medium is used in the piston. The volume of the piston can be varied by the change in the cross-sectional area at the edge of the seal, since the size of the piston in the direction of movement is constant. This change causes the incompressible and contractible medium to flow within the piston rod to or from the spring operated piston. It is also possible that the spring-operated piston is located elsewhere. The combination of the pressure caused by the change in the volume of the piston and the change in pressure due to the spring force results in a certain sealing force. This spring force acts as a fine tuning of the sealing force. The improved load adjustment can be achieved by exchanging an incompressible medium from a combination of compressible and incompressible media, which acts as a load regulating member, by 159900.doc -222-201235565. Another improvement is that the piston is more easily contracted due to the lower sealing force and lower friction due to the exchange of the spring by the operating force of the piston of the chamber. In particular, when a medium that can be heated more rapidly is selected, a temperature rise of the medium in the heating piston can be achieved. Figure 109A shows the longitudinal section of the pressurized chamber of Figure 108A and the piston 146 at the beginning of the stroke of Figures 1 and 9B and the piston 146' of Figure 109C at the end of the stroke. Figure 109B shows a piston 146 having an inflatable body having a wall containing fibers 130 having a pattern such that the inflatable body becomes a sphere. Cover 131 and pad 132. The impervious bladder 133 is shown in the sphere. The ball is directly mounted on the piston rod 12〇. The ball is locked at one end by the cover 121 and locked by the cover 122 at the other end. The hollow passage 125 of the piston rod 120 has a hole 123' in its side in the body such that, for example, the unloading medium ι 24 contained in the ball can be freely attached to and from the passage 125 of the piston rod 120. flow. The other end of the passage 125 is closed by a movable piston 126 that is loaded by a spring 127. The magazine is mounted on the piston rod 128. The spring 127 tunes the pressure and sealing force within the ball. The sealing surface 129 is in substantially line contact with an adjacent wall of the chamber. The fibers are only shown schematically (in all of the figures in this application). Figure 109C shows the piston of Figure 109B at the end of the stroke where the cross-sectional area is the smallest. The ball exhibits a much larger sealing surface 134 that conforms to the adjacent walls of the chamber. The piston 126 has moved relative to its position shown in Figure 9B, 159900.doc - 223 - 201235565 This is due to the incompressible medium 124 having been squeezed out of the twisted sphere. In order to minimize friction, it is possible that the cover at the sealing surface has ribs (not shown) or may have a low friction coating (and walls of the chamber, not shown). Since neither of the covers 121 and 122 can move along the piston rod m, the lattice effect can only be part of the material balance of the outer skin. The remainder is shown as a "shoulder" 135, which can significantly reduce the lifespan while Also increase friction. Sealing edge 129,. Sealing the edge 129 in the cross section shown, and the distance a' between the axis to the "axis 19" is approximately 48% of the distance a at the beginning of the stroke. Figure 109D shows the incompressible medium us and The improved compression of the sealing force by the compressible medium 137. The pressure of the medium is adjusted by the piston 138 and the seal ring 139 and the piston rod 14 ,, and the piston rod 14 〇 is directly connected to the operating force. The piston 138 can be in the sphere The cylinder i4i slides. The support member 145 fastens the ball to the piston rod ι4. Fig. 110A, Fig. 110B, Fig. 11 shows the modified piston where the outer skin of the chamber can be released. Balance, this situation means improved service life and less friction. This method focuses on the fact that the suspension of the piston on the piston sill can be translated over the piston rod and/or rotated farther away from the piston. The side of the pressure is located at the side of the pressure. The spring between the movable cover and the stop on the piston rod acts as another load adjustment member. Figure 110A shows a longitudinal section of the chamber 169 of the pump not according to the present invention and is respectively 168 and 168·the two piston positions Figure 110B shows a piston having an inflatable outer skin having at least two layers of fibers 171 having a fiber that is substantially spherical '13⁄4 round when inflated 159900.doc • 224 · 201235565 If the outer skin is not tensioned, the interior of the piston may be a water impermeable layer 172. The medium is a combination of a compressed medium 173 (eg, air) and an incompressible medium 174 (eg, water). The outer skin 170 is mounted to the piston rod. At the end in the cover 175, the cover π is secured to the piston rod 176. The other end of the outer skin is hingedly secured to the movable cover 177, which is slidable over the piston rod 176. The spring 178 presses the cover 177 toward the pressed portion of the chamber 169, and the spring 178 is pressed at the other end toward the washer 179 that is secured to the piston rod 176. The seal edge 167. Figure 110C shows the π〇B in the pump stroke The end of the piston compresses the spring 178'. The same applies to the incompressible medium 174, and the compressible medium 173'. The outer skin 17 (V is deformed and now has a large sealing surface "?," the sealing edge 167 and the chamber It The distance a between the axes of the core is approximately 430/ of the distance a at the beginning of the stroke. Fig. 111A, Fig. U1B, Fig. 1C show a movable direction in the direction of movement of the piston at both ends The piston of the cover, which removes the material balance. This situation is an improvement of the piston in the single-piston pump, but in particular, it is used in a double-operated pump with a stroke of either stroke (and contraction stroke). The piston is possible. The movement of the outer skin during operation is indirectly limited by the air bearing on the piston. These stops are positioned such that the pressure of the medium in the chamber does not allow the piston to peel from the piston rod. . Figure 111A shows the longitudinal section of the chamber with the modified piston 208 at the beginning of the stroke and the piston (2〇8,) at the end of the stroke. Figure 111B shows a ninth embodiment of the piston 2〇8. The outer skin of the sphere is equivalent to one of the spheres of Figure j 159 159900.doc -225- 201235565. Now at the top of the cover i9i and at the bottom of the cover = tightly inside the impervious layer. The details of the covers are not shown and all types of assembly methods can be used. Both covers i9i, 192 can translate and/or rotate above the plug 195. This situation can be performed by various methods (e.g., different types of bearings not shown). The cover 191 in the top can only move upward due to the presence of the stop 196 within the piston. The cover 192 in the bottom can be moved only downwards because the stopper 197 prevents upward movement. The "tuning" of the sealing force includes a combination of an incompressible medium 205 in the ball and a compressible medium 206, and a piston 126 operated by a spring force in the piston rod 195. The medium can freely flow through the holes 199, '2〇1 through the J 207 of the piston rod. The beak rings or the like 202, 203 in the cover in the top and bottom of the cover seal the lids 191, 192 to the piston rod, respectively. A cover 204 (shown as a thread assembly at the end of the piston rod 195) secures the piston rod. Depending on the required movement of the outer skin, the equivalent stop can be positioned elsewhere on the piston rod. Figure 111C shows the piston of Figure 111B at the end of the pump stroke. The top cover 191 is moved from the stop 196 by a distance x" against the stop I) to press the bottom cover 192. Compressible medium 206· and incompressible medium 2〇5'β Fig. 1 1 2A, Fig. 112B, Fig. 1 12C show a modified piston with respect to an earlier piston. These improvements are related to better tuning of the sealing force by loading the adjustment member, by a smaller sealing contact surface (specifically, by a smaller cross-sectional area). The improved tuning focuses on the fact that the pressure in the piston is now attributed to one of the same piston rods being directly affected by the pressure in the chamber' and the pressure in the piston is independent of the piston rod 159900.doc •226· 201235565 The pressure effect of the presence of the operating force 1 is that the sealing force is known to be lost. Therefore, the operating force will be: ''', during the stop of the chest stroke in the case of sealing; the big = the end of the 'end' When the strength of the factory in the room is reduced, the contraction =. The stroke of the pump will be easier for i to double the pump as the second "because of lower friction, tongue 窠..., the loading adjustment member can be placed" on both sides of the plug (for example, by this load adjustment member (not shown) The double match of the show). The display of the piston is in accordance with the specifications: for example, in the chamber

An increase in pressure will give an increase in the force in the piston. Other specifications can result in other configurations. The association can be designed such that the increase can be different from the linear association. It is configured to have an equal area, a different size, and/or a change in area by the piston rod. The I is shown as having a small internal overpressure due to the specific fiber structure and the total resulting loading. The shape of the piston in the longitudinal section is a diamond pattern. The two corners of the diamond shape act as a sealing surface in this section, which gives a reduced contact area by the smaller cross-sectional area of the chamber. The size of the contact surface remains It may be increased by the presence of a ribbed outer surface of the piston skin. The wall of the chamber and/or the exterior of the piston may have a coating (e.g., nylon), or may be made of a low friction material. .

Not depicted as having a chamber according to, for example, the cross-sectional shape of FIG. 107F, and the possibility of having (in this case, by way of example) a piston according to, for example, three separate pistons of FIGS. n2A through 112C, Each individual piston seals the other individual pistons and the boundary curve in the first circular cross-sectional area (upper left in Fig. 107F) and at the other point of the longitudinal axis of the chamber, each individual piston seals three convex shapes One of the parts and the other individual pistons (Fig. 7F 159900.doc • 227-201235565 'for example 'upper right)' and at a further point, each individual piston only seals one of the three convex portions. Figure 112A shows a tenth embodiment of a longitudinal section of the piston chamber combination with a piston 222 at the beginning of the stroke in chamber 216 and a piston (222,) at the end of the stroke. Figure 112B shows the pistons which are primarily constructed in Figures 11B and 11C. The outer skin includes outer ribs 210. The outer skin and the inner impervious layer 190 are extruded at the top between the inner portion 21 and the outer portion 212, and the inner portion 211 is screwed together with the outer portion 212. At the bottom, in the case of the inner portion 213 and the outer portion 214, a similar configuration exists. Within the piston, there is a compressible medium 215 and an incompressible medium. The pressure in the piston is tuned by a piston configuration that is directly activated by the pressure of the chamber 216. The piston in the bottom that is connected to the pressurized chamber 216 The 148 is mounted on the piston rod 217, while at the other side, another piston 149 is mounted and the piston 149 is coupled to the medium of the piston 222. The piston rod 217 is guided by a sliding bearing 218, and other bearing types (not shown) may be used. The pistons on either side of the piston rod 217 can have different diameters, and it is even possible to exchange the cylinders 221 in which the pistons are moving by having two chambers of the type according to the invention, by the foregoing The pistons (etc.) also have the type according to the invention. Sealing edge 220. Piston rod 224. The distance d 活塞 between the piston 148 and the orifice (2). Figure me shows the piston at the end of the gm2A's differential stroke and there is still high dust in the chamber. The sealing edge 22〇, the negative trimming configuration, has different distances from the aperture 223 toward the chamber. Pistons 148, and 149•Show 159900.doc •228- 201235565 is positioned at a distance 1 that is greater than the distance from orifice 223 in Figure 112B. Figure 113A' Figures 113B, 113C show a combination of a pump and a pressurized chamber having an elastically deformable wall and a piston having a fixed geometry having different cross-sectional areas. Within the outer casing (e.g., a cylinder having a fixed geometry), the inflatable chamber is positioned, the chamber being inflatable by a medium (incompressible medium and/or compressible medium). It is also possible to avoid this housing. The inflatable wall contains, for example, a cushion-fiber hood composite or a water-impermeable outer skin. The angle of the sealing surface of the piston that is parallel to the axis of movement is slightly greater than the comparative angle of the wall of the chamber. This difference between the angles and the instantaneous deformation of the wall by the piston occurs with a slight delay (by having proper tuning of the invisible medium and/or the load regulating member in the wall of the chamber, for example) , which provides a sealing edge similar to the fact that the pistons have been shown, the distance between the sealing edge and the central axis of the chamber may change during movement between the two pistons and/or chamber positions. . This situation provides a change in the cross-sectional area during the stroke and, by this scenario, provides a change in designable operational force. However, the cross section of the piston in the direction of movement may also be equal, or have a negative angle with respect to the angle of the cavity to the wall. In these cases, the front end of the piston should be rounded. In the last mentioned case, It may be more difficult to provide a change in cross-sectional area, and by this situation it is more difficult to provide a designable operational force. The walls of the chamber may be equipped with all of the load adjustment members that have been shown, the load adjustment member being shown in Figure 112B, and If necessary, the shape adjustment member ❶ = the speed of the plug in the chamber can have an effect on the seal. 159900.doc • 229· 201235565 Fig. 113A shows the piston 23 处 at the four piston positions in the chamber 231. Around the wall is a housing 234 having a fixed geometry. Within the wall 234 is a compressible medium 232 and an incompressible medium 233. There may be a valve arrangement (not shown) for the inflation of the wall. The shape is only an example to show the principle of sealing the edge. In the cross section shown, the distance between the end of the stroke and the beginning of the stroke is approximately 39%. The shape of the longitudinal section can be different from Figure 113B shows the piston after the beginning of the stroke. The distance between the sealing edge 235 and the central axis 236 is ~. The angle between the piston sealing edge 235 and the central axis 236 of the chamber. The wall and center of the chamber The angle V between the axes 236. The angle v is shown to be less than the angle. The sealing edge 235 is configured such that the angle v becomes as large as the angle.... Other embodiments of the piston are not shown. Figure 113C shows during the stroke The piston. The distance between the sealing edge 235 and the central axis 23 6 is Z2 'this distance is less than z ^. Figure 113D shows the piston almost at the end of the stroke. The distance between the sealing edge 235 and the central axis 236 is Z3, which is less than & Figure 114 shows a combination of a wall of a chamber and a piston having a changeable geometry that is adapted to each other during the pump stroke to enable continuous sealing. The chamber shown in Figure 13A is shown. With only the incompressible medium 237 and the piston 222 at the beginning of the stroke, and the piston 222, shown just before the end of the stroke. Also, the size of the piston can be used here. Other embodiments. The correct selection of the speed of the piston and the viscosity of the medium 237 can have a positive effect on the operation. The shape of the chamber shown in the longitudinal section of Figure 14 can also be different. 159900.doc • 230· 201235565 207 Special Preferred Embodiments According to an embodiment of the present invention, there is provided a piston and a chamber surname, wherein: the chamber defines an elongated chamber having a longitudinal wheel line, the chamber 2 having at its first longitudinal position Its first-planted; two-site 〇* μ ^ truncated face area and has its second cross-sectional area at its second longitudinal position, the second cross-sectional area being 95% or less of the first cross-sectional area' The change in face area is at least substantially continuous between the first longitudinal position and the second longitudinal position, and the piston is adapted to

The self-adapting section of the chamber is adapted to move from the first to the longitudinal position of the chamber to the second longitudinal position. Preferably, the second cross-sectional area is between (4) and (10) of the first cross-sectional area. Preferably, the second cross-sectional area is between 7 〇% of the cross-sectional area. Preferably, the second cross-sectional area is about 5% of the first cross-sectional area. Preferably, the 'piston comprises a plurality of at least substantially rigid support members rotatably secured to the common member, the elastically deformable member, the common member and the elastically deformable member being supported by the branch member against the chamber The inner wall is sealed and the support members are at 1 相对 with respect to the longitudinal axis. With 4 〇. Rotate. According to an embodiment of the invention, a combination is also provided wherein the support member is rotatable so as to be at least substantially parallel to the longitudinal axis. . Preferably, the common component is attached to the handle for the operator to extend in the chamber in a direction relatively far from the handle using the jaw member. Preferably, the combination further comprises means for biasing the 159900.doc -23 201235565 floor member against the inner wall of the chamber. Preferably, the piston comprises an elastically deformable container comprising a variable material. Preferably, the deformable material is a fluid or a mixture of fluids such as water, steamed and/or gas or foam. Preferably, in the section through the longitudinal direction, the container has a first shape in a first longitudinal direction and a second shape in a second longitudinal direction, the first shape being different from the second shape. Preferably, at least a portion of the deformable material is compressible, and wherein the first shape has an area greater than the area of the second shape. Preferably, the deformable material is at least substantially incompressible. Preferably, the 'piston comprises - a chamber in communication with the deformable volume, the chamber having a variable volume. Preferably, the volume can be changed by the operator. 〇

Preferably, the chamber includes a spring-biased piston defining a volume of the chamber such that the second longitudinal position of the chamber is between

Preferably, the combination further comprises a pressure associated with the fluid of chamber t and a member associated with the pressure of the piston and the fluid. Preferably, the defining member is adapted to define a pressure in the chamber that is at least substantially the same as the pressure between the piston and the second longitudinal position of the container. Preferably, the first cross-sectional shape is different from the second cross-sectional shape. The change in the cross-sectional shape of the chamber is substantially continuous between the first longitudinal position and the second longitudinal position. Preferably, the first cross-sectional area is at least 5% larger than the second cross-sectional area compared to 159900.doc • 232·201235565 preferably at least 0% (such as at least 20%), preferably at least 3〇% (such as at least 40%). Preferably at least 5% (such as at least 6%), preferably at least 鸠 (such as at least, such as at least 9%). Preferably, the first cross-sectional shape is at least substantially _, and the cross-sectional shape is an elongated shape (such as an elliptical shape) having a first size, the first dimension being at least 2 times the size of the first dimension. (such as at least 3 times) 'preferably at least 4 times. Preferably, the first cross-sectional shape is at least substantially circular, and wherein the second cross-sectional shape comprises two or more at least substantially elongated (such as convex) portions. Preferably, in the first-longitudinal direction The first circumference of the chamber in the section at the location is (four) to 120% (such as 85% to 115%) of the second circumference of the section at the second longitudinal direction of the chamber, preferably 9〇% to ιι〇 Called such as (four) to 105%) 'better 98°/. To 102%. Preferably, the first circumference and the second circumference are at least substantially identical. Preferably, the 'piston comprises: an elastically deformable material adapted to adapt itself to the cross-section of the chamber when moving from the first to the longitudinal position of the chamber to the second longitudinal position; and - having at least substantially along the longitudinal axis A flat helical spring of the central axis 'the spring is positioned adjacent to the elastically deformable material to support the elastically deformable material in the longitudinal direction. Preferably, the piston further includes a plurality of flat abutment members positioned between the elastically deformable material and the spring, the support members being rotatable along an interface between the projectile and the elastically deformable material. Preferably, the support member is adapted to rotate from the first position to the second position 159900.doc • 233·201235565, wherein in the first position its outer boundary may be included in the first cross-sectional area and wherein in the second position The outer boundary thereof may be included in the second cross-sectional area. According to an embodiment of the invention, a combination of a piston and a chamber is provided, wherein: the chamber defines an elongated chamber having a longitudinal axis, the chamber having its first cross-sectional area at its first longitudinal position and Having at its second longitudinal = position a second cross-sectional area, the first cross-sectional area being greater than the second cross-sectional area 'the change in the facet of the chamber 纟 at least substantially continuous between the first longitudinal position and the second longitudinal position The piston is adapted to adapt itself to a cross-section of the chamber when moving from the first longitudinal position to the second longitudinal position of the chamber, the piston comprising: at least a plurality of at least one of the elastically deformable members rotatably secured to the common component The substantially rigid support member 'common component, the elastically deformable member is supported by the support member against the inner wall of the chamber, the support members being at 丨0 with respect to the longitudinal axis. With 4 〇. Rotate between. According to an embodiment, a combination is also provided wherein the support member is rotatable so as to be at least substantially parallel to the longitudinal axis. Preferably, the common component is attached to the handle for use by an operator, and wherein the support member extends in the chamber in a direction relatively away from the handle. Preferably, the combination further comprises a member for biasing the support member against the inner wall of the chamber, the combination of the piston and the chamber, wherein the chamber defines an elongated chamber having a longitudinal axis, the chamber being The first longitudinal position has its first cross-sectional area and at its second longitudinal position has its second cross-sectional area 'the first cross-sectional area is greater than the second cross-sectional area, the change in the cross-section of the chamber is in the first longitudinal position and The two longitudinal positions are at least substantially continuous 159900.doc • 234·201235565 The longitudinal position moves to the second longitudinal direction. The piston includes a variable 'piston adapted to adapt itself to the first position from the chamber. The cross section of the chamber, the elastically deformable container of the shaped material. Preferably, the deformable material is a fluid or a mixture of fluids such as water vapor K and/or gas or foam. Preferably, in the cross section extending through the longitudinal direction, the container has a first shape in the first longitudinal direction and a second shape in the second longitudinal direction, the first shape being different from the second shape.

Preferably, at least a portion of the deformable material is compressible, and wherein the first shape has an area greater than the area of the second shape. Preferably, the deformable material is at least substantially incompressible. Preferably the 'piston comprises - a chamber in communication with the deformable container, the chamber having a variable volume. Preferably, the volume can be changed by the operator. Preferably, the chamber includes a spring biased piston. (d) The ground combine step includes means for defining the volume of the chamber such that the pressure of the fluid in the chamber is related to the pressure of the fluid between the piston and the second longitudinal position of the container. The rider's component is adapted to define that the pressure in the chamber is at least substantially the same as the pressure between the piston and the second longitudinal position of the container. Preferably, the container comprises an elastically deformable material comprising a reinforcing member. Preferably, the reinforcing member comprises fibers. Preferably, the foam or fluid is adapted to be provided in the container during translation of the piston from a first-longitudinal value of 159900.doc • 235·201235565 to a second longitudinal position or from a second longitudinal position to a first longitudinal position. Higher than the highest (four) pressure of the surrounding atmosphere. Preferably, the chamber defines an elongated chamber having a longitudinal axis, the chamber having its first cross-sectional shape and area at its first longitudinal position and its second cross-sectional shape and area at its second longitudinal position. A cross-sectional shape is different from the second cross-sectional shape, the change in the cross-sectional shape of the chamber being at least substantially continuous between the first longitudinal position and the second longitudinal position, the piston being adapted to move from the first longitudinal position of the chamber Adapting itself to the cross section of the chamber to the second longitudinal position. Preferably, the first cross-sectional area is at least 5% greater than the second cross-sectional area, preferably at least 10% (such as at least 20%), preferably at least 3% (such as at least 4%), preferably at least 50% ( Such as at least 6〇%), preferably at least? 〇% (such as at least 80% 'such as at least 9000%). Preferably, the first cross-sectional shape is at least substantially circular, and wherein the second cross-sectional shape is an elongated shape (such as an elliptical shape) having a first dimension that is at an angle to the first dimension At least 2 times (such as at least 3 times), preferably at least 4 times. Preferably, the first cross-sectional shape is at least substantially circular, and wherein the second cross-sectional shape comprises two or more at least substantially elongate (e.g., convex) portions. Preferably, in the section at the first longitudinal position, the first circumference of the chamber is 120% (such as 85% to 15%) of the second circumference of the section at the first longitudinal direction of the cavity, Preferably, 9% to 〇% (such as 95% to 105%)' is preferably 98% to 102%. 159900.doc • 236· 201235565 Preferably, the first circumference and the second circumference are at least substantially identical. Preferably, the piston comprises: a plurality of at least substantially rigid support members rotatably secured to the common member, the elastically deformable member, the common member and the elastically deformable member being supported by the support member against the inner wall of the chamber And sealed. Preferably, the piston comprises: an elastically deformable container, the container comprising a deformed material. According to another embodiment of the present invention, a combination of a piston and a chamber is provided, wherein: the chamber defines an elongated chamber having a longitudinal axis, the chamber having a first cross-sectional area at a longitudinal position thereof And having a second cross-sectional area at a second longitudinal position thereof, the first cross-sectional area being greater than the second cross-sectional area 'the change in the cross-section of the chamber is at least substantially continuous between the first longitudinal position and the second longitudinal position' The piston includes: an elastically deformable material adapted to adapt itself to a cross-section of the chamber when moving from a first longitudinal position to a second longitudinal position of the chamber; and - having at least substantially a longitudinal axis a flat spiral spring that supports the elastically deformable material in the longitudinal direction adjacent to the elastically deformable material. Preferably, the 'piston advance step includes a plurality of flat branches positioned between the discs of the deformable material. The material reading member is rotatable along an interface between the spring and the elastically deformable material. Preferably, the member is adapted to rotate from the first position to the second position, wherein in the first position its outer boundary may be included in the first cross-sectional area 'and wherein in the second position its outer boundary may be included The second section area is 159900.doc -237- 201235565 within the domain.

According to an embodiment of the present invention, there is provided a combination of a piston and a chamber, the chamber defining an elongated chamber having a longitudinal axis, and the piston being movable in the chamber from a first-longitudinal position To the second longitudinal position, the chamber has at least a portion between the first longitudinal position and the second longitudinal position along the inner wall of the chamber - elastically deformable [the chamber is located at the first longitudinal position of the chamber at the piston bore The first longitudinal position of the chamber has its first cross-sectional area and at its second longitudinal position has its second cross-sectional area when the piston is positioned at the position of the chamber, the first cross-sectional area being greater than the first: Face Area 'When the piston moves between a first longitudinal position and a second longitudinal position, the change in the cross-section of the chamber is at least substantially continuous between the first longitudinal position and the second longitudinal position. Preferably the piston is made of a material that is at least substantially incompressible. Preferably, the piston has a shape in the cross section that tapers in a direction from the second longitudinal position along the longitudinal axis. ^ Ground cavity to include: an outer support structure enclosing the inner wall, and a fluid contained by a space defined by the outer support structure and the inner wall. The embodiment according to the present invention provides a pump for pumping fluid. Pump 3. A combination according to any of the foregoing technical solutions, a member for occluding a position from the cavity to the outside, a fluid inlet connected to the chamber and the bag member, and a connection to the cavity The fluid outlet of the chamber. The engagement member also has an outer position and an inner position at which the piston is at its first longitudinal position, at which the piston is at its second longitudinal position. 159900.doc • 238·201235565 Internal position at which the engagement member preferably has an outer position and an outer position where the piston is at its second longitudinal position and the piston is at its first longitudinal position. According to an embodiment of the present invention, a shock absorber is provided, each of which has a combination as described above, and a member for engaging a piston from a position outside the chamber has a member An outer position and an inner position at which the piston is at its first longitudinal position, at which the piston is at its second longitudinal position.

Preferably, the shock absorber further comprises a fluid inlet connected to the chamber and including a valve member. Preferably, the shock absorber further comprises a fluid outlet connected to the chamber and comprising a valve member. Preferably, the chamber and the piston form an at least substantially sealed cavity containing a fluid, the fluid being compressed when the piston is moved from the first longitudinal position to the second longitudinal position. Preferably, the shock absorber further comprises A member for biasing the piston toward the first longitudinal position. According to an embodiment of the present invention, there is also provided an actuator comprising: a combination as described above, a member for engaging a piston from a position outside the chamber for introducing a fluid to The chamber is adapted to displace the member of the piston between the first longitudinal position and the second longitudinal position. Preferably, the actuator further includes a fluid inlet coupled to the chamber and including a valve member. Preferably, the actuator further includes a fluid outlet connected to the chamber and including a valve member 159900.doc • 239-201235565. Preferably, the actuator further includes means for biasing the piston toward the first longitudinal position or the second longitudinal position. Preferably, the introduction member includes means for introducing the pressurized fluid into the chamber. Preferably, the introduction member is adapted to direct a combustible fluid, such as gasoline or diesel, to the chamber to the towel and wherein the actuator further comprises means for combusting the combustible fluid. Preferably, the actuator according to the invention further includes a crank adapted to translate the translation of the piston into a rotation of the crank. 653 DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 201A shows a longitudinal section of a non-moving non-vango pressure piston 5 at a first longitudinal position of the non-pressurized chamber 1 at which the chamber has a circle of constant radius Shape section. The piston 5 may have a production size of substantially the diameter of the cavity to 1 at this first longitudinal position. Show piston 5* when pressurized to a certain pressure level. The pressure within the piston 5* results in a certain contact length. Figure 201B shows the contact pressure of the piston 5* of Figure 2〇iA. The piston 5* can be stuck in this longitudinal position. 2A shows a non-moving non-pressurized piston 5 at a first longitudinal position of the non-pressurized chamber 1 and a piston 5 at a second longitudinal position, the longitudinal section 'chamber in the first longitudinal direction Both the position and the second longitudinal position have a circular cross section with a constant radius. The piston 5 can have a production size which is generally the diameter of the chamber 1 at this first longitudinal position. The piston 5 exhibits a piston 5 that is uncompressed and positioned in a smaller cross section of the second longitudinal position. 159900.doc • 240· 201235565 Figure 202B shows the contact pressure of the piston 5' on the wall of the chamber in the second longitudinal position. The piston 5' can be snapped at this longitudinal position. Figure 202C shows a longitudinal section of the non-moving non-pressurized piston 5 at the first longitudinal position of the non-pressurized chamber 1 and the piston 5 at the second position, the chamber being in the first longitudinal position and Both of the longitudinal positions have a circular cross section with a strange radius. The piston 5 may have a production size of approximately direct to chamber 1 at this first longitudinal position. The piston 5'* shows a piston 5 that is pressed into the smaller section of the second longitudinal position and pressurized to the same level as the level of Figure 1A. Figure 202D shows the piston 5, * in the second longitudinal position of the chamber. Contact pressure on the wall. The piston 5, * can be stuck in this longitudinal position: the friction can be 72 kg. Figure 203A shows the piston 5 of Figure 201A and the deformed piston 5"* when pressurized to the same pressure level as the piston 5* of Figure 2A. When the piston may not have a member that restricts the extension, the deformation is caused by the pressure in the chamber 丨*, which is mainly in the vertex direction (the longitudinal direction of the chamber). Figure 203B shows the contact pressure. The piston 5"* can be stuck in this longitudinal position. Figure 204A shows the longitudinal wear surface of the piston 2 in the second longitudinal position of the non-pressurized chamber 10 having a circular cross section. The piston 15 may have a production size that is substantially the diameter of the chamber 10 at this second longitudinal position. The piston 15,* exhibits a deformed piston 15 that is pressurized to a certain level. The deformation is attributed to the fact that the Young's modulus of the hoop direction (in the cross-sectional plane of the chamber) is selected to be lower than the Young's modulus of the apex direction (in the longitudinal direction of the chamber). Figure 204B shows the contact pressure on the wall of the piston 15,*. This contact pressure guide 159900.doc •241 _ 201235565 Causes appropriate friction (4.2 kg) and a suitable seal. Figure 204C shows the longitudinal section of the piston 15 at the second longitudinal position (production size) of the non-pressurized chamber 及 and the pressurized μ"* at the first longitudinal position, the piston 15" There is the same pressure as when the piston 15, * is positioned at the second longitudinal position of the chamber 1 (Fig. 4A). Again, here is the deformation in the loop direction & is different from the deformation in the direction of the apex. Figure 204D shows the contact pressure on the wall of the piston 15". This contact pressure results in proper friction (〇·7 kg) and proper sealing. Thus, within the selected limits of the diameter of the section in this experiment, it is possible to seally move the piston comprising the elastically deformable container from the smaller cross-sectional area to the larger cross-sectional area while having the same internal pressure. Figure 205A shows the piston 15 of the piston 15 (production size) and the second longitudinal position of the non-pressure chamber 1 , the longitudinal section of the piston 15 of the *, is showing the deformation of the piston 15 of the piston 15 when pressurized structure. The pistons 15, 15, * are attached to the imaginair piston rod at the lower end to prevent movement of the piston during application of the chamber pressure. Figure 205B shows the contact pressure of the piston 15, * of Figure 205A. This contact pressure is low enough to allow movement (friction of 4.2 kg) and is suitable for sealing. Figure 205C shows the longitudinal section of the piston 15 (production size) and the piston 15"* which is pressurized and deformed by the chamber pressure at the second longitudinal position of the pressure chamber 1〇*. The pistons 15, 15, * are attached to the fictitious piston rod at the lower end to prevent movement of the piston during application of the chamber to pressure. The deformed piston 丨5 " * is approximately twice as long as the non-deformable piston 15. Figure 205D shows the contact pressure of the piston 15"* of Figure 205C. This contact pressure 159900.doc -242- 201235565 is low enough to allow movement (friction 3.2 kg) and is suitable for sealing. Therefore, when the chamber pressure is applied to the piston including the pressure-sensitive elastically deformable container, it is possible to seally move at least at the longitudinal position having the smallest sectional area. The extension due to the applied chamber force is large and it may be necessary to limit this stretching. Figures 206 through 209 illustrate the limitations of the extension of the piston skin which can result in a contact area that is sufficiently small to properly seal and a frictional force that is low enough to permit movement of the piston. When the container may or may not be subjected to the pressure in the chamber and allow for expansion in the transverse direction (when moving from the second longitudinal position of the chamber to the first longitudinal position) and in particular to allow for contraction (moving in the opposite direction) Time) 'This limit contains the limit of the extension in the longitudinal direction. The extension of the wall of the bar type piston in the longitudinal direction can be limited by several methods. This limitation can be made by reinforcing the walls of the container using, for example, fabric and/or fiber reinforcement. This restriction can also be made by the expansion body (which limits the expansion of the expansion body) located inside the chamber of the container when the expansion body is connected to the wall of the container. Other methods can be used, such as pressure management of the chamber between the two walls of the container, pressure management of the space above the container, and the like. The reinforcement can also be located outside the piston. The expansion behavior of the walls of the container may depend on the type of extension limit used. In addition, the retention of the piston that moves over the piston rod during expansion can be guided by a mechanical stop. The positioning of the stop can depend on the use of the piston chamber combination. This may also be the case where the container is guided over the piston rod when it is expanded and/or subjected to an external force. It is possible to use all kinds of fluids·compressible and incompressible media, 159900.doc -243· 201235565 combination, compressible media only, or only incompressible media. Since the change in the size of the container can be substantially expanded from the smallest cross-sectional area (with its production size) and at the maximum cross-sectional area, the chamber in the container and, for example, the first enclosed space in the piston rod Connectivity can be necessary. In order to maintain the pressure in the chamber, the first enclosed space may also be pressurized during the volume change of the chamber of the container. Pressure management for at least the first enclosed space may be required. 206A shows a longitudinal section of a chamber 186 having a concave wall 185 and a pneumatic piston, the inflatable piston including a container 208 at a first longitudinal position in the chamber 186 and a second longitudinal position in the chamber 186. Container 2〇8,. The central axis of the chamber 186 is 184. The container 2 is shown in its production size, the container 208 is roughly of its production size when pressurized, and has a fabric reinforcement 189 in the alcove outer skin us. During the stroke beginning at the second longitudinal position of the chamber 186, the wall 87 of the container expands until the stop configuration causes the movement during the stroke to be discontinuous, which may be the fabric reinforcement 189 and/or the exterior of the container 208 Mechanical stop 196 and/or another stop configuration. And thus the expansion of the container 208 is stopped. Depending on the pressure in the chamber 186, the longitudinal extension of the wall of the container can still occur due to the pressure exerted by the chamber 186. However, the first major function of the fabric reinforcement limits this longitudinal extent of the wall 87 of the container 2〇8. It results in a second primary function of the small contact area fabric reinforcement 189 to allow for contraction when the container is being moved to the second longitudinal position (and vice versa where necessary for expansion). During the stroke, the pressure in the containers 2〇8, 2〇8· can be kept constant. This pressure is dependent on the change in volume of the containers 2〇8, 2〇8 and thus depends on the change in length of the circumference of the section 159900.doc • 244· 201235565 of the chamber 186 during the stroke. It is also possible that the pressure changes during the stroke. It is also possible that the pressure changes during the stroke, depending on or not depending on the pressure in the chamber 丨%. Figure 206B shows a first embodiment of an expanded piston 2〇8 in a first longitudinal position of the chamber 186. The wall 187 of the container is formed by stacking a flexible material outer skin 188 with a fabric reinforcement 189 that allows expansion and contraction, and the flexible material may be, for example, a rubber type or the like. The direction of the fabric reinforcement with respect to the central axis 184 (= braid angle) is different from 54.44. Changes in the size of the piston during the stroke do not necessarily result in the same shape as drawn. Due to the expansion, the thickness of the wall of the container can be less than the thickness of the wall of the container as produced at the second longitudinal position of the chamber 186. A water impermeable layer 190 may be present within the wall 187. It is pressed tightly into the lid 191 at the top of the container 2〇8, 2〇8, and the lid 192 at the bottom. &Show the details of the covers and use all types of assembly methods' These methods may be able to adapt themselves to the varying thickness of the walls of the container. Both covers 191, 192 may be capable of translating and/or rotating over the piston rod 195. Such movement can be performed by various devices such as, for example, different types of bearings not shown. The lid 191 in the top of the container can be moved up and down. A stop 196 on the piston rod 195 that is external to the container 208 limits the upward movement of the container 208. The cover 192 in the bottom can only be moved downwards, since the stop member 197 prevents upward movement, this embodiment can be considered to be used in the piston chamber # for pressure in the chamber 186 below the piston. Other configurations of the stop t may be possible in other pump types (such as 'dual work dishes, vacuum pumps, etc.) and only depend on design specifications. Used to enable and/or limit the piston relative to the piston rod 159900.doc •245 · 201235565 Other configurations for relative movement may occur. The tuning of the sealing force may comprise a combination of the incompressible fluid 2〇5 and the compressible fluid 206 inside the container (both of which are also a possibility) but the chamber 2〇9 of the container may be associated with the second chamber 210 In communication, the second chamber 210 includes a spring force operated piston 126 inside the piston rod 195. Fluid can flow freely through the bore 2 through the wall 207 of the piston rod. It may be possible for the second chamber to communicate with the third chamber (see Figure ι2), but the pressure inside the container may also depend on the pressure in the chamber 186. The container can be inflated via the piston rod 195 and/or by communicating with the chamber 186. The lids or the like in the lid and the bottom of the top, 2, 2, 2, 3, respectively, seal the lids 191, 192 to the piston rod. The cap 2 (shown as a thread assembly at the end of the piston rod 195) secures the piston rod. A comparable stop can be located elsewhere on the piston rod depending on the desired contact area 198 between the wall of the container and the wall of the chamber. Figure 206C shows the piston of Figure 2 at a second longitudinal position of the chamber. The cover 191 in the top moves from the stop 196 by a distance a. The spring force operated valve piston 126 has moved a distance b. The bottom cover i 92 is shown adjacent to the stop member 197. When there is pressure in the chamber 186 below the piston, the chamber 186' can be pressed against the stop member ^ 97 ^ compressible fluid 2 〇 6 · and the incompressible fluid 205, Figure 206D is a 3D pattern and shows a reinforcing matrix of fabric material that allows the walls of the containers 208, 208 to elastically expand and contract as they move in a sealed manner in the chamber 186. The fabric materials can be elastic and placed on top of each other in separate layers. «Hai special layers can also be woven and placed together. The angle between the two layers can be different from 159900.doc -246- 201235565 54°44'. When the material types and thicknesses of all layers are the same, and even if the number of layers is the same, the expansion and contraction of the walls of the container may be equal in the XYZ direction when the stitch lengths in each direction are equal. When the expansion of the stitch lengths ss and tt on each of the directions of the substrates will become large, the contraction of the stitches ss and tt will become smaller. Because the material of the yarn can be elastic, another device (such as a mechanical stop) that is used to stop expansion may be necessary. The stop member can be the wall of the chamber and/or be shown as a mechanical stop on the piston rod, as shown in Figure 206B. Figure 206E is a 3D pattern and shows the expanded matrix of Figure 2〇6D that has been expanded. It is larger than the stitch length ss and the stitch length ss of U, and tt. The result of shrinkage can result in the matrix shown in Figure 2〇6〇. Figure 206F is a 3-dimensional drawing and shows a reinforcing matrix of fabric material which may be made of non-elastic yarns (but elastically bendable) and placed on top of each other or braided together in separate layers. Expansion is possible because of the extra length of each loop 700, an extra length is obtained when the container is in production size, and is also compressed when located at the second longitudinal position of the chamber. The stitch length in each direction - and (9). The non-elastic material (but elastically bendable) can limit the maximum expansion of the wall 187 of the container 217 as the wall of the container expands. It may be necessary to stop the movement of the bar 217 above the piston rod 195 by, for example, a striker 196 so that the seal can be maintained. The lack of this stop 196 gives the possibility of forming a valve. Figure 206G is a 3D pattern and shows the reinforced matrix of Figure 2 of the swelled gland. A in the stitch length of SS" and U"~" and 『. The result of shrinkage can result in the matrix shown in Figure 206F. I59900.doc • 247· 201235565 Figure 206H shows three stages I, II and III of the production process for a piston containing an elastically deformable container. The rubber pad 401 is positioned over the rod 400, such as the reinforcing pad 402 of the reinforcing pad of Figures 406E through 406G, positioned over the rubber pad 401. On top of the last mentioned pad, another rubber pad has been positioned. Between the pad 401 and the stem, one or more covers 404 can be positioned. All pads can slide over the rod 400. Rod 400 can be hollow and can be connected to a source of high pressure steam. Stage II: Pressurized steam can enter the cavity 408 of the oven 406 by an outlet 405 that can be positioned at the end of the rod. A complete rubber/reinforcement liner 407 can be cut and transported over the rod 400 into the cavity 408. The cavern can then be closed and pressurized steam is injected into the cave. Sulfurization can occur which involves mounting the walls of the container to the lid 404. The pad can be in the form of a bend. After vulcanization, the cavern can be opened and the vessel (III), which has its production size, can be pushed out. In order to use the vulcanization time of the piston to produce other pistons, several methods can be used. The bulging of the rubber pad 407 (complete: including the fabric reinforcement) can occur prior to vulcanization. The rod 400 can be divided into sections, each section being approximately the height of the container at its production size. Each part can be detached from the main pole before entering the cave. And/or, there may be a plurality of cavities at the end of the production feed line which may each erect, receive a complete liner 407 and vulcanize the liner 407. This can be achieved by rotating and/or translating the cavity to and from the end of the production feed line. It may also be possible to integrate several vulcanization caverns into the production feed line. Figure 207A shows a longitudinal section of a chamber 186 having a concave wall 185 and an inflatable piston containing a container 159900.doc-248-201235565 217 at a first longitudinal position of the chamber and at a second longitudinal position Container 217,. The container 2i7| exhibits its approximate production size when pressurized. The figure shows the expanded piston 217 in the first longitudinal position of the chamber. The wall 218 of the present body is made of an elastic material sheath 216 (which may be, for example, a rubber type or the like) and a fiber reinforcement 219 according to the lattice shape. The effect build up into a 'fiber stiffener 219 that allows expansion of the container wall 218. The direction of the fiber with respect to the central axis 184 (= braid angle) may differ from 54.44. The contact area 2 ι between the wall 218 of the container 217 and the wall 185 of the chamber 186. Due to the expansion, the thickness of the wall of the container may be less than (but not necessarily very different from) the thickness of the wall of the container as produced at the second longitudinal position. An impermeable layer 190 may be present inside the wall. It can be squeezed tightly into the lids 191 of the tops of the containers 2, 217, and the lids 192 of the bottom. The details of the f-cover are not shown and all types of assembly methods can be used, and such methods may be able to adapt themselves to the varying thickness of the wall of the container. Both covers 191, 192 can translate and/or rotate above the piston rod 195. Such movements can be made by various methods, such as, for example, different types of shafts not shown. The cover 191 in the top can be moved up and down until the stop 214 limits the movement. The cover 192 in the bottom is only movable downwards, since the stop 197 prevents upward movement, this embodiment is contemplated for use in a piston chamber device having pressure in the chamber 186 below the piston. Other configurations of the stop may be possible in other pump types (such as dual working pumps, vacuum pumps, etc.) and only depend on design specifications. Other configurations for enabling and/or limiting the relative movement of the piston relative to the piston rod may occur. During the stroke, the pressure within the vessels 217, 217 can be kept constant. Also 159900.doc -249- 201235565 It is possible that the pressure changes during the stroke. The tuning of the sealing force may comprise a combination of the incompressible fluid 205 and the compressible fluid 2〇6 inside the container (both of which are also a possibility), but the chambers 215, 217, the chamber 215 may be the first The chamber is connected to 210, and the second chamber 21A includes a spring force operated piston 126 inside the piston rod 195. Fluid can freely flow through the wall 2 of the piston rod through the bore 2〇1. The second chamber may be in communication with the third chamber (see Figure 21A), but the pressure inside the barrel may also depend on the pressure in the chamber. The container may be inflated via the piston rod 195 and/or by communication with the chamber 186. The shackles in the cover and the similarly shaped members 202, 203 in the cover in the top and the bottom of the cover seal the caps 191, 192 to the piston rod, respectively. The piston rod 2 (shown as a thread assembly at the end of the piston rod 195) is fastened to the piston rod. Figure 207C shows the piston of Figures 2-7b at a second longitudinal position of the chamber 186. The contact area 21 is small. The cover 191 is moved from the stopper 216 by a distance c. The spring force operated valve piston 126 has moved a distance. The bottom cover 192 is shown adjacent to the stop member 197, and if there is pressure in the chamber 186, the bottom cover 192 presses the stop member 197. The compressible fluid 2〇6, and the incompressible fluid 205·, may have a varying volume in the container. 208A, 208B, and 2B (consideration: the construction of the same piston as the pistons of Figs. 207A, 207B, and 207C except for the following cases: the reinforcement is composed of any type of reinforcing member, and the reinforcement The members may be squeakable and may be in a reinforced "column" pattern that does not intersect each other. This pattern may be one of the patterns parallel to the central axis 184 of the chamber 186, or a portion of the reinforcing member may be in the center One of the patterns in the plane of the axis 184 0 159900.doc • 250- 201235565 FIG. 208A shows a container 228 including a first longitudinal position of the chamber 186 and a container 228 at a second longitudinal position of the chamber 186. 'Inflatable piston, pressurized, wherein the inflatable piston has its production size without pressure 〇 Figure 208B shows the container 228 in the first longitudinal position of the chamber 186. The wall 221 of the container contains an elastomeric material 222, 224 and reinforcing member 223 (e.g., fibers). A water impermeable layer 226 may be present. The area of contact between the container 228 and the wall 185 of the chamber 186. Figure 208C shows the container 228' in a second longitudinal position of the chamber 186. Contact area 225' may be slightly larger than the contact area 225. The top cover 191 has been moved from the stop 214 to e'. Figure 208D shows the first longitudinal position and the second longitudinal position of the chamber 186, respectively, having reinforcing members 223 and 223" A top view of the pistons 228 and 228'. Figure 208E shows a top view of a piston similar to one of the pistons 228 and 228', respectively, in a first longitudinal position and a second longitudinal position of the chamber 186, the pistons having An alternative embodiment of the reinforcing members 229 and 229'. One portion of the stiffener is not in the plane passing through the central axis 184 in the longitudinal direction of the chamber 186. Figure 208F shows the reinforcement 227 and 227' in the wall of the container. Similar to the top view of the piston of one of 228 and 228', the stiffener is located in a plane that does not pass through the central axis 184 of the chamber 186. During the stroke, the wall of the container rotates about the central axis 184. Figure 208G is a schematic representation How many fibers 802 can be mounted in the cave 159900.doc-251 - 201235565 43 1 of the cover 430. This can be achieved by rotating the cover and the fiber about the central axis 433, the cover and the fiber can have At its own speed, but facing and pushing the fiber 432 in the cavity 431. Figure 209A shows a longitudinal section of a chamber 186 having a convex wall 185 and an inflatable piston 'the inflatable piston comprising a container 258 at the beginning of the stroke and At the end of the stroke, the container 258, the pressurized container 258, is in the second longitudinal position. Figure 209B shows the longitudinal section of the piston 258, the piston 258 has a reinforcing sheath 252 'reinforced outer skin 252 by a plurality of at least elastically deformable flaps The member 254 is rotationally secured to the common member 255, the common member 255 is coupled to the pistons 258, 258, and the outer skin 252 is in a stretched condition and depends on the hardness of the material 'which has a particular maximum stretch length. This finite length limits the extension of the piston skin 252. The common component 255 can slide over the piston rod 195 with the sliding member 256. For the remainder, it is a construction equivalent to that of the pistons 208, 208'. Contact area 253. Figure 209 (: shows the longitudinal section of the piston 25 8 | contact area 2531. Figures 210 to 212 discuss the management of the pressure inside the container. The pressure management system piston chamber of the piston containing an inflatable container with an elastically deformable wall An important part of the chamber construction. Pressure management must involve maintaining the pressure in the vessel in order to maintain the seal to an appropriate level. This means that during the per-stroke of the volume change of the vessel, and from a long-term perspective, ##自容器的Leakage can reduce the pressure in the container 'it can affect the milton force. Money flow can be a solution. When the container changes volume during the stroke, the fluid flow is tied to and from the container' and/or to the container (inflated) The volume change of the container can be balanced by a change in the volume of the first enclosed space that communicates with the volume 159900.doc - 252. 201235565 via, for example, a hole in the piston rod. The pressure can also be balanced at the same time. And this can be done by a spring-operated piston that can be positioned in the first enclosed space. The spring force can be enclosed by a spring or pressurized enclosure (eg, a second enclosed space) The pressurized enclosed space is in communication with the first enclosed space by a pair of pistons. Any type of force can be passed by each of the pistons (eg, by a second enclosure) The space and the combination of pistons in the second enclosed space are configured such that when the pair of pistons move toward the first enclosed space (eg, when fluid is moving from the first enclosure to the container) Time), the forces on the pistons in the first enclosed space remain equal, and the forces on the pistons in the second enclosed space decrease. In the second enclosed space, 'this situation is well followed by the ρ constant The tuning of the pressure in the chamber of the vessel during all or part of the stroke can also be effected by the communication of the chamber with the chamber of the vessel. This has been described in WO 00/65235 and WO 00/70227. The grain can be inflated via a valve in the piston and/or a handle of the piston rod. The valve can be a check valve or an inflation valve (eg, a Schrader valve). The container can be inflated via a valve that communicates with the bore. If an inflation valve is used, the Schrader valve avoids > female leaks Safety and its ability to allow control of all types of fluids are preferred. It may be necessary to cause Sb to inflate (for example, a valve actuator disclosed in W〇99/26002 or US 5,094,263). The valve actuator of WO 99/26002 has the advantage that it can be inflated by very low forces, so it is extremely practical in the case of manual inflation. Furthermore, in combination with a valve with a spring-operated valve core, The valve automatically closes when equal pressure levels have been obtained. 159900.doc -253· 201235565 If the pressurized volume flows from the enclosed space to the container and the flow from the container to the enclosed space can be substantial, then there is greater than the envelope The volume of the volume of the space and the pressure/volume source equal to or lower than the pressure level of the pressure in the vessel may be preferred. In the last mentioned condition, the volume of the pressure source can be reduced as compared to a pressure source having a pressure rating equal to the pressure level of the container. Where the pressure level in the pressure source is higher than the pressure level in the vessel, it may be necessary that during the stroke, the fluid between the pressure/volume source and the vessel may be directed by means of a valve. These valves may have a core pin that is operable by an actuated spring force. The actuator can open/close the valve with respect to even continuously changing the flow. An example is a similar configuration for inflating the container due to a drop in pressure by leakage (see next page). Other valve type and valve guiding solutions are possible. This may also be a method of continuously maintaining the pressure level in the vessel at a predetermined level. The valve is communicated with the chamber and the automatic inflation of the granulator is enabled when the pressure in the container is lower than the pressure in the chamber. When this may not be the case, the more moderate pressure in the chamber may be temporarily formed by closing the outlet valve in the chamber adjacent the chamber in the second longitudinal position of the container. This closing and opening can be performed, for example, by pedaling manually. The pedal is open and a passageway in communication between the valve actuator (WO 99/26002) and, for example, the Schrader valve. When open, the valve actuator is movable, but lacks the force of the core pin that operates the spring force of the valve, and thus the Schrader valve may not be open, so that the chamber can be closed and any high pressure can be gradually formed so that The container can be inflated. When the passage is closed, the actuator functions as disclosed in WO 99/26002, and the operator 159900.doc -254 - 201235565 ° checks the pressure of the container by means of a pressurized juice (for example, a pressure gauge). This: the opening and closing of the room can also be carried out automatically. In this case, the closing of the outlet can be initiated by the member of all kinds of f. The material member is measured by the amount of the borrowing type which is purely the value of the devaluation (four) force.

The automatic inflation of the container to a predetermined value can be performed by a combination of a valve in communication with the chamber and, for example, a release valve of the container. The release valve is released, for example, to a space above the container or to the chamber at a predetermined pressure value. Alternatively, the valve actuator of WO 99/2_2 may first be opened, for example, by a combination of a valve actuator and a spring when the predetermined home force value has been reached. Another option may be that the opening to the valve actuator is closed by a piston or cover that is operated, for example, by a spring force when the a force reaches a value above a predetermined value. Alternatively, by combining the piston 292 of Figure 9 211E with the member, the piston opens the passage 297 (not shown) when a certain pressure has been reached. Figure 210A shows a piston chamber system having a piston containing a container 2〇8, 2〇8 according to Figures 206A-206C and a chamber 186 having a central axis 184. The aeration and pressure management described herein can also be used with other pistons that contain the container. The containers 2〇8, 2〇8 can be inflated via the valve 241 in the handle 24〇 and/or the valve 242 in the piston rod 195. If the handle is used instead of, for example, a rotating shaft, the rotating shaft can be hollow to communicate with, for example, a Schrader valve. Valve 241 can be an inflation valve (e.g., a Schrader valve) that includes a bushing 244 and a valve core 245. The valve in the piston rod 195 can be a check valve having a flexible piston 126. The chamber between the check valve 242 and the chamber 209 of the vessel 208, 208' is described earlier as the "second" chamber 210. Pressure gauge 250 enables control of the pressure inside the vessel and does not show other details of 159900.doc • 255· 201235565. The use of this gauge to control the pressure in the chamber 186 may also be possible. It is also possible that the chamber 209 of the vessel 208, 208' has a release valve (not shown) that can be adjusted to a predetermined pressure value. The released fluid can be directed to chamber 209 and/or to space 251. Figure 21B shows an alternative option to the inflation valve 241. Instead of the inflation valve 241 in the handle 240, there may be only the bushing 244 without the valve core 245, which is connected to the pressure source. 210C shows details of the bearing 246 of the stem 247 of the check valve 126. Bearing 246 includes a longitudinal conduit 249 that defines a fluid passageway around rod 247. Spring 248 enables the pressure on the fluid in second chamber 210. Stop 249. 210D shows details of the flexible piston 126 of the check valve 242. Spring 248 maintains the pressure on piston 126. 210E shows a pressure source 451 that can have a pressure that exceeds the pressure level of the container. The inlet valve 452 has, for example, a valve actuator 453 (the configuration 459 shown is similar to one of FIG. 211E (292, 297)), And the outlet valve 454 has, for example, a valve actuator 45 5 (the configuration 45 1 shown is similar to one of the illustrations 211E (292, 297)). Space 460 is coupled to chamber 457 and space 462 is coupled to chamber 458. Valves 452 and 454 can be mounted in a piston rod 456 that can be divided into two chambers 457 and 458. 210F shows the configuration of FIG. 210E in which two black boxes are shown as each containing a valve configuration steerable by an external signal. The manipulator 415 can receive pressure signals 416 from the interior of the pistons at different longitudinal positions of the chamber, respectively. And 41 7. Actuator 415 can send signals 418 and 419 to actuator 422 of outlet valve arrangement 420 and actuator 423 of inlet valve arrangement 421. 159900.doc •256· 201235565 This valve and valve actuation configuration can be similar to the valve and inter-operating configuration shown in Figure 21 IF. 211A shows a piston chamber system having a piston containing a container 248, 248· according to FIGS. 206A-206C and a chamber 186 having a central axis 184, the central portion of the container 248, 248 Same as containers 208, 208'. The aeration and pressure management described herein can also be used with other pistons that contain the grain. The containers 248, 248' can be inflated via a valve in communication with the chamber 186. The valve may be a checkback 242' according to Figures 210A, 210D or it may be an inflation valve, preferably a Schrader valve 26A. The first enclosed space 210 communicates with the chamber 209 in the container through the hole 201, while the first enclosed space 210 communicates with the second enclosed space 243 via a piston arrangement, and the second enclosed space 243 can be For example, an inflation valve similar to the Schrader valve 241 that can be positioned in the handle 24A is inflated. The valve has a core pin 245. If the handle is used instead of, for example, a rotating shaft, the valve core 245 can be hollow and the Schrador valve can be in communication with this passage (not shown). The Schrader valve 26 has a valve actuator 261 according to WO 99/26002. The base 262 of the chamber 186 can have an outlet valve 263 (e.g., a Schrader valve) that can be equipped with another valve actuator 261 in accordance with WO 99/26002. To manually control the exit compartment 263, the base 262 can be provided with a pedal 265 that can pivot the shaft 264 on the base 262 by an angle. The pedal 265 is coupled to the piston rod 267 by a shaft 266 in a non-circular aperture 275 in the top of the pedal 265. The base 262 has an inlet valve 269 (not shown) for the chamber I86. (schematically drawn) the spring 276 holds the pedal 265 in its initial position 277 with the outlet valve remaining open. When the outlet valve remains closed, the pedal 265 is held at its starting position of 277% of the outlet 159900.doc • 257. 201235565 Channel 268. 21B shows details of the communication between the first enclosed space 210 and the second enclosed space 243 by a pair of pistons 242, 270. The piston rods 271 of the pair of pistons are guided by bearings 246. Longitudinal conduit 249 in bearing 246 enables fluid transport from the space between bearing 246 and pistons 242 and 270. A spring 248 can be present. Piston rod 195 having piston type vessels 248, 248' of inner wall 194. The pistons 242, 270 are sealed on the inner wall 194. Figure 211C shows an alternative wall 273 of the piston rod 272 of the piston-type container 248, 248' that is at an angle to the central axis 184 of the chamber 186. The piston 274 is schematically drawn and can adapt itself to the altered cross-sectional area of the interior of the piston rod 272. Figure 211D shows the piston 248' with the outer casing 280 built thereon. The housing includes a Schrader valve 260 having a core pin 245. Valve actuator 261 is shown to depress core pin 261 while fluid can enter valve 260 via passages 286, 287, 288, and 289. The piston ring 279 seals the wall 285 of the inner cylinder 283 when the core pin 245 is not depressed. The inner cylinder 283 can be hermetically sealed by seals 281 and 284 between the outer casing 280 and the cylinder 2 82. Chamber 186. Figure 211E shows a configuration of an outlet valve 263 having a core pin 245 that is shown depressed by a valve actuator 261. Fluid can flow through passages 304, 305, 306, and 307 to the open valve. The inner cylinder 302 is hermetically sealed between the outer casing 301 and the cylindrical body 303 by seals 281 and 284. A passage 297 having a central axis 296 is positioned by the wall of the inner cylinder 302, the wall of the cylinder 303, and the wall of the outer casing 301. At the exterior of the outer casing 301 there is an opening 308 (widened portion 309) of the passage 297 which is energized by the top 294 in the closed position 292 by the top 294. 159900.doc - 258 - 201235565. The piston 292 can be moving in another 'channel 295, which can have the same central axis 296 as the passage 297. The bearing 293 of the piston rod 267 of the piston 292, the piston rod 267, can be coupled to the pedal 265 (Fig. 211A) or to other actuators (shown schematically in Fig. 211E). In addition to the configuration 369 of the outlet valve of control map 211E, FIG. 211F shows the piston 248' of FIG. 211D and the inflated configuration 368. The inflated configuration 368 now also includes a configuration 370 that controls the valve of Figure 211E. This configuration 37 can be performed to close the valve ' when the predetermined pressure has been reached and to open the valve when the pressure is below a predetermined value. The sensor 363 is being actuated in the converter 361 that imparts the k number 362 to the actuator 363. The actuator 363 is actuating the piston 292 via the actuating member 364. When the chamber has a working pressure that is lower than a predetermined pressure value in the piston, the closed and open configuration 369 of the control outlet valve 263 can be via another member 363 via member 367 initiated by signal 365 from converter 361. To control. The measurement of the signal 371 given to the transducers 361 and/or 366 in the chamber automatically detects if the actual pressure of the chamber is below the working pressure of the piston. This can be particularly useful when the pressure of the piston is below a predetermined pressure. Figure 211G schematically shows a cover M2, 312 having a spring 310 attached to the outer casing 3 of the valve actuator 315. The spring 31 〇 keeps the opening 3丨4 tightly closed. The contact area 313 of the cover 312 with the cylinder 282 (Fig. 211D). When the force from the chamber on the cover 312 becomes greater, the cover can be moved to the position shown as the cover 312 until there is equal force in the force of the cover provided by the medium of the chamber. The spring 310 can determine the maximum value of the pressure at which the spool pin 245 is depressed. Schrader valve 260. 159900.doc • 259-201235565 Figure 212 shows an elongated piston rod 320 movable in a bearing 324, a pair of pistons 321, 3M positioned at the end 323 of the piston rod, Figures 213A, 213B, 213C showing the pump and having A combination of a compression chamber of an elastically deformable wall and a piston having a fixed geometry having a different cross-sectional area. Within the outer casing (e.g., a cylinder having a fixed geometry), an inflatable chamber is positioned that is inflatable by a fluid (incompressible fluid and/or compressible fluid). It is also possible to avoid this housing. The inflatable wall contains, for example, a lining_fiber_cover composite, or a water-impermeable outer skin. The angle of the sealing surface of the piston that is parallel to the axis of movement is slightly greater than the comparative angle of the wall of the chamber. This difference between the specific angles and the instantaneous deformation of the wall by the piston occurs with a slight delay (by having proper tuning of the incompressible fluid and/or load regulating member of the wire in the wall of the chamber, for example) , which may provide a sealing edge similar to the fact that the pistons have been shown, the distance between the sealing edge and the central axis of the chamber during movement between the two pistons and/or chamber positions may be change. This situation provides a change in the cross-sectional area during the stroke and provides a change in designable operational force by this situation. However, the cross-section of the piston in the direction of movement may be equal, or the angle of the wall of the chamber may have a negative angle. Under these conditions, the "front end" of the piston may be rounded. The last mentioned; under the brother, it is more difficult to provide the cross-sectional area of the variable, and it is more difficult to provide a designable operating force chamber to the wall by which it can be equipped with all the loading adjustment members that have been shown, The loading adjustment member is shown in Figure 212B and, if necessary, has a shape adjustment J. The speed of the piston in the chamber can have an effect on the seal. 159900.doc -260· 201235565 FIG. 213A shows the piston 23〇 at four piston positions in the chamber 231. Around the inflatable wall is a housing 23 4 having a fixed geometry. Within this wall 234 is a compressible fluid 232 and an incompressible fluid 233. There may be a valve arrangement (not shown) that inflate the wall. The shape of the piston on the uncompressed side is only an example to show the principle of sealing the edge. In the cross section shown, the distance between the end of the stroke and the beginning of the stroke is approximately 39%. The shape of the longitudinal section can be different from the shape shown. Figure 213B shows the piston after the beginning of the stroke. The distance between the sealing edge 235 and the central axis 236 is Z1. The angle between the piston seal edge 235 and the central axis 236 of the chamber. The angle v between the wall of the chamber and the central axis 236. The angle v is shown to be less than the angle. The sealing edge 235 is configured such that the angle v becomes as large as the angle ζ. Other embodiments of the piston are not shown. Figure 213C shows the piston during the stroke. The distance between the sealing edge 23 5 and the central axis 23 6 is z2, which is less than Z1. Figure 213D shows the piston almost at the end of the stroke. The distance between the sealing edge 235 and the central axis 23 6 is z3, which is less than Z2. Figure 214 shows a combination of the walls of the chamber and the pistons having 2-28 modifiable geometries that are adapted to each other during the pump stroke to enable continuous sealing. It has its production size at the second longitudinal position of the chamber. Shown is now the chamber of Figure 213 A with only the incompressible medium 237 and the piston 385 at the beginning of the stroke, while the piston 385 is shown just before the end of the stroke. Again, all other embodiments of the variable size of the piston can be used herein. The correct choice of the speed of the piston and the viscosity of the medium 237 can have a positive effect on the operation. The shape of the chamber shown in Figure 14 is 159900.doc • 261 · 201235565 The shape can also be different. Figures 21A through 21F show an embodiment of a chamber having sections of different sizes. The sections have a constant circumferential extent. This situation is another solution to the stuck problem of the referenced piston of w〇 00/70227. The piston according to claim 1 can also function well in such specific chambers, when the reinforcement of the outer skin allows the portion of the wall of the container to be spaced apart in the longitudinal section of the chamber.

Where the central axes of the chambers are of different sizes, it is also possible to use, for example, a stiffener position of Figure 208D that is substantially parallel to the central axis of the chamber, and when the reinforcement is made of, for example, an elastic yarn (Fig. 206D, 206E) Or when shown in Figures 2〇6F, 206G, each individual size is allowed. The pistons shown in Figures 209A and 209B also function well. A piston having a reinforcing member comprising a non-elastically deformable container or an elastically deformable container having a production size substantially equal to the circumferential length of the first longitudinal position of the chamber can be moved in the chamber without being jammed. Jamming in chambers having different circumferential dimensions in cross section allows the piston to contract under high friction. If the braiding angle of the reinforcing member of the container can be changed to 54.44, it can be elastic

The deformable container becomes otherwise non-elastically deformable (i.e., flexible and deformable but because the container is bendable, it will not be stuck in such chambers) "If the cross-sectional area of the piston and / Or if the chamber between the two pistons changes continuously in the direction of movement but is still large such that the leakage is caused by this situation, it is advantageous to minimize the change of other parameters of the section. This situation can be used by For example, a circular cross section (fixed shape) is used to illustrate that the circumference of the circle is D' and the area of the circle is % d2 (d = diameter of bi). (D), the decrease of D will only give the complex H of the circumference into the 丨β network. q <踝/生 reduction and area reduction twice. Also maintain round 159900.doc •262· 201235565 weeks and only reduce the area even q” This 07 right shape is also fixed (case round) exists a certain minimum area. The shape is a parameter height: the number can be calculated by using the following four-stage expansion method to enter the lamp and/or the cross section of the piston can have any form And this can be defined by at least a curve. The curve is closed and can be used by two The special module parameterized Four-Frequency Expansion method is used to approximate the general-purpose series expansion method for a standard function. / W = Let +J cP^(px)^dpsin(px) where 2 CP =~[f(xJc 〇s( pxjdx 2 dp=~lf(x)^( px)dx

^Sx<2n,x eN P~>〇, p eR cp=the average of the cosine weights 〇ff(x), dp=the average of the sinusoidal weights 〇ff(x), p= indicates the triangular fineness Level maps 215A, 215E show examples of such curves by using different sets of parameters in the following formulas. In these examples, only two parameters have been used. If more coefficients are used, it is possible to find the best curve that meets other important requirements, for example, as a curved transition, the curve of the curved transition has a certain maximum radius and/or (for example) under a given precursor It does not exceed the maximum value of the tension in the seal portion of a certain 159900.doc -263- 201235565 - maximum. As an example: Figure 215F shows the best convex and non-convex curves to be used for the possible deformation of the bounded domain in the plane under the constraint that the length of the boundary curve is fixed and its numerical curvature is minimized. By using the starting area and the starting boundary length, it is possible to expect the smallest possible curvature for a certain desired target area. The piston shown in the longitudinal section of the chamber has been drawn primarily for the condition that the boundary curve of the cross section is circular. That is, the shape of the longitudinal section of the piston may be different in the case where the chamber has a non-circular cross section according to, for example, Figs. 215, 215, and 215F. All types of closed curves can be described by this formula, for example, a c-curve (see PCT/DK97/00223 'Figure ιΑ) β. One of these curves is characterized by the fact that when a line is drawn from a mathematical pole located in the section, the line Will intersect the curve at least once. The curves are symmetrical toward the line in the profile and can also be produced by a subsequent single Fourier series expansion. When the curve of the cross section is symmetrical with respect to the line passing through the mathematical poles in the section, the piston or chamber will be easier to produce. These rule curves can be roughly defined by a single Fourier series expansion method: / (x) = -i. + ^ cpcos( px)

Z where 2 cp = ~ I" f(x)cos( px)dx

^"Sx<2n,x eN P>〇, p eR cp=weighted average 〇ff(x), 159900.doc -264- 201235565 p = indicates the level of triangular fineness. When drawing a line from a mathematical pole, the line will always intersect the curve only once. The specifically formed sector of the cross section of the chamber and/or piston can be roughly defined by the following formula: f(x) = S〇. + ^ Cpcos(3px) 2 p^i where f J~r〇+a.^ sin2C ~~)x • 6χ 1 00 c〇s(3p〇c) dx

7C

^Sx<2%, x eN Ρ^Ο, ρ eR cp = weighted average 〇 ff(x), P = indicates that the section of the triangular fineness level 8 in the polar coordinates is roughly expressed by the following formula: Φ rar〇 + α «I sin(^ φ) where r〇^〇, a>〇, m>0,me , n>0,ne , 〇<φ^2, and where '=the circular section of the start pin The limit of the "petal", ... the radius of the circular section around the axis of the starting pin, 159900.doc 201235565 β = the scaling factor for the length of the "petal", rmax = r〇+ am = used to define the "petal" The parameter of width n = the parameter used to define the number of "petals" Ψ = the angle of the delimiting curve. The entrance is close to (4) the end of the position 'this is attributed to the nature of the sealing part of the piston member. These specific chambers can The die is formed by injection molding and, for example, also by using a so-called superplastic forming process, which is heated and forced by air pressure formed in the tool cavity or also using tool movement. Figure 215A shows the chamber a series of cross sections in which the area is reduced in a particular step' while the circumference remains constant - by A unique modular parameterized Fourier expansion method is defined, and a Four-Frequency expansion method is for a standard function. The section of the initial section of the series is placed at the upper left. The set of parameters used is shown at the bottom of the figure. This series shows the decreasing area of the cross section. The bold numbers in the figure show the decreasing cross-sectional area of different shapes, wherein the cross-sectional area in the upper left corner is taken as the starting area size. The area of the shape of the lower right section is the upper left. The square area is about 28 〇 / 。. Figure 215B shows a longitudinal section of the chamber 162, the cross-sectional area of the chamber 162 is varied by maintaining a circumference along the central axis. The piston 丨 63. ^ also has wall portions 155, 156, The portion of the cross-face of the different cross-sectional areas of 157, 158. The transition sections 159, 160, 161 are between the wall portions. The sections GG, HH and I-Ι are shown. The section GG has a surrounding section and the section H_H 152 has An area approximately between 90% and 70% of the area of the section GG. 159900.doc -266 - 201235565 Figure 215C shows the cross section h_h ! 52 of Fig. 2〇7G and shows the section GG 150 as a dotted line as a comparison. Section H_H Has a large The area between 90 〇/. and 70% of the area of the section gg makes the transition section 151 smooth. The smallest portion of the chamber having about 5% of the wearing area of the section GG is also shown. Figure 215D shows 207G is a cross section I-; [and as a comparison, the section GG is shown by a dotted line. The section W has an area of about 7% of the area of the wearing surface G_G. Make the transition ^ 15 3 smooth. The smallest part of the chamber is also shown. Figure 215E shows a series of cross-sections of a chamber in which the area is reduced in a particular step while the circumference remains constant. These are defined by two unique modular parametric Four-Frequency expansion methods, a Four-Frequency series expansion method. For a standard function. In the upper left is the section of the initial section of the series. The set of parameters used is shown at the bottom of the diagram. This series shows the decreasing area of the cross-section, but it is possible to increase this area by keeping the circumference constant. The bold numbers in the figure show the decreasing cross-sectional areas of different shapes, with the cross-sectional area in the upper left corner as the starting area size. The size of the cross-sectional area at the lower right is about 49% of the initial area of the upper left. Figure 215F shows a convex curve optimized for a fixed length boundary curve and the smallest possible curvature. The general formula of the minimum radius of curvature corresponding to the maximum curvature of the graph shown in Fig. 7L is as follows: r = - (4π A,) The length specified by the following formula is determined by the following formula: y = ~-\jL2 —4π Aj where 159900.doc -267- 201235565 r = minimum radius of curvature L = boundary length = constant A1 = reduced value of the starting domain area aq as an example from Figure 203D. Domain area A 〇 = (3〇 2) and the boundary length L = 60 = 188.5' which corresponds to the area of the disk having a radius of 30 and the length of the boundary. The length needs to be constant, but the area is reduced to the value mountain to be specified. The final configuration should have a convex curve with the smallest possible curvature of the area 丨 = (19/2) 2 = 283.5 ^ boundary curve is as follows: r = 1.54 =1 / r = 0.65 x = 89.4 curve on the graph It is not drawn to scale and the figures only show the principles. The curve can be further optimized by exchanging straight lines from the curve, which improves the piston to wall seal. Figure 216 shows a combination in which the piston includes an elastically deformable container 372 that moves within the cylinder wall 374 and the wedge wall 373 (e.g., shown here around the center axis 370) in the chamber 375. The piston is suspended in at least one piston rod 371. Display containers 372, 372' are at a second longitudinal position (372,) of the chamber and at a first longitudinal position (372). All of the solutions disclosed in this document can also be combined with the type of piston in which the chamber has a circumferentially sized cross section that can be a solution to the jamming problem. Figure 217A shows a convex chamber 38〇 in wall 381. "s" means stroke. Figure 217B shows a forced stroke diagram in the direction shown in Figure 217A. This curve shows the best change in force as the operator pumps during the stroke, the inlet of the fluid in 159900.doc •268· 201235565 is located approximately at the first longitudinal position of the chamber and the outlet is located in the second longitudinal direction of the chamber Location. The curve is roughly tangent to the maximum operating force at the pump stroke. Figure 218A shows an example of a movable power unit 39 that is shown as being movable by a parachute 391 and by wheels 392. Figure 218B shows a movable power unit 39A in which the power unit includes a collection of solar cells 393 at the top and a motor 394. In addition, a water pump 395 and a compressor 396. Manipulation unit 397. 653 Particularly Preferred Embodiments According to an embodiment of the present invention, a piston chamber assembly is provided that includes an elongated chamber bounded by an inner chamber wall and includes a piston in the chamber that will be Sealingly moving at least between the first longitudinal position and the second longitudinal position of the chamber relative to the chamber wall, the chamber having a plurality of sections having a first longitudinal position and the second longitudinal position At least substantially continuous different cross-sectional areas and circumferential lengths at different cross-sectional areas and different circumferential lengths and intermediate longitudinal positions between the first longitudinal position and the second longitudinal position, the cross-sectional area at the second longitudinal position And the circumferential length is smaller than the cross-sectional area and the circumferential length at the first longitudinal position, the cross-sectional area and the circumferential length at the second longitudinal position are smaller than the cross-sectional area and the circumferential length at the first longitudinal position, and the piston comprises a container. The trough is elastically deformable thereby providing different cross-sectional areas and circumferential lengths of the piston in the first longitudinal position and the second longitudinal position of the piston Adapting the different cross-sectional areas of the piston and the different circumferential lengths to accommodate the relative movement between the intermediate longitudinal positions of the piston chambers 159900.doc • 269-201235565 Different cross-sectional areas and different circumferential lengths, wherein: the piston is produced to have a production size of the container in its unstressed and undeformed state, the circumference of the piston in the unstressed and non-deformed state The length is approximately equal to the circumferential length of the chamber (162, 186, 231) at the second longitudinal position. The container is expandable from its production size in a lateral-direction relative to the longitudinal direction of the chamber. Thereby providing the piston to expand from one of its production sizes during the relative movement of the piston from the second longitudinal position to the first longitudinal position. Preferably, the container is inflated and the container is resiliently deformable and inflatable to provide different cross-sectional areas and circumferential lengths of the piston. Preferably, the cross-sectional area of the chamber at its second longitudinal position is between 98% and 5% of the cross-sectional area of the chamber at its first longitudinal position. Preferably, the cross-sectional area of the chamber at its second longitudinal position is from 95% to 15 〇/〇 of the cross-sectional area of the chamber at its first longitudinal position. Preferably, the cross-sectional area of the chamber at its second longitudinal position is about 5% of the cross-sectional area of the chamber at its first longitudinal position. Preferably, the container contains a deformable material. Preferably, the deformable material is a fluid or a mixture of fluids such as water, steam and/or gas or foam. Preferably, the deformable material comprises means for operating a ridge force, such as a spring, preferably in a section through the longitudinal direction, when the container is positioned at the first longitudinal location of the chamber, the stomach The container has a first shape that is different from a second shape of the container when the container is positioned at the second longitudinal position of the chamber 159900.doc • 270-201235565. Preferably, at least a portion of the deformable material is collapsible - the shape has an area greater than the area of the second shape. Preferably, the deformable material is at least substantially incompressible. Preferably, the container can be inflated to a predetermined pressure value. Preferably, the pressure remains constant during the stroke. Preferably, the piston includes between the deformable container and the enclosed space having a variable volume. ^ $ two

Preferably, the volume of the enclosed space is adjustable. The plug preferably has a 'first-enclosed type' comprising a spring biasing force, preferably further comprising a volume for defining the first enclosed space to cause fluid in the first enclosed space A member of pressure associated with the pressure of the second enclosure. ]τ Preferably, the boundary (four) is adapted to define the pressure in the flush space. The enclosure preferably 'defines the member to be adapted to define the pressure in the first enclosure space that is constant during the stroke. Preferably, the <spring biased pressure is applied to the piston system for a checkback, and the fluid of the external pressure source can flow into the first enclosed space through the check valve. Preferably, the fluid from the external source of ink can be accessed through inflation and has a valve (4) biased by a (four) spring, such as a Schrader valve from an external source of pressure, into the second enclosed space. Preferably the 'piston is in communication with at least one valve. 159900.doc •271- 201235565 Preferably, the piston contains a source of pressure. Preferably, the valve is an inflation valve, preferably a valve having a spring biased bias (such as a Schrader valve). Preferably, the valve is a check valve. Preferably, the base of the chamber is connected to at least one valve. Preferably, the outlet valve is an inflation valve, preferably a valve having a spring biased core pin (such as a Schrader valve) that moves toward the chamber when the valve is closed.

Preferably, the core pin of the valve is coupled to an actuator that opens or closes the valve. Preferably, the actuator is for a valve actuator operated by a valve having a spring-loaded spool pin, the actuation n comprising: an outer casing to be connected to a source of pressure, etc., within the outer casing a coupling portion for accommodating a valve to be actuated, a cylinder surrounded by a cylinder wall of a predetermined cylinder wall diameter and having a first cylinder end and a second farther from the lighter portion of the first steam red end a turbo-end end-piston that is movably positioned in the cylinder and fixedly coupled to the actuating pin, the starting pin being (4) fitted with a spool pin that is stored in a purely partially actuated valve, and a conductive pin a passage for conducting pressure medium from the cylinder to the (four) portion when the piston is moved to the first piston position, the piston being at a first predetermined distance from the first cylinder end at the first piston position, and when the piston moves to the first plug position (4) The conduction of the pressure medium between the steam rainbow and the pure portion is suppressed, and the piston is larger from the end of the first cylinder at the second piston position.

(d) a second predetermined distance of the first distance - the middle conduction path is disposed in the cylinder wall and leads to the cylinder at a portion of the cylinder wall having a predetermined cylinder wall diameter and the piston includes a piston ring having a sealing edge, the sealing edge is The 159900.doc • 272·201235565 cylinder wall portion is sealingly engaged whereby the pressure medium is inhibited from being conducted into the passage at the second position of the piston and opening the passage at the first position of the piston. The conduction of the pressure medium during the first piston position is inhibited by the first cylinder position at the first cylinder position, and in the second preferred embodiment, the actuator is used for a valve core operated by a spring force Valve operated valve actuator for a pin 'The actuator comprises: a housing to be connected to a medium source of pressure, a coupling portion within the housing for receiving a valve to be actuated, a cylinder, which is predetermined cylinder a wall of the wall diameter circumferentially surrounding and having a first cylinder end and a second cylinder end that is further from the coupling portion than the first cylinder end and is coupled to a housing for receiving pressure medium from the pressure source, a piston movably positioned in the cylinder and fixedly coupled to the actuating pin for engaging a spring force operated spool pin' and a conductive passage of the valve received in the coupling portion, a second cylinder end and the lightly connected portion are configured to move the medium from the second cylinder end to the _ portion when the piston moves to the first piston position, at a predetermined distance from the first piston position, when the piston moves to

159900.doc -273 . between 201235565 'Through the passage 0 at the first piston position open to the end of the second cylinder preferably 'actuator' is for selectively feeding pressurized air to the container-type piston An actuator valve of an internal container-type piston pressure management system, the valve comprising: a valve body having a cylindrical central passage open to both the pressurized fluid and the interior of the container-type piston, a spring loaded a return valve that is tightly received in the central passage, the spring loaded check valve blocks the central passage when closed and allows fluid to flow when open, a spring loaded

a piston slidably received in the passage above the check valve, the spring loading piston sliding from the closed position toward the check valve to the open position and the pressurized fluid moving when the pressurized fluid is supplied When closed again, the piston circumscribes the surface of the passage with sufficient clearance to allow unrestricted sliding 'but not tight enough to prevent leakage of pressurized fluid between the piston and the central passage surface' a handle Λ carried by the piston and engageable with the check valve to open the check valve and allow pressurized fluid to flow to the check valve and to the interior of the container piston when the piston is moved to the open position, a static plug 'between the check valve and the piston in the central passage, the shank extending through the plug, the static plug being generally axially spaced from the piston in the open position with the piston Connecting, the plug has an exhaust path at a radial point near the shank, the exhaust path being erected from the atmosphere into a space between the plug and the piston such that a force passing through the piston: pressure Flow (four) leaks in When moving, it will not compress between the plug and the piston to delay its movement 'and round (four) shrink seal, which surrounds the exhaust point, and the seal is compressed to the piston and plug when the piston is connected to the plug The shallow air leakage between the 159900.doc -274-201235565 and the piston may not be exhausted to the atmosphere when the check valve is open. Preferably, the actuator is for selectively feeding a pressurized fluid between the actuators of the container-type piston pressure management (4) inside the container-type piston, the valve comprising a valve body Pressurized fluid and the inside of the container type piston. P. Both open cylindrical center passages, a spring loaded check valve that is tightly received in the central passage, the elastomeric loading check closure blocks the central passage when closed and allows fluid flow when open 35 a magazine loading piston that is slidably fitted in the passage above the check valve, the spring loaded piston sliding from the closed position toward the check valve to the open position when the pressurized fluid is supplied The pressurized fluid is again closed upon removal, the piston engaging the surface of the central passage with sufficient clearance to allow unrestricted sliding, but not sufficiently tight enough to prevent pressurized fluid between the piston and the central passage surface Leaking, a handle carried by the piston and merging with the check valve to open the check valve and permit pressurized fluid to the check valve and to the interior of the container piston when the piston is moved to the open position a passage, an outer annular disc and an inner annular disc, the yoke being joined in the central passage to form a plug between the check valve and the piston. The shank extends through the plug, the piston generally axially The outer disc is spaced apart but is in contact with the outer disc in its open position, the outer disc having a series of apertures radially adjacent to the shank that lead to a series of recesses in the inner disc a port to create an exhaust path that is erected from the atmosphere into a space between the plug and the piston such that a pressurized fluid leaking through the piston will not shrink over the plug and piston as it moves Between the delays of its movement, and a circular compression seal 159900.doc -275-201235565, which surrounds the holes, the seal is compressed between the piston and the plug when the piston is connected to the plug so that the The pressurized fluid leakage of the piston cannot be vented to the atmosphere when the check valve is open. Preferably, the activation pin is for connecting to an inflation valve, the activation pin comprising: a housing connected to a pressure source, wherein a connection hole in the housing has a core axis and an inner diameter, the inner diameter substantially corresponding An outer squat of the inflation valve to be connected to the activation pin, and a cylinder and member for conducting a liquid medium between the cylinder and the pressure source, and wherein the activation pin is configured to engage the center of the inflation valve a spring-operated core pin configured to be located within the outer shunt continuation coupling bore and coaxial with a central axis of the coupling bore, and including a piston portion having a piston that will be positioned in the cylinder Moving between a piston position and a second piston position, the activation pin includes a passage for the piston. The first end and the second end are disposed, the piston is positioned at the first end and the passage has an opening at the first end, a valve portion movable in the passage at the first valve position and the second The position of the valve can be driven by a difference in force acting on the surface of the intermediate portion, wherein the first valve position opens the opening and the second valve position closes the opening, and the top of the piston portion forms for the valve member The seat of the sealing surface. Preferably, the valve actuator is for connecting to the activation pin of the inflation valve, the valve actuator comprising: a housing having a hole in the housing for coupling with the inflation valve, the coupling hole having a central axis and an outer opening, a positioning member for positioning the inflation valve when coupled in the coupling hole, and a starting pin configured to be coaxial with the coupling hole for pressing the center of the inflation valve A spring-loaded core pin, a cylinder having a pressure cylinder 159900.doc -276-201235565 > a cylinder wall connected to a pressure source, wherein the activation pin is positionable at a proximal pin position and a distal pin position Displacement relative to the positioning member such that when the inflation valve is positioned by the positioning member, the activation pin depresses the core pin of the inflation valve at its distal pin position and unwinds the inflated core pin at its proximal pin position, the activation pin Coupled to the piston and slidably disposed in the cylinder and movable between a proximal piston position corresponding to the proximal pin position and a distal piston position corresponding to the distal pin position, the piston being under pressure The coupling holes are disposed in the cylinder and are self-stressed The pressure supplied to the cylinder from the source is driven from its proximal piston position to its distal piston position and the flow regulating member is provided for selective interruption or passage between the pressure source and the coupling bore depending on the piston position The flow path is adapted such that the flow path is interrupted at the proximal piston position and the flow path is unobstructed at the distal piston position at least when the inflation valve is positioned by the positioning member. Preferably, the piston includes means for obtaining a predetermined pressure level. Preferably, the valve system releases the valve. Preferably, the spring force operated cover of the closed passage is above the valve actuator when the pressure reaches above a predetermined pressure value. Preferably, the passage is open or closed, the passage connects the chamber with a space between the valve actuator and the core pin, the piston is movable between an open position and a closed position of the passage, and the movement of the piston is utilized The result of the measurement of the pressure in the piston is controlled by the actuator being manipulated. Preferably, the passage is open or closed which connects the chamber to the space between the valve actuator and the core pin. Preferably, the piston is movable between an open position and a closed position of the passage. 159900.doc - 277 - 201235565 Preferably, the piston is operated by an operator controlled pedal that rotates from the non-acting t position about the shaft To the active position and vice versa. Preferably, the tongue plug is controlled by an actuator that is manipulated as a result of the measurement of the pressure t in the piston. Preferably, the combination further comprises means for defining the volume of the enclosed space such that the fluid_force in the enclosed space during the stroke is related to the pressure acting on the piston. Preferably, the foam or fluid is adapted to be during translation of the piston from a second longitudinal position of the chamber to a first longitudinal position of the chamber or from a first longitudinal position of the chamber to a second longitudinal position of the chamber The vessel provides a pressure above the highest pressure in the surrounding atmosphere. Preferably, the combination comprises a source of pressure. Preferably, the pressure source has a pressure rating that is higher than the pressure rating of the container. Preferably, the pressure source is in communication with the container through the outlet valve and the inlet valve. Preferably, the outlet valve is an inflation valve, preferably a valve having a spring biased core pin (such as a Schrader valve) that moves toward the pressure source as it is closed. Preferably, the inlet valve is an inflation valve, preferably a valve having a core pin biased by a spring (such as a Schrader valve) that moves toward the container when the valve is closed. Preferably, the passage is open or closed which connects the chamber to the space between the valve actuator and the core pin. Preferably, the passage is open or closed which connects the chamber to the space between the valve actuator and the core pin. 159900.doc 201235565 Preferably, the piston is moveable between an open position and a closed position of the passage. Preferably, the passage is opened or closed by the passage connecting the chamber and the space between the valve actuator and the core pin, the piston is movable between the open position and the closed position of the passage and the movement of the piston is borrowed Actuated by an actuator that is manipulated as a result of the measurement of the pressure level in the piston and the pressure source. Preferably, the 'channel through open or closed' passage connects the chamber to the space between the valve actuator and the core pin via the space, and the piston is movable between the open and closed positions of the open position of the passage' and the piston The movement is controlled by an actuator that is manipulated as a result of the speculation of the pressure level as the pressure and pressure source in the piston. Preferably, the wall of the container comprises an elastically deformable material and the elastically deformable material comprises a reinforcing member. Preferably, the reinforcing coil has a different braiding angle than 54.44. Preferably, the reinforcing member comprises a fabric reinforcement that allows expansion of the container when moved to the first longitudinal position and allows for contraction when moved to the second longitudinal position. Preferably, the piston is produced by a production system having a plurality of vulcanization cavities. Preferably, the reinforcing member comprises fibers that allow the swell to expand when moved to a larger first longitudinal position and allow for contraction when moved to the second longitudinal position. Preferably, the piston is produced by a production system having a plurality of vulcanization cavities, and wherein the fibers are mounted in the cavern of the cover by rotation of the fibers and cover at different speeds' while the fibers are pushed onto the interior of the cover. 159900.doc -279- 201235565 Preferably, the fiber is configured with respect to the lattice effect. Preferably, the reinforcing member comprises a flexible material reinforcing member positioned in the container comprising a plurality of rotatably secured to the common member. At least substantially elastically supporting the components, the common components being attached to the outer skin of the container. Preferably, the components and/or common components are inflatable. Preferably, the pressure system # on the wall of the crucible is formed by a device that operates with a yellow force. Preferably, the piston comprises a stiffener located outside of the container. Preferably, the container moves around the wedge wall in the cylinder. Preferably, the chamber is convex and the operating force is tangent to the set maximum force during the stroke. According to an embodiment of the invention, there is also provided a combination of a combination according to any of the preceding statements or a piston comprising a container having a bendable wall, or a combination comprising a piston of a container, the container having substantially The production size of the circumferential length of the first-longitudinal position of the chamber, the combined body having a reinforcing member that allows shrinkage of high frictional force H. The cross-section of different cross-sectional areas having different cross-sectional shapes '15 chambers in the cavity The first longitudinal position of the chamber is at least substantially continuous between the longitudinal positions of the whistle-peach, wherein the piston is further designed to adapt itself and the sealing member to accommodate different cross-sectional shapes. Preferably, the cross-sectional shape of the chamber at its II_Μ, the longitudinal position of the younger brother is at least substantially circular ' and wherein the cross-sectional shape of the chamber at its second longitudinal position is an elongated shape having a first size (such as an elliptical shape), the first dimension is at least 2 times (e.g., at least 3 times) the size of the first dimension force angle, and at least 4 times better than 159900.doc -280 - 201235565. Preferably, the cross-sectional shape of the chamber at its first longitudinal position is at least substantially circular ' and wherein the cross-sectional shape of the chamber at its second longitudinal position comprises two or more at least substantially elongated shapes ( For example, the projections are preferably 0. Preferably, the first circumferential length of the cross-sectional shape of the cylinder at its first longitudinal position is equal to 80% to 120% of the second circumferential length of the cross-sectional shape of the chamber at its second longitudinal position. (such as 85% to 115%), preferably • to uo% (such as 95% to 105%), preferably 98% to 102%. Preferably, the length of the first circumference and the length of the second circumference are at least substantially identical.

An embodiment of the present invention also provides a piston chamber assembly comprising an elongated chamber bounded by an inner chamber wall and including therein a piston that is sealably movable in the chamber t Relating the piston from at least its second longitudinal position to its first longitudinal position in the chamber, the chamber including at least a portion of the length of the chamber wall between the longitudinal position and the second longitudinal position Deformation (d), the chamber having a first cross-sectional area at its first longitudinal position when the piston is in the position, the first cross-sectional area being greater than the second cross-section at the second longitudinal position of the chamber when the piston is in the position An area, wherein the change in the cross-section of the chamber is at least substantially continuous between the first longitudinal position and the second longitudinal position as the piston moves between the first longitudinal position and the second longitudinal position, the piston including the changeable A geometrically flexible expandable container having a changeable geometry that is adapted to each other during the stroke of the piston to provide a continuous sealing capability, and the piston is located in the chamber 159900.doc -281-201235565 At the second longitudinal position while having its production size. Preferably, the piston is made of a material that is at least substantially incompressible. Preferably, the piston has a shape along the longitudinal axis in section A that tapers in a direction from a longitudinal position of the chamber to a second longitudinal position thereof (4). Preferably, the angle between the wall of the cylinder and the central axis is at least less than the angle between the wall of the wedge of the piston and the central axis of the chamber. Preferably, the chamber includes an outer support structure that encloses the inner wall and a fluid contained by a space defined by the outer support structure and the inner wall. Preferably, the space is defined by an outer structure and the inner wall is inflatable. Preferably, the piston comprises an elastically deformable container comprising a variable material and designed according to statements 7 to 17. According to an embodiment of the invention, there is provided a pump for pumping a fluid, the pump comprising a combination of any of the earlier mentioned statements for a member for oscillating a piston from a position outside the chamber' A fluid inlet connected to the chamber and including a valve member, and a fluid outlet connected to the chamber. Preferably, the sounding member has an outer position and an inner position at which the piston is at a first longitudinal position of the chamber, at which the piston is in a second longitudinal position of the chamber At the office. Preferably, the mouthpiece member has an outer position and an inner position at which the piston is at a second longitudinal position of the chamber, at which the piston is in a first longitudinal position of the chamber At the office. The shock absorber package is for providing a shock absorber according to an embodiment of the present invention, comprising: a combination according to any one of the preceding statements 1 to 80, 159900.doc-282. 201235565 cavity to the outside a member locating the piston, wherein the engagement member has an upright position - an internal position at which the piston is at the first longitudinal position of the chamber, at the internal position, the activity is at The second longitudinal position. Fluid of the valve member Preferably, the shock absorber comprises a connection to the chamber and an inlet. Preferably, the shock absorber further comprises a fluid inlet connected to the chamber and comprising a valve member.

Preferably, the cavity forms an at least substantially sealed cavity containing a fluid with the piston which is compressed as the piston moves from the first longitudinal position to the second longitudinal position of the chamber. Preferably, the shock absorber further includes means for biasing the piston toward the first longitudinal position of the chamber. According to an embodiment of the present invention, there is provided an actuator comprising: a member for engaging a piston from a position outside a chamber, according to a combination of any of the foregoing statements to a rib, A member for introducing fluid into the chamber to displace the piston between a first longitudinal position and a second longitudinal position of the chamber. Preferably, the actuator further includes a fluid inlet connected to the chamber and including a reading member. Preferably, the actuator further includes a fluid outlet connected to the chamber and including a valve member. Preferably, the actuator further includes means for biasing the piston toward the first longitudinal position or the second longitudinal position of the chamber. 159900.doc -283- 201235565 Preferably the 'introducing member' comprises means for introducing the m-fluid into the chamber. Preferably, the 'introducing member is adapted to introduce a combustible fluid such as gasoline or diesel into the cavity to the middle' and wherein the actuator further comprises means for combusting the combustible fluid. Preferably, the introduction member is adapted to introduce the expandable fluid into the chamber, and wherein the -theo actuator further comprises a member for expanding the expandable fluid. Preferably, the actuator further includes a crank adapted to translate the translation of the piston into a rotation of the crank. Preferably, the motor includes a combination according to any of the above statements. Preferably, the power unit comprises a combination, a power source and a power device according to any of the above statements. Preferably, the power unit is movable. 5 07 DESCRIPTION OF THE PREFERRED EMBODIMENT Figure 301 shows a valve actuator to be coupled to a clip-on valve connector of, for example, a Schrader valve. The piston 477 is extremely close to 2 at the first end of the cylinder 47. The connector has a housing 500 and the sealing member includes an annular portion 475. The fastening member includes temporary threads 476. The housing also has a central axis 479 and a coupling portion 510. Figure 301A shows an enlarged detail of Figure 301. The steam 470 has a cylinder wall portion 511 '. The wall portion 511 has a diameter that fits the piston ring 5〇8 of the piston 477. Near its first end 492, the cylinder wall includes an enlarged wall having an enlarged diameter 159900.doc • 284·201235565 portions 475a, 475b, 476a, the cylinder being contained in the piston members 477, 508 when the activation pin has sufficiently opened the core of the valve Surrounding flow channel portions 471, 472, 473. It is now possible to establish a flow from the pressure source to the valve. The first end 492 of the cylinder 470 acts here as a stop for actuating the movement of the pin. Channel portions 473 and 474 are part of piston control member 476c. Such portions may have a number of shapes depending on the selected production technique: for example, as a sector portion of a circle and (507) channel portions 473, 474 as cylinders are formed by injection molding, or channel portions (507) It can also be drilled. Channel portions 473, 474 can be considered "flow shaping" and are constructed to reduce aerodynamic drag. The angled enlarged wall portion 475a is at an angle to the central axis 479 that is greater than 0° and less than 20°, typically in the range of 1° << 12° relative to the direction of the gas and/or liquid medium from the pressure source, respectively. in. Piston control member 476c has three recesses having walls 476a and 476b, respectively. Wall 476a has an angle greater than 0° and less than 20° (typically in the interval between 6° and 12°) relative to the direction of the gas and/or liquid medium from the pressure source. An alternative to the channel portions 473 and 474 described above is the channel (507), wherein the piston control has no grooves. In this alternative, the hole (507), which is parallel to the central axis 479 and adjacent to the piston control, connects the channel portion 475b (shown as a three-hole with a dotted line) and engages the hole. Figure 301B shows a portion G-G from channel 473A having channel portions 473 and 474 and a stop 492. The alternate channel portion (507) is sketched by dotted lines. Figure 302 shows a valve actuator in a universal clip-on valve connector having a housing 504 and having a sealing member, the sealing member being included coaxially with the central axis 486 of the coupling portion in the direction of the central axis 486 of the coupling portion 503 Position the first annular portion 482 and the second annular sealing portion 483 of 159900.doc • 285 - 201235565. The first annular seal portion 482 is closer to the opening 502 of the coupling portion than the second annular seal portion 483, and the diameter of the first annular seal portion 482 is larger than the diameter of the second annular seal portion 483. The coupling valve can be secured by at least one "clip" (=, ie, temporary thread) 476. However, two clips 493 opposite each other are preferred. A wedge-shaped conical shape 5 接近 1 close to the sealing surface 482 helps center the valve. The wedge-shaped conical shape is at an angle to the central axis 486, and typically this angle > 45. . A sealed individual cylinder sleeve 496 having a cylinder wall portion 5〇9 is shown. It is fastened to the wall of the outer casing 504 by, for example, a spring clasp 497. This is an economical way of making the negative slip angle of the inclined enlarged wall portion 512 possible. The pi cylinder sleeve 496 has an angle away from the piston stop 495 such that the piston ring 508 is not sealed there. Figure 3 02 shows channel portions 480 and 481, respectively defined by enlarged wall portions 487 and 488 of the piston control member, respectively. The start pin is streamlined by the piston 484 and the piston cup 485. The wall portion 487 is at an angle to the central axis 486 seen in the direction of the medium from the pressure source, which angle is greater than 〇. And less than 20. (usually in the interval between 6. and 12.). The stepped surface 498 of the wall of the outer casing 504 forms a hermetic connection from the wall of the cylinder casing 496 to the cylinder 499. It is of course also possible to form a gas-tight connection on the other side of the cylinder. An inclined enlarged wall portion 512 is shown at the bottom of the cylinder sleeve 496, and the inclined enlarged wall portion 512 forms a passage portion 471 together with the piston ring 515. Figure 302A shows a portion of Figure 302 and a stop 495 for actuating the movement of the pin. Wall portion 488 and channel portion 481 are also shown. Figure 303 shows the start pin as compared to the start pin of Figure 3 。 1. Also show live 159900.doc -286- 201235565 Plug 529 ^Piston rod 531 does not need to control the seal against the piston. The cylinder 536 of the valve actuator is within the outer casing 532 of the valve connector. A coupling portion 53A is also shown. Figure 303A shows a channel portion 533 having an expansion 535 and a channel portion 534 formed as a radial bore 534. Piston ring 539 opens and closes the conductive passage at its aperture 537 depending on the position of the actuating pin. The direction of the channel portion 534 with respect to the central axis is comparable to the angle of the channel portion 471 of Figure 301A. The wall of the expansion 535 has an angle that is comparable to the angle of the wall 476a of Figure 1A. The steam rainbow wall portion 5 3 8 of the cylinder 5 3 6 is also shown. Figure 304 shows the start pin and its cylinders, which are shown in Figure 3.1. This is placed in the assembled official line housing member 520, 521 or the like, in which a valve 522 (e.g., 'Schladder valve) having a spring loaded core pin 523 is located. The start pin engages with the valve pin 523. Figure 305 shows a valve actuator in a universal valve connector. It is comparable to the valve actuator of Figure 3〇1. However, the two sealing members 540, 541 having an intermediate distance A can seal two valves having different sizes. Two enlarged portions of the diameter of the cylinder 542 in the cylinder wall 55A are shown with an intermediate distance b. A start pin 543 is also shown, with two shouting layers at a distance b. The intermediate distances may be equal or different, for example, when the valves are of different types, such that the distance from the core pin to the seal is different. The tie between the two enlarged portions 丨 and 2 has a cylindrical wall portion 544 that engages the cylinder portion 545 of the piston ring 508. A center axis 546, a coupling portion 547, and an opening 548 from the outer casing 549 are also shown. 507 Particularly Preferred Embodiments In accordance with an embodiment of the present invention, a valve actuator for operation of a valve having a spring loaded solenoid pin is provided, the valve actuator comprising: an outer 159900.doc • 287- 201235565 The shell 'connects to a source of pressure medium within which a coupling portion is used to receive a valve to be actuated, a cylinder surrounded by a cylinder wall of predetermined cylinder wall diameter and having a first cylinder end and compared to a second cylinder end of the first cylinder end that is further from the coupling portion, a piston movably located in the cylinder and fixedly coupled to the activation pin for engaging the valve housed in the coupling portion a spring-operated spool pin and a conductive passage for conducting pressure tantalum from the steam to the consumption of the p-knife at the first piston position and the piston from the first cylinder end when the piston is moved to the first-piston position For a first predetermined distance, the conduction of the force medium between the steam rainbow and the face joint portion is inhibited when the piston is moved to the second piston position, and the piston is at a second predetermined distance from the end of the first cylinder at the second piston position, The first The predetermined distance is greater than the first distance, wherein: the conductive passage is disposed in the cylinder wall and opens to the cylinder at a portion of the steam red wall having a predetermined cylinder, the piston includes a piston ring having a sealing edge, the sealing edge and the cylinder The wall portion is sealingly engaged such that the second position of the piston inhibits the pressure medium from being conducted into the passage and opening the passage at the first position of the piston. Preferably, the first predetermined distance is greater than zero. Preferably, the first predetermined distance is about zero. Preferably, it & _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ Preferably, it is contained in a conical portion of the steam, when the wedge portion and the piston portion at the "2" coincide with the deformed portion. In the plug position, the conical shape of the piston preferably, the conduction passage i is made of a vapor red wall An enlarged portion of the diameter is formed, the enlarged portion of the I59900.doc 201235565 configured to radially surround the piston when in the first piston position of the piston such that the pressure medium can surround the edge of the piston ring when the piston is in its first piston position Preferably, the enlarged portion of the cylinder diameter is formed at one or several portions of the circumference of the cylinder wall. Preferably, the wall of the enlarged portion includes a cylindrical enlarged wall portion and an inclined enlarged wall portion 'inclined enlarged wall portion Forming an angle greater than 0 with the central axis and less than 20' wherein the inclined enlarged wall portion is located between the cylindrical enlarged wall portion and the cylinder wall portion having a predetermined cylinder wall diameter. Preferably, the cylindrical enlarged wall portion is coupled The channel portion of the conductive channel between the portions is designed to be shaped as a wedge-shaped channel portion of the groove or designed to be flat with the central axis of the cylinder Preferably, the coupling portion is coupled to the aperture in the cylinder wall portion by a conductive passage positioned at a distance from the first cylinder end such that when the piston is in the first piston position The aperture is located between the piston and the second end of the cylinder. Preferably, the piston is further movable within the vapor red to a third predetermined distance from the first end of the cylinder and a third predetermined distance from the first predetermined distance And the third position in the fourth position is greater than the second predetermined distance and the fourth predetermined distance is greater than the third predetermined distance; and the cylinder includes the second passage 'the second passage poem allowing gas when the piston is in the three-position position And / or the liquid medium between the cylinder and the consumable part when the piston is in the fourth position (four) air limb / or (four) medium in the material connection part 159900.doc • 289-201235565 preferably 'S Hai implementation For example, a sealing member for sealing a valve actuator to a valve of a different type and/or size is included in the facing portion. The sealing member includes a coaxially positioned and displaced portion of the central portion of the lightly coupled portion. Among ^ The first annular sealing portion in the direction of the axis and the first annular portion of the second annular knives are closer to the opening σ of the coupling portion than the second annular portion. The diameter of the first annular portion is greater than the first Preferably, the embodiment includes a fastening thread for fastening the valve actuator to the inflation valve within the coupling portion. Preferably, the fastening thread temporarily tightens the thread Preferably, the cylinder wall formed by the cylinder sleeve is fastened and sealed in the outer casing and formed by the inclined enlarged wall portion, the cylinder sleeve has an angle away from the first cylinder end-wall portion such that the piston ring is not in the Preferably, the 'eight cylinder liners are secured and sealed by spring clips in the wall of the outer casing. Preferably, the embodiment is provided in the face joint portion for sealing the valve actuator to have a spring A sealing member on the valve of the spool pin that is operated by force. According to an embodiment of the present invention, there is also provided a valve connector coupled to a hand pump for inflating a carrier tire, a base pump, an automobile pump, a pressure tank or a compressor, which includes any one of the technical solutions 116 Valve actuator. Embodiments according to the present invention also mentions (d) a pressure groove or hand pump for inflating a plant tire, wherein: an integrated valve actuator. According to an embodiment of the invention, a valve actuator is also provided in a static configuration, such as a chemical plant. 15990〇.cj〇c -290. 201235565 19597 Description of the Preferred Embodiment FIG. 401A shows a line XX between two of the three mating surfaces of the base 4 having a rigid surface 5, the combined body 6 Move around the line XX. The wire 丫 Y between the two of the three engaging surfaces of the pedestal 4 of the rigid surface 5, the combined body 6 is movable around the line γ·γ. A line Z-Z' combining body 6 between two of the three contact points of the pedestal 4 having a rigid surface 5 is movable around the line Z-Z. Figure 401B shows the combination 6' which comprises a chamber 7, a guide 8 for the piston rod 9, and a handle 10. The base 4 has contact points 1, 2 and 3 which are rounded toward the rigid surface. The chamber 7 is rigidly connected to the base 4 by a stiffener 11. Figure 402A shows the handle 10 of the combination 6 when the combination 6 is in its rest position 12. Figure 402B shows the combination 6 in its rest position 12 when the transition section 13 between the combination body 6 and the reinforcement 14 of the base 40 is in its rest position. The transition section 13 can be made of a flexible material and is located around the chamber 7. Figure 402C shows the activation position 14 of the handle 10 when the handle 1 has moved from its rest position 12 before the rest position. Figure 402D shows the activation position 15 of the handle 1 when the handle has moved from its rest position 12 after the rest position. Figure 402E shows the activation position of the handle 10 when the handle has moved from its rest position 12 to the left front side of the rest position 16» Figure 402F shows the handle 10 when the handle has moved from its rest position 12 to the left rear side of the rest position The starting position is 17. Figure 402G shows the activation position 18 of the handle 10 when the handle has been moved from its rest position 159900.doc • 291·201235565 to the right front side of the rest position. Figure 402H shows the activation position 19 of the handle 1 when the handle has moved from its rest position 12 to the right rear side of the rest position. Figure 403A shows the foot pump in the case where the transition between the chamber 7 and the base 4 is an elastically deformable bushing 20. Figure 403B shows an enlarged view of the transition between chamber 7 and base 40. The chamber 7 has a projection 21 which follows the recess 22 in the bushing 20 so that the chamber 7 can be simply mounted in the base 40. The projection 41 is on the top of the reinforcement 42 of the base 40. Figure 403C shows the foot pump in the case where the transition between the chamber 7 and the base 4 is an elastically deformable bushing 23. Figure 403D shows an enlarged view of the transition between chamber 7 and base 40. The chamber 7 has a recess 25' recess 25 in accordance with the projection 24 in the bushing 23, so that the chamber 7 can be simply mounted in the base 40. Figure 404A shows a combination 6 in the form of a foot pump with a cover 25 that allows lateral displacement and/or deflection of the piston rod relative to the remainder of the combination 6 and the base 43. The base 43 can be indirectly coupled to the base 41 by a stiffener 42 either directly or, for example, by a flexible bushing. Figure 404B shows an enlarged view of the cover 25 of Figure 404A when the piston 44 is furthest from the base 43 at the end of the stroke. The piston rod 9 moves in the guide member %, and the convex contact inner surface 31 of the guide member 26 is lined with the piston rod 9 at its center line 27. The guide member 26 is received in the cover 9 by the surfaces 36 and 37 and by the flexible beak ring 28. The cross-sectional area of the space 29 between the surfaces 36 and 37 of the cover 9 is shown to be larger than the cross-sectional area of the ring 28 itself, so that compression of the substantial 159900.doc 292·201235565 of the ring 28 is possible (see, for example, Figure 4〇4C). ). The distance a is between the outside of the piston rod 9 and the wall 38 of the spaces 33 and 34 of the cover 9. This distance & can be substantially the same as the distance b between the piston rod and the wall 38 of the cover 9 at the top of the cover. Figure 404C shows the deflection angle a of Figure 4B' in which the central axis 32 of the piston rod 9, with respect to the central axis 30 of the remainder of the joint. The space 29' is always filled by the compression ring 28' which compresses the "space 34" by the translational guiding member 26. Space 33,. The contact surface 35 is between the guiding member 26 and the piston rod 9. The distance a' is smaller than the distance a of the map 404B. The distance b' is smaller than the distance b of Figure 404B and greater than the difference between the distances a and a. Figure 404D shows an enlarged view of the cover 25 of Figure 404A when the piston 44 is closest to the base 43 at the end of the stroke. The center line of the combined body is 3〇. Spaces 33 and 34 are between the inner wall 38 of the cover 25 and the piston rod 9. Figure 404E shows Figure 4〇4D when the piston rod 9, translated to the left to a distance between the exterior of the piston rod 9, and the inner wall 38 of the cover 25 is a. The guiding member 26" moves to the left so that the compression ring 28_display space 29h has been filled in this section by the compression ring 28". The space 33" is substantially equal to the space 34" having a distance a" 'distance a, equal to the distance bM, the distance b•• is less than the distance & 405A shows the left side 51 of the handle 52 with respect to the central axis 54 of the combined body 55. And the right portion 53 of the handle 52. When viewed from the position X of the user, the angle a between the central axis 56 of the left portion 51 of the handle 52 and the central axis 57 of the right portion 53 of the handle 52 is less than 18 inches. The center point 61 of the left portion 51 and the center point 62 of the right portion 53. Fig. 405A shows a front view of the foot pump 159900.doc • 293 - 201235565 including the handle 52 and the combination body 55. The handle 52 has a left portion 51 And right 53" central axis 54 of the combined body 55. Figure 406A shows the left portion 58 of the handle 59 and the right portion 60 of the handle 59 with respect to the central axis 54 of the combined body 55. When viewed from the position X of the user, The angle β between the central axis 56 of the left portion 58 of the handle 59 and the central axis 61 of the right portion 60 of the handle 59 is greater than 18 〇〇. Figure 406B shows the foot pump of Figure 4〇6a including the handle 59 and the combination 55. Front view. Handle 59 has left 58 part (around Part 53 is rotated) and right portion 60 (= is rotated about left portion 5 1). 1 9597_2 Particularly preferred embodiment In accordance with an embodiment of the present invention, a piston chamber assembly is provided that includes delimiting by an inner chamber wall An elongated chamber, and including a piston member in the chamber, the piston member being sealingly movable relative to the chamber wall at least between a first longitudinal position of the chamber and a second longitudinal direction, the combination The body is fused to a rigid surface, wherein the combination includes a piston rod that is erected through a cover that covers the chamber, wherein the piston rod is guided by a guiding member movably coupled to the cover. Preferably, the f-guide member is a piston rod Week® has a mat for the go fitting. The loop is received between the two surfaces of the lid. The flexible loop is received in the space between the surface and the guiding member, wherein the cross-sectional area of the space is larger than Ο The cross-sectional area of the shaped ring. Preferably the guiding member comprises a convex guiding surface for guiding the piston rod. Preferably, the piston is rounded at the junction with the wall of the chamber. Preferably, the piston rod The connection to the piston (44) is recyclable 159900.doc • 294· 201235565 Preferably, the piston chamber coupling system—the bearing includes a member for engaging the piston from a position outside the chamber, the fluid outlet of the valve member and the fluid inlet are connected to the chamber. Jiadi 'piston chamber combination system-shock absorber, which comprises a member for spraying the piston from the cavity to the outside, wherein the kneading member has a position and an internal position, and the name visits the ice v 罝 at the external position of the piston a first-longitudinal position of the chamber in which the piston is in a second longitudinal position, wherein a sealed air chamber containing fluid is formed with the piston, and the piston is sealed from the first longitudinal position to the second longitudinal position The cavity is compressed. A 'piston chamber combination system-actuator that includes a member for the salivation of a taxi from the cavity to the exterior' and is used to introduce fluid into the chamber so that the piston is in the first Preferably, the longitudinal position 盥_, the member 0 displaced between the longitudinal positions, the chamber has a cross-sectional area of different cross-sectional areas and different circumferential lengths at a longitudinal position of the first and the second Han, and a cross section of the intermediate longitudinal position between the longitudinal position of the music and the second longitudinal standing, a cross-sectional area of the negative and a length of the circumference of the circle, the cross-sectional area and the circumference of the second longitudinal position The length is less than the cross-sectional area and the circumferential length at the first longitudinal position, wherein the piston member can be sized, thereby providing different cross-sectional areas and circumferential lengths of the piston member to adjust the piston member to accommodate the piston member in the first = different cross-sectional areas and different circumferential lengths of the chamber during relative movement between the position and the second longitudinal position through the intermediate longitudinal positions of the chamber. Preferably, the chamber has different cross-sections at the first and second longitudinal positions 159900.doc 201235565 and a section of equal circumferential length, and has an intermediate longitudinal position between the first longitudinal position and the second longitudinal position a cross section having at least substantially different cross-sectional areas and circumferential lengths, the cross-sectional area and circumferential length at the second longitudinal position being less than the cross-sectional area at the longitudinal position of the first one and the circumferential length 'where the piston can be resized' thereby providing a piston Different cross-sectional areas and circumferential lengths' thereby adapting the piston to accommodate the difference in chambers during relative movement of the piston member between the first longitudinal position and the second longitudinal position through the intermediate longitudinal positions of the chamber Cross-sectional area and equal circumferential length. BRIEF DESCRIPTION OF THE DRAWINGS A brief description of the present invention will be described hereinafter with reference to the drawings in which: FIG. 1A shows a longitudinal section of a chamber having fixed different cross-sectional areas and comprises a fabric. A first embodiment of a stiffener piston having a dimension that changes axially in the radial direction during the stroke, exhibiting a piston configuration that is compressed at the beginning and end of the stroke, wherein without pressure The piston has its production size. Figure 1B shows an enlarged view of the piston of Figure 1A at the beginning of the stroke. Figure 1C shows an enlarged view of the piston of Figure 8 at the end of the stroke. 2A shows a second embodiment of a longitudinal section of a chamber having fixed different cross-sectional areas and a piston comprising a fiber reinforcement ("grid effect"), wherein the size of the elastic material of the wall is during the stroke. Upwardly changing axially 'shows a piston configuration that is pressurized at the beginning and end of the stroke, where the piston has its production size without pressure. 159900.doc -296· 201235565 Figure 2B shows an enlarged view of the piston of Figure 2a at the beginning of the stroke. Figure 2C shows an enlarged view of the piston of Figure 2A at the end of the stroke. Figure 3A shows a longitudinal section of a chamber having fixed different cross-sectional areas and a third embodiment of a piston comprising a fiber reinforcement (without "grid effect"). The fiber reinforcement has a radial direction during the stroke The dimension changed in the axial direction 'shows the piston configuration at the beginning and end of the stroke, where the piston has its production size. Figure 3A shows an enlarged view of the piston of Figure 3 at the beginning of the stroke. #图3C shows an enlarged view of the piston of Figure 3 at the end of the stroke. Figure 3D shows a top view of the piston of Figure 38 with a stiffener in the wall, with the stiffener in a plane passing through the central axis of the piston, the left side: at the first longitudinal position, and the right side: at the second longitudinal position. Figure 3A shows a top view of the piston of Figure 3 with a stiffener in the outer skin, wherein the stiffener is located partially through the central axis and partially at the central axis

Longitudinal position.

There is no pressure difference between them. Figure 5A shows the piston of Figure 4, the chamber interior does not move instantaneously, moving toward the non-movable cover. The piston has a wall having a conical shape, wherein the piston begins to expand,

Figure 5 shows the --π -...一-expansion, which increases at the second longitudinal position of 159900.doc -297- 201235565, and the movable cover does not move. Figure 5C shows the piston of Figure 5B that does not move momentarily and thereby expands such that the contact area of the piston wall with the wall of the chamber decreases at the second longitudinal position of the contact area while the piston wall and cavity The contact area of the wall of the chamber increases at a first longitudinal position of the contact area and the movable cover does not move. Figure 5D shows the piston of Figure 5C in which the non-movable cover is momentarily beginning to move from the second longitudinal position to the first longitudinal position whereby the piston is moved in the same direction. Figure 5E shows the piston of Figure 5D in which the movement of the piston is reduced due to the increased contact area. Figure 6A shows an expandable piston that moves in a closed conical shaped chamber. Figure 6B shows an expandable piston moving in a closed conical shaped chamber wherein the chamber is in communication with the surrounding atmosphere on both sides of the piston. Figure 6C shows an expandable piston moving in a closed conical shaped chamber' wherein the chambers are in communication with each other on both sides of the piston via a closed passage outside the chamber. Figure 6D shows an expandable piston moving in a closed conical shaped chamber' wherein the chambers are in communication with each other on both sides of the piston via a closed passageway inside the piston. Figure 6E shows an expandable piston that moves in a closed conical shaped chamber. The chamber communicates with one another on either side of the piston via a passage between the chamber wall and the piston wall. Figure 7D shows a 3-dimensional representation of the reinforcing matrix of the elastic fabric 159900.doc-298-201235565 material in the wall of the container as it will expand. Figure 7E shows a pattern of the figure when the wall of the container has expanded. Figure 7F shows a 3-dimensional representation of the reinforcement pattern of the inelastic textile material in the wall of the container as the piston will expand. Figure 7G shows the reinforcement matrix of Figure 7F when the piston has expanded. Figure 8 shows the combination of a piston that does not move in the chamber and allows a wedge wall. Figure 9A shows a longitudinal section of a chamber having fixed different cross-sectional areas and a fourth embodiment of a piston comprising an "octopus" device that limits the extension of the container wall by means of a touch, which can be Inflatable, showing the piston configuration at the beginning and end of the stroke, where the piston has its production size. Figure 9B shows an enlarged view of the piston of Figure 9A at the beginning of the stroke. Figure 9C shows an enlarged view of the piston of Figure 9A at the end of the stroke. Figure 9D shows the piston of Figure 9A, which just encloses the conical portion of the chamber. Figure 10A shows the piston chamber assembly 'where the pressurized dome-shaped piston is moved from the second longitudinal position to the first longitudinal position, the internal volume of the piston is enlarged, and the enclosed space has a fixed volume, thereby reducing the The internal pressure of the piston 'the piston can change its shape into a sphere, the dashed line at the ends shows the outer contour of the piston 'where the chamber has a wall parallel to the central axis of the chamber' in the middle, the size of the piston In comparison with the same size of the piston appearing in Figures 1B, it is shown that the piston in Figure i 〇B can be flexibly connected to the wall of the chamber, while in Figure 10A, the connection is sealed. connection. Figure 10B shows the piston chamber assembly of Figure 10A, wherein the internal pressure of the piston 159900.doc - 299 - 201235565 pressure has been additionally reduced by the following operation: at the farthest first longitudinal position or at the piston returning to the second The volume of the enclosed space is changed during the longitudinal position, thereby changing the size of the piston, continuously accommodating the piston to accommodate the size of the chamber to avoid jamming. Figure 10C shows the piston chamber assembly of Figures 10A, 10B, but wherein the internal pressure of the piston has been reduced by the following operation: at the farthest first longitudinal position or during the return of the piston to the second longitudinal position The fluid is removed from the enclosed space, thereby changing the size of the piston, continuously sizing the piston to accommodate the size of the chamber to avoid jamming. Figure 10D shows the process of Figure 10A when the piston is of a spherical shape as produced at the second longitudinal position. Figure 10E shows the process of Figure 10B when the piston is of a spherical shape as produced at the second longitudinal position. Figure 10F shows the process of Figure 10C when the piston is of a spherical shape as produced at the second longitudinal position. Figure 10G schematically shows the motor of the configuration of Figures 12A and 12C having a propulsion system that includes an inflatable inflatable actuator piston that rotates in a circular chamber, the circle The shaped chamber has a central axis about the center of the central shaft of the motor. Figure 10H schematically shows the motor of Figures 13A, 13B having a propulsion system that includes, for example, five non-movable inflatable inflatable actuators in a rotating circular chamber a piston having a centerline concentric with a center of rotation, the chamber including four sub-chambers that are continuous with each other, the chamber having successively different transition cross-sectional areas and circumferences, 159900.doc -300 - 201235565 the chamber Rotating around a spindle rod that passes through the center of the shaft. Consumption Technique FIG. 11A schematically shows a motor having a propulsion system including an inflatable inflatable actuator piston and a two-stage piston pumping system in an elongated chamber. The chamber has a continuously different cross-sectional area and circumference, all mounted on a crankshaft shaft, and a pressure reservoir 'and an electric starter motor, the smallest pump and starter motor being energized, inter alia, by solar energy. Figure 11B schematically shows the control member and pressure management for the motor of Figure 11A. Figure 11C shows a mechanical assembly made by some of the motors of Figures 11A and 11B in which the master cylinder does not move. Figure 11D shows the pressure management of the inflatable actuator piston at the junction of the crankshaft and the connecting rod shown in Figure 11C. Figure 11E shows details of the joint between the piston rod and the connecting rod shown in Figure lie. Figure 11F shows the suspension of the crankshaft shown in Figures ha and iiB and the details of the passage inside the crankshaft. Enclosed Space Volume Technology Figure 11G shows an alternative to managing the pressure change in the pneumatic actuator piston by the following operation: by changing the volume of the enclosed space via the piston of the second piston chamber combination, And an additional adjustment of the pressure via the piston of the third piston chamber combination for managing the speed/power of the motor' without constant repressurization of the pressure reservoir (for pairing 159900.doc - 301 · 201235565 The actuator is pressurized to achieve this change in the volume of the enclosed space). Figure 11A shows the configuration of Figure 11G in which constant repressurization of the pressure reservoir is performed by, for example, a cascade pump as shown in Figure 11A. Figure 111 shows a cylinder motor based on the portion of the concept shown in Figure 11H where the rate controller and ESVT pump are powered by a battery powered dual actuator; for repressurizing the pressure reservoir The pump is powered by a separate electric motor powered by a battery, clearly showing the respective power lines, the auxiliary power source being at least according to Figures 15A, 15B, 15C, 15E, 15F, etc. One can charge the batteries. Figure 11J shows a two-cylinder motor that is not based on the portion of the drawing in which each actuator piston chamber assembly has a separate rate controller and an ESVT pump that are in communication with each other. The left side of Figure 11J shows a scaled up view of the left portion of Figure 1U. Figure 11J shows the scaled up graph of the right side of Figure 1 on the right side of Figure 1. Figure 11K shows a cylinder motor based on the concept of the concept shown in Figure 11H, in which the actuator piston 7 pump is now powered by the crankshaft (the last mentioned case is by the battery) The power supply _ 达来供动力), the rate controller (two-way actuator) is controlled according to the rate in the figure 对 _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ Power; Auxiliary Power (4) According to ® 15B, Figure 15C, Figure 15E, Figure m, one of these powers can charge the batteries. Figure UL shows a two-steam rainbow motor based on the portion of Figure 11IC

159900. Doc 201235565 The arbor is used for the ESVT pump and the crankshaft is used for each actuator piston gentleman. The rate controllers (each actuator piston-rate controller) are in communication with one another; the pump for repressurizing the pressure reservoir is powered by a separate electric motor powered by a battery; the auxiliary power source is According to FIGS. 5A, 15B, 15C, 15E, and 15F, at least one of the power sources can charge the batteries. The left side of Fig. 11L shows a scaled up view of the left portion of Fig. 11L. The right side of Fig. 11L shows a scaled up view of the right portion of Fig. 11L. Figure 11M shows a cylinder motor based on the portion of the concept shown in Figure 11H. The ESVT for the actuator piston chamber assembly is now powered by a camshaft that is The 'rate controller' is a two-way actuator that communicates with the governor by an electric motor powered by a battery. The pump for repressurizing the pressure reservoir is powered by a separate electric motor powered by a battery; the auxiliary power source is according to Figures 5A, 15B, 15C, 15E, 15F, At least one of the equal power sources can charge the batteries. Figure 11N shows a two cylinder motor based on the portion of Figure nM, with a camshaft for the ESVT pump and a camshaft for each actuator piston chamber junction. The rate controllers (each actuator piston-rate controller) are in communication with one another; the pump for repressurizing the pressure reservoir is powered by a separate electric motor powered by a battery; the auxiliary power source is According to Figures 15A, 15B, 15C, 15E, 15F, at least one of the power sources can charge the batteries. The left side of the figure shows a scaled up view of the left part of Fig. 11N. 159900. Doc -303 · 201235565 Fig. 1 The right side of Figure 1 shows the scaled up graph of the right part of Figure 1. Figure 11A shows a cylinder motor based on the portion of the concept shown in Figure 11K, wherein the ESVT pump of the actuator piston chamber is powered by a crankshaft that is directly from the gas ( For example, air) is used to cool the combustion motor (using h2 obtained by electrolysis of H2, which is powered by a battery) to drive; the pressure storage tank is additionally used by the combustion motor. The speed controller is powered by a two-way actuator powered by a battery; the battery according to Figure 15D is charged by an alternator mounted on the main motor shaft. The heat generated by the combustion motor can be used, for example, to heat the interior of the vehicle. Figure Lip shows a two-cylinder motor based on the portion of Figure ii, wherein the ESVT pumps (each actuator piston chamber combination is a different pump) are powered by a crankshaft that is powered Directly driven by an auxiliary power from a forced liquid-cooled combustion motor (using H2 obtained by electrolysis of KhO, which is powered by a battery); the pump that repressurizes the pressure reservoir is directly driven by the combustion motor To drive; the rate controllers (per-actuator piston chamber combined with a rate controller) are powered by a two-way actuator 'the rate controllers are connected to each other' and by the battery Power is supplied, and the battery according to Fig. 15D is charged by an alternator mounted on the main motor shaft. The heat generated by the combustion motor can be used, for example, to heat the interior of the vehicle. The left side of Fig. 11P shows a proportional increase of the left part of Fig. 11P. Fig. 1 shows the right side of the IP. Figure 11Q shows based on the portion of the concept shown in Figure 11K - I59900. Doc • 304- 201235565 / Flying Cylinder Motor's EsvT pump in which the actuator piston chamber combination is powered by a camshaft that directly cools the combustion motor from a forced gas (eg, air) (using Hr obtained by electrolysis of HA, the electrolysis system is powered by a battery) is driven by auxiliary power; the pump for repressurizing the pressure reservoir is directly driven by the combustion motor; the rate controller is A battery powered dual actuator is used to power; the battery according to Figure 15D is charged by an alternator mounted on the main motor shaft. The heat generated by the combustion motor can be used, for example, to heat the interior of the carrier. Figure 11R shows a two-cylinder motor based on the portion of Figure 11Q, wherein the ESVT pumps (each actuator piston chamber assembly-esvt pump) are powered by a camshaft that directly borrows Driven by a forced power from a gas (eg, air) to cool the combustion motor (using H2 obtained by electrolysis of H20, which is powered by a battery); the pump that repressurizes the pressure reservoir is directly used The combustion motor is driven; the rate controllers (each actuator piston chamber combined with a rate controller) are powered by a two-way actuator that communicates with each other by The battery is powered; the battery according to Figure 15D is charged by an alternator mounted on the main motor shaft. The heat generated by the combustion motor can be used, for example, to heat the interior of the carrier. μ The left side of Fig. 11R shows a scaled up graph of the left portion of Fig. 11R. The right side of Fig. 11R shows a scaled up view of the right portion of Fig. 11R. Figure us shows the details of the joint of the base of the piston chamber assembly ι66 with the spindle of the motor. 159900. Doc • 305-201235565 Figure 11T shows details of the joint of the connecting rod of the actuator piston according to Figures ill to 11R with the crankshaft on the main shaft of the motor. Figure 11U shows details of the joint of the base of the piston chamber assembly 1〇6〇 of Fig. hr to Fig. hr with the spindle shaft of the motor. Figure 11V shows the mechanism for driving the pump of Figure ι to Figure 11R and its base. Fig. 11W shows the connection joint between the two crankshafts of the motor according to Fig. iij, Fig. 2, Fig. 11N, Fig. 11 and Fig. 11R. Consumption Technique Figure 12A schematically illustrates a motor having a propulsion system including an inflatable inflatable actuator piston that rotates in a circular chamber, and a chamber within an elongated chamber Two-stage piston pumping system 'The elongated chamber has successively different cross-sectional areas and circumferences, all mounted on a crankshaft shaft, and a pressure reservoir, and an electric starter motor, minimum pump and start The motor is energized, inter alia, by solar energy, including the control member. Figure 12B schematically shows the motor of Figure 12A having a propulsion system including an inflatable inflatable body that moves within a non-moving chamber The non-moving chamber has a centerline concentric with the center of rotation. The non-moving chamber includes four sub-chambers that are continuous with one another, the non-moving chamber having successively different transition cross-sectional areas and circumferences. Figure 12C schematically illustrates the control member and pressure management for the motor of Figure 12B, wherein the change in pressure in the actuator piston is controlled by adding fluid to the actuator piston and removing fluid from the actuator piston. . Enclosed space volume technology 159900. Doc 306 - 201235565 Figure 12D schematically shows the control member and pressure management for the motor of Figure 12B, wherein the change in pressure in the actuator piston is achieved by varying the volume of the enclosed space of the actuator piston. control. Consumption Technology Figure 13A unintentionally shows a motor with a propulsion system, the propulsion system. An inflatable inflatable actuator piston that does not move on a crucible in a rotating chamber, the chamber having a centerline concentric with the center of rotation; and a two-stage piston in the elongated chamber The pumping system, the elongated chamber has a continuous different cross-sectional area and circumference, all of which are assembled on the crankshaft shaft, a pressure reservoir, and an electric starter motor, the smallest pump and the starter violation Energy is supplied by solar energy. Figure 13B shows the motor of Figure η, in which the piston pump of the two-stage piston pumping system has been exchanged with a rotary pump mounted on the spindle shaft of the motor. Figure 13C is a schematic illustration of the motor of Figures 13A, nB having a propulsion system ''the propulsion system' containing a non-movable inflatable inflatable actuator piston within a rotating chamber, the chamber having a And the central center of the center of rotation, the chamber comprising four sub-chambers that are continuous with each other, the chamber having a continuously different transition cross-sectional area and circumference that rotates about a shaft that passes through the center of the chamber. Figure 13D schematically shows the suspension of the motor of Figure UB, including a drive belt. Figure 13E shows in unisonively the control member and pressure management of the motor for Figure Ua, Figure 3β, including a pressure reservoir. The continuously varying internal pressure of the actuator pistons is used by each of the actuator pistons 159900. Doc • 307· 201235565 A separate piston chamber combination is determined (computer controlled). Enclosed Space Volume Technology Figure 13F shows the pressure management of the inflatable piston of Figure 13C in accordance with the principles of Figure 11F, wherein each actuator piston is managed by a combination of two piston chambers. One piston chamber combination For continuously varying the pressure and a piston chamber combination for adjusting the pressure level for adjusting the speed/power of the motor. Figure 13G shows the pressurized system for the configuration of Figure 13F. Enclosed space volumetric technique Figure 14 shows several stages of the actuator piston, the circular chamber running around this stage of the actuator piston, and the stage of the actuator piston is changed by the chamber in the connected chamber It is necessary to change the internal pressure of the actuator piston by the volume under the pump piston. Figure 14A shows the configuration of Figure 14 with the cam wheel set connected to the piston rod of the pump piston in communication with a cam having a suitable profile. Figure 14C shows Figure 14D showing a circular chamber moving according to Figure 13, wherein the pressure in the actuator piston is defined by the pressure in the piston chamber assembly with the piston chamber assembly having the piston chamber The piston of the combined body is in communication with: a wheel set that runs on a spindle shaft that includes a cam having a particular contour. Figure 14A shows the rim and its suspension, and the auxiliary motor rotation shown as an electric motor; according to the configuration of Figure 16 having the configuration of Figure 14D built therein, the auxiliary motor makes the cam profile pressure controller ( "With wire drive 159900. Doc • 308* 201235565 “)” is connected to a passage containing the enclosed space of the actuator piston, which is in communication with the remote governor. Figure 14F shows an enlarged detail of the section of the piston of the mid-July work of Figure 14E when the piston is in the first circular position. Figure 14G shows an enlarged detail of a section of the piston in the circular chamber of the figure when the piston is in the second, circular position. Figure 14H shows the configuration of Figure 14E in which a gearbox (e.g., planetary gear type) is built in between the rim of the wheel set and the circular cavity. Auxiliary Power Source Figure 15A shows an H2 fuel cell, necessary components, and power lines as a power source for a repressurizing pump that pressurizes a force reservoir. Fig. 15B shows a combustion motor using n's generated by electrolysis of conductive water as a power source, the shaft of the combustible motor driving an alternator for charging a battery, the battery causing the electric motor to operate, and the electric motor The pump is connected for repressurizing the pressure reservoir. Figure 15C shows a combustion motor using h2 generated by electrolysis of conductive water as a power source, the shaft of the combustible motor being in direct communication with the pump(s) via the crankshaft for repressurizing the pressure reservoir. Figure 15D shows a combustion motor as a power source generated by electrolysis of electrically conductive water, the shaft of the combustible motor being in direct communication with the rotary pump(s) for repressurizing the pressure reservoir. Figure 15E shows a capacitor that is charged and is a power source for the electric motor. The electric motors are in communication with the pump(s) for repressurizing the pressure reservoir. 159900. Doc -309- 201235565 ESVT-Crankshaft Design_Multiple Uses of Components Figure 16A shows a scaled-up two-way actuator of Figure HG to Figure R. Figure 16B shows a prior study of the two-way actuator of Figure 16A. ESVT-Crankshaft Design_Multiple Uses of the Assembly Figure 17A shows, unintentionally, the two strokes of the actuator piston of the cylinder motor according to Figure A, wherein the second longitudinal position to the first longitudinal position The stroke is the power stroke ' and the stroke from the first longitudinal position to the second longitudinal position is the (no power) return stroke. Figure 17B shows a two-cylinder motor ("a" and "B") with a stroke according to the figure" whereby the crankshaft (consisting of two sub-crankshafts) is designed such that the power stroke of each cylinder is reversed ( 18〇.) Move in the direction. Figure 17C shows the two-cylinder motor according to Figure 11R, whereby the combustion here is a forced liquid cooling type whereby the sub-cranks are exchanged for one of the ESVT pumps for one of the inlet/outlet ports of a sub-crankshaft The shaft-population/exit is in communication with the other-crankshaft 2ESVT pump, and wherein the communication is controlled by a valve actuator according to Figure 210E, the motion of the valve actuators being by the camshaft Starting with a cam, the camshaft is driven 'and' by the combustible motor such that the beginning of the power stroke of the left cylinder is synchronized with the beginning of the return stroke of the right cylinder, and the second enclosed space of a sub-crankshaft The third enclosed space of the other sub-crank is separated. Figure 17C1 shows an enlarged view of the left side of Figure 17C and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 17Cr shows an enlarged view of the right side of Figure 17C. Figure 17D shows the power stroke of the left cylinder of the motor according to Figure i7C 159900. Doc • 310· 201235565, and the middle of the return stroke of the right cylinder. Figure 17D1 shows an enlarged view of the left side of Figure 17D and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 17Dr shows an enlarged view of the right side of Figure 17D. Figure 17E shows the end of the power stroke of the left cylinder of the motor according to Figure 17D, and the end of the return stroke of the right cylinder. Figure 17E1 shows an enlarged view of the left side of Figure 17E and the relationship between the connecting rods of the two actuator pistons. Figure. Fig. 17Er shows an enlarged view of the right side of Fig. 17E. Figure 17F shows the beginning of the return stroke of the left cylinder of the motor of Figure 17 and the beginning of the power stroke of the right cylinder. Figure 17F1 shows an enlarged view of the left side of Figure 17F and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 17Fr shows an enlarged view of the right side of Figure 17F. Figure 17G shows the middle of the return stroke of the left cylinder of the motor of Figure 17F and the power stroke of the right cylinder. Figure 17G1 shows an enlarged view of the left side of Figure 17G and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 17Gr shows an enlarged view of the right side of Figure 17G. Figure 17H shows the tail of the return stroke of the left steam red of the motor of Figure 17G, and the end of the power stroke of the right cylinder. Figure 17H1 shows an enlarged view of the left side of Figure 17H and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 17Hr shows an enlarged view of the right side of Figure 17H. 159900. Doc -311 - 201235565 ESVT-Crankshaft Design - Multiple Uses of Components Figure 18A shows a two-steam red motor ("a" and "B") with a stroke according to Figure 17A. The crankshaft (by two sub-cranks) The shaft composition is designed such that the power stroke of each actuator piston moves in the same (0.) direction. Figure 1AA1 shows an enlarged view of the left side of Figure 18A and a diagram of the relationship between the connecting rods of the two actuator pistons. Fig. 18Ar shows an enlarged view of the right side of Fig. 18A. Figure 18B shows a simple configuration of the two-cylinder motor according to Figure 17C, whereby the combustion motor here is a forced liquid-cooled type, including one of the two actuator pistons of the ESVT pump, the first crankshaft The second enclosed space is in communication with the third enclosed space of the other sub-cranked shaft such that the beginning of the power stroke of the left cylinder is synchronized with the beginning of the power stroke of the right cylinder. Fig. 18B1 is a view showing an enlarged view on the left side of Fig. 18B and a relationship between the connecting rods of the two actuator pistons. Figure 18Br shows an enlarged view of the right side of Figure 18B. Figure 18C shows the middle of the power stroke of the left and right cylinders of the motor of Figure 18B. Fig. 18C1 is a view showing an enlarged view on the left side of Fig. 18C and a relationship between the connecting rods of the two actuator pistons. Figure 18Cr shows an enlarged view of the right side of Figure 18C. Figure 18D shows the end of the power stroke of the left and right cylinders of the motor of Figure 18C. Figure 18D1 shows an enlarged view of the left side of Figure 18D and a diagram of the relationship between the connecting rods of the two actuator pistons. 159900. Doc - 312 - 201235565 Fig. 18Dr shows an enlarged view of the right side of Fig. 18D. Fig. 18E shows the beginning of the return stroke of the left and right cylinders of the motor according to Fig. 18D. Figure 18E1 shows an enlarged view of the left side of Figure 18E and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 18E shows an enlarged view of the right side of Figure 18E. Figure 18F shows the middle of the return stroke of the left and right cylinders of the motor of Figure 18E. φ Figure 18F1 shows an enlarged view of the left side of Figure 18F and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 18Fr shows an enlarged view of the right side of Figure 18F. Figure 18G shows the end of the return stroke of the left and right cylinders of the motor of Figure 18F. Figure 18G1 shows an enlarged view of the left side of Figure 18G and a diagram of the relationship between the connecting rods of the two actuator pistons. Figure 18Gr shows an enlarged view of the right side of Figure 18G. #CT-Crankshaft Design-Multiple Uses of Components Figure 19A shows a cylinder motor based on one of Figures 11B and 11C, in which some parts have been further made, the auxiliary power source is a combustion motor, and the combustion motor is burned from the electrolysis of H20. H2. 19B shows a two-cylinder motor based on FIG. 19A, wherein the two vapor reds are mirror-positioned with respect to a centerline of the connection such that the third enclosed space (outlet) communicates with each other via the connection of the two sub-crankshafts, The first-to-the-space (inlet) communicates with each other outside the crankshaft (by the check valve) 159900. Doc-313-201235565 and wherein the crankshaft (consisting of two sub-crankshafts) is designed such that the power stroke of each actuator piston moves simultaneously (simultaneously) in the same (0.) direction (according to Figure 18A) principle). Fig. 19B1 shows an enlarged view of the left side of Fig. 19B. Figure 19Br shows an enlarged view of the right side of Figure 19B. Figure 19C shows a two-cylinder motor based on Figure 19A, wherein a comparable enclosed space (here a third enclosed space) is connected to each other via the sub-cranked shafts, while the second enclosed space is gathered externally Together (by a check valve), and wherein the crankshaft (consisting of two sub-crankshafts) is designed such that the power stroke of each actuator piston is in the same (18 〇.) direction (different Time) Move (according to the principle of Figure 18A). Fig. 19C1 shows an enlarged view of the left side of Fig. 19C. Figure 19Cr shows an enlarged view of the right side of Figure 19C. Brief Description of the 1962 Rounded Form In the following, a preferred embodiment of the present invention will be described with reference to the drawings in which: Figure 21A shows a longitudinal section of a conical shaped chamber having a constant maximum working force characteristic of a pump, which is shown Common (pressure) boundaries, and convex and conical shapes on the sides of the longitudinal section between the boundaries. Figure 218 shows the shape of the chamber of Figure 21 (1 bar overpressure) and the other chamber (16 bar overpressure) (for the same chamber length) (dashed line;). Figure 22 shows a longitudinal section of the conical shaped chamber of Figure 21 showing the expansion chamber as part of the chamber. Figure 23 shows an advanced conical shaped chamber having a constant maximum working force characteristic of the pump, shown from the inner conical portion of the chamber to the second longitudinal direction 159900. Doc -314· 201235565 A specific internal concave transition to the straight portion inside the position, which is parallel to the central axis of the chamber. Figure 24 shows an expandable deformable piston that does not automatically move from a second longitudinal position to a first longitudinal position because the inner wall of the chamber of Figure 23 is parallel to the central axis. Figure 25 shows a chamber of the constant force type having a hose connector ' as an outlet connected to a hose. BRIEF DESCRIPTION OF THE DRAWINGS In the following, a preferred embodiment of the invention will be described with reference to the drawings in which: Figure 30A shows the circular chamber of Figure 12B with the piston moving in a non-moving chamber. Figure 30B shows the circular chamber of Figures 13C and 14D with the piston not moving and the cavity moving. Here is the design of the same circular chamber and subchamber as the design of Fig. 30A. Figure 31A shows a scaled-up detail of the section χ_χ of the chamber of Figure 31D, showing the section χ_χβ Figure 3 1 Β. Mathematical description of a circular chamber and piston Figure 32 shows that the wall of the chamber intersects a circle orthogonal to the base circle at a circle centered at the base circle. Figure 32 shows a section of the boundary of the piston. Figure 32C shows the geometry of the cover. For the area of the cover and the internal volume, only the values α and /1 are required. See equations (2^ and 卩2). The radius of the virtual sphere is (2. Given in 3). Figure 32D shows a piston with an end cap. 159900. Doc • 315- 201235565 Figure 32E shows the piston with an end cap inside the transparent Fermi chamber. Figure 32F shows the pure contact area between the piston and the chamber visible inside the transparent chamber wall. Figure 32G shows the area of contact between the piston and the chamber. Figure 32H shows a section of the chamber wall, the chamber reaction force is marked by gray, the total force on the section is orthogonal to the chamber wall, for the section, the (variable) longitudinal length of the section being shown and the piston The value of the force proportional to the internal pressure. Figure 321 shows a section of Figure 32H with additional cross sections to provide an open view. Fig. 32J shows Fig. 32H, and the red vector is a component of the gray force in the longitudinal direction. Figure 32K does not show Figure 32J' with additional cross-section to provide an open view. Fig. 32L shows that Fig. 32J' in which the actual sliding force along the wall is shown in blue' is obtained by projecting a red vector orthogonal to the chamber wall. Figure 32M shows Figure 32L with additional cross-section to provide an open view. BRIEF DESCRIPTION OF THE DRAWINGS In the following, a preferred embodiment of the invention will be described with reference to the drawings in which: Figure 40A shows a longitudinal section of a pump having a piston at a first longitudinal position, the piston comprising a support member, a zero shape Ring and flexible impervious layer (the last mentioned case is supported by a foam). Figure 40B shows details of the suspension of the vulcanized support member, the ❾ ring and the flexible, water impermeable layer. 159900. Doc • 316· 201235565 Figure 40C shows the longitudinal section of the piston of Figure 40A at a second longitudinal position. Figure 41A shows a top view of the piston of Figure 40A and the wear surface of the chamber as viewed from the first longitudinal position. Figure 41B shows details of the suspension of the support members of the shackle and the lying spring of the piston of Figure 40A. Figure 41C shows a cross section of the chamber of Figure 40A with the piston not in the second longitudinal position. Figure 41D shows a bottom view of the piston of Figure 40A and a section of the chamber at a first longitudinal position showing the spiral reinforcement of the water impermeable sheet. Figure 41E shows a bottom view of the piston of Figure 4A, and a section of the chamber at a first longitudinal position showing the spiral reinforcement of the water impermeable sheet. Figure 42A shows a longitudinal section of a piston at a first longitudinal position, the piston comprising a support member, a stirrup ring and a flexible, water impermeable layer (the last mentioned case is at a particular angle to the central axis of the chamber). Figure 42B shows details of the suspension of the vulcanized support member, the 〇 ring and the flexible, water impermeable layer. Figure 42C shows the longitudinal section of the piston of Figure 42A at a second longitudinal position. BRIEF DESCRIPTION OF THE 19650 GRAPH Figure 50 shows a top view of a foam piston (specifically, a suspension of a reinforcing pin). Figure 51 shows a longitudinal section A_A of a piston made of a PU foam. Figure 52 shows a longitudinal section 活塞;6 of the piston of Figure 50. 159900. Doc • 317· 201235565 19660 BRIEF DESCRIPTION OF THE DRAWINGS Figure 60 shows a longitudinal view and section of the end of a container-type piston. Figure 61 shows details of the ends of the container-type piston of Figure 60. Figure 62 shows the container-type piston at the beginning and end of the stroke in the chamber where the force applied to the piston rod is constant (see 19620). BRIEF DESCRIPTION OF THE DRAWINGS In the following, preferred embodiments of the invention will be described with reference to the drawings, in which: FIG. In the following, the figures or figures are shown. The cross section means a section perpendicular to the moving direction of the piston and/or the chamber, and the longitudinal section is a section in the direction of the moving direction: Fig. 101 shows a cylinder and A so-called dynamometer of a single-stage, single-acting piston pump with a fixed diameter piston. Figure 102A shows a dynamometer of a piston pump in accordance with the present invention, with Part A showing the piston moving option and Part 3 showing the chamber moving. Figure 102B shows a power diagram of a pump in accordance with the present invention in which the cross section again increases from a particular point in the pump stroke, but still increases the pressure. Figure 103A shows a longitudinal section of the pump having a fixed cross-sectional area of the pressurized chamber and a piston having a dimension that changes axially in the radial direction during the stroke, shown at the beginning of the pump stroke and End piston configuration (first embodiment). Figure 103B shows an enlarged view of the piston arrangement of Figure 1-3a at the beginning of the stroke. Figure 103C shows an enlarged view of the piston configuration of Figure 1-3a at the end of the stroke. Figure 0 159900. Doc 201235565 Figure 103D shows a longitudinal section of the chamber of the foot pump according to the invention, wherein simultaneously shown to keep the operating force substantially constant (as an existing low pressure (dotted line) foot pump and high pressure (dashed line) foot pump cylinder The size of the comparison). Figure 104A shows a longitudinal section of a pump having a fixed different cross-sectional area of a pressurized chamber and a piston having a radially/partially axially varying dimension during the stroke, shown in the pump stroke Piston configuration at the beginning and end (second embodiment). Figure 104B shows an enlarged view of the piston arrangement of Figure 1-4A at the beginning of the stroke. Figure 104C shows an enlarged view of the piston arrangement of Figure 1-4A at the end of the stroke. Figures 1-4D show the wear side A-A of Figure 104B. Figure 104E shows a section B-B of Figure i〇4C. Figure 104F shows an alternative solution to the loading portion of Figure i〇4D. Figure 105A shows a longitudinal section of the pump having a fixed cross-sectional area of the pressurized chamber and a piston having a dimension that changes axially in the radial direction during the stroke, shown at the beginning of the pump stroke And the end piston configuration (third embodiment). Figure 105B shows an enlarged view of the piston arrangement of Figure 5 at the beginning of the stroke. Figure 105C shows an enlarged view of the piston configuration of Figure i〇5a at the end of the stroke. Figure 105D shows a section C-C of Figure 〇5Α. Figure 105 shows the section 〇-0 of Figure 1〇5. 159900. Doc-319-201235565 Figure 105F shows the pressurized chamber of Figure 105A having a piston member having a sealing member made of a composite of materials. Figure 105G shows an enlarged view of the piston member of Figures 1 - 5F during the stroke. Figure 105H shows an enlarged view of the piston member of Figures 1 - 5F at the end of the stroke (both when still under pressure and when no longer under pressure). Figure 106A shows a longitudinal section of a pump having a fixed cross-sectional area of a pressurized chamber and a fourth embodiment of a piston having a dimension that varies axially in the radial direction during the stroke, shown in the pump Piston configuration at the beginning and end of the stroke. Figure 106B shows an enlarged view of the piston arrangement of Figures 1A-6A at the beginning of the stroke. Figure 106C shows an enlarged view of the piston arrangement of Figures 1-6A at the end of the stroke. Figure 106D shows a fifth embodiment of the pressurized chamber and piston of Figure 106A having a dimension that changes axially in the radial direction during the stroke, showing the piston configuration at the beginning and end of the pump stroke. Figure 106E shows an enlarged view of the piston arrangement of Figure 1〇6〇 at the beginning of the stroke. Figure 106F shows an enlarged view of the piston arrangement of Figures 1 - 6D at the end of the stroke. Figure 107A shows a longitudinal section of a pump comprising a concave portion having a fixed size pressurized chamber to a wall and a sixth embodiment of the piston having a dimension that changes axially in the radial direction during the stroke, Shown on the pump stroke of 159900. Doc •320- 201235565 Piston configuration at the beginning and end. Figure 107B shows an enlarged view of the piston arrangement of Figure 1A5A at the beginning of the stroke. Figure 107C shows an enlarged view of the piston arrangement of Figure 1A-5A at the end of the stroke. Figure 107D shows a section E-E of Figure iB. Fig. 107E shows a section F_F of Fig. 7C. Fig. 107F shows an example of a cross-section made by the Four-Frequency expansion method of the pressurizing chamber, the cross-sectional area of the pressurizing chamber being reduced while the circumference is kept constant. Figure 107G shows a variation of the pressurized chamber of Figure 现在7, which now has a longitudinal section and a fixed cross-section such that the area of the section during the pump stroke is reduced but the circumference of the section is approximately Keep m salty and small in a way that is designed to be low. Fig. 107H shows a cross section G_G (dotted line) and a longitudinal section H of Fig. 107G. Figure 1071 shows the cross section G_G (dotted line) and longitudinal section of Figure 107H. Lu ® 1〇7J shows the variant of the piston of Fig. 10 with the wearing surface H-H of Fig. 1〇7H. Fig. 107K shows another example of a cross section made by the Four-Frequency expansion method of the pressurizing chamber, the cross-sectional area of the pressurizing chamber being reduced while the circumference is kept constant. Fig. 107L shows an example of the optimum convex shape of the cross section at a specific approximate stroke. Fig. 107M shows an example of the optimum non-convex shape of the cross section under the four bundles of the win, and the special bundle. 159900. Doc • 321· 201235565 Fig. 108A shows a longitudinal section of a pump comprising a convex portion of a wall of a pressurized chamber having a fixed size and a seventh embodiment of a piston having a radial direction in the axial direction during the stroke Change the size to show the piston configuration at the beginning and end of the pump stroke. Figure 108B shows an enlarged view of the piston arrangement of Figures 1 to 5 at the beginning of the stroke. Figure 108C shows an enlarged view of the piston arrangement of Figures 1A-5A at the end of the stroke. Figure 109A shows a longitudinal section of a pump having a fixed different cross-sectional area of the pressurized chamber and an eighth embodiment of the piston 'the piston having a dimension that changes axially in the radial direction during the stroke, shown on the pump stroke Piston Configuration at the Beginning and End of Figure 109B shows an enlarged view of the piston arrangement of Figure i〇9A at the beginning of the stroke. Figure 109C shows an enlarged view of the piston arrangement of Figures 1A-9A at the end of the stroke. Figure 109D shows the piston of Figure iB with different rotational configurations. Figure 110A shows a ninth embodiment of a piston similar to the piston of Figures 1 〇 9A having a different cross-sectional area of the pressurized chamber. Figure 110B shows an enlarged view of the piston of Figure 11A at the beginning of the stroke. Figure 110C shows an enlarged view of the piston of Figure 110A at the end of the stroke. Figure 111A shows a longitudinal section of a pump having a fixed cross-sectional area of a pressurized chamber and a tenth embodiment of a piston having a dimension that varies axially in the radial direction during the stroke, shown in the pump The beginning of the stroke and 159,900. Doc •322.2012. The piston configuration at the end of 201235565. Figure 111B shows an enlarged view of the piston of Figure iua at the beginning of the stroke. Figure me shows an enlarged view of the piston of Figure 111 at the end of the stroke. Figure 112A shows a longitudinal section of a pump having a fixed cross-sectional area of a pressurized chamber and an eleventh embodiment of a piston having a dimension that changes axially in the radial direction during the stroke, shown in the pump Piston configuration at the beginning and end of the stroke. Figure 112B shows an enlarged view of the piston of Figure i12a at the beginning of the stroke. φ Figure 112 (: an enlarged view of the piston of Figure 112A showing the end of the stroke. Figure 113A shows a longitudinal section of the chestnut having a variable cross-sectional area of the pressurized chamber and a piston having a fixed The geometrical dimensions show the configuration of the combination at the beginning and end of the stroke. Figure 113B shows an enlarged view of the configuration of the combination at the beginning of the pump stroke. Figure 113C shows an enlarged view of the configuration of the combination during the pump stroke. Figure 113D shows an enlarged view of the configuration of the combination at the end of the pump stroke. Figure 114 shows the longitudinal section of the spring 'The pump has a variable non-φ cross-sectional area of the pressurized chamber and a piston having Variable geometry, showing the configuration of the combination at the beginning, during and at the end of the pump stroke. 6 Brief description of the phantoms In the following, a preferred embodiment of the invention will be described with reference to the drawings, wherein: Figure 201A shows A longitudinal section of the non-moving piston in the unstressed cylinder at the first longitudinal position, showing the piston at the production of the piston and under pressure. Figure 201B shows Figure 201A on the wall of the cylinder Contact of pressurized piston 159900. Doc -323- 201235565 Pressure. Figure 202A shows a longitudinal section of the piston of Figure 201A in a cylinder at a first (right) longitudinal position and a second (left) longitudinal position, the piston being uncompressed. Figure 202B shows the contact pressure of the piston of Figure 202A on the wall of the cylinder at the second longitudinal position. Figure 202C shows a longitudinal section of the piston of Figure 201A in a cylinder at a second longitudinal position, the piston being compressed at the same pressure level as the pressure level of Figure 201A, also shown at the first longitudinal position (production) size piston. Figure 202D shows the contact pressure of the piston of Figure 202C on the wall of the cylinder at the second longitudinal position. Figure 203A shows a longitudinal section of the piston of Figure 201A in a cylinder at a first longitudinal position, showing the piston when it is at the production size of the piston and when the piston is subjected to the pressure in the chamber. Figure 203B shows the contact pressure of the piston of Figure 203A on the wall of the cylinder. Figure 204A shows a longitudinal section of a non-moving piston in accordance with the present invention in an uncompressed cylinder at a second longitudinal position, showing the piston at the production size of the piston and when pressurized to a particular level. Figure 204B shows the contact pressure of the pressurized piston of Figure 204A on the wall of the cylinder. Figure 204C shows a longitudinal section of a non-moving piston in accordance with the present invention in a cylinder at a second longitudinal position, shown in a first longitudinal position when in the production size of the piston and when pressed to the same level as the level of Figure 204A. Pistons. 159900. Doc •324· 201235565 Figure 204D shows the contact pressure of the piston of Figure 204C on the wall of the cylinder. Figure 205A shows a longitudinal section of the piston of Figure 204A in an uncompressed cylinder at a second longitudinal position, showing the piston at the production and compression of the piston. Figure 205B shows the contact pressure of the pressurized piston of Figure 205A on the wall of the cylinder. Figure 205C shows a longitudinal section of the piston of Figure 204A in the cylinder at the second longitudinal position, showing the piston when it is at the production size of the piston and when subjected to compression from the pressure of the cylinder. Figure 205D shows the contact pressure of the piston of Figure 205C on the wall of the cylinder. Figure 206A shows a longitudinal section of a chamber having fixed different cross-sectional areas and a first embodiment of a piston comprising a fabric reinforcement having a dimension that varies axially in the radial direction during the stroke, shown on the stroke The piston arrangement in the beginning and at the end of the compression, wherein the piston has its production size without being pressed. Figure 206B shows an enlarged view of the piston of Figure 206A at the beginning of the stroke. Figure 206C shows an enlarged view of the piston of Figure 206A at the end of the stroke. Figure 206D shows a 3-dimensional representation of the reinforcing matrix of the elastic fabric material in the wall of the container as the container will expand. Figure 206E shows the pattern of Figure 206D as the wall of the container has expanded. Figure 206F shows a 3-dimensional representation of the reinforcement pattern of the inelastic fabric material in the wall of the container as the piston will expand. 159900. Doc-325 - 201235565 Figure 206G shows the pattern of Figure 206F as the wall of the container has expanded. Figure 206H shows the production details of a piston with a fabric reinforcement. Figure 207A shows a longitudinal section of a chamber having fixed different cross-sectional areas and a second embodiment of a piston comprising a fiber reinforcement ("grid effect"), wherein the size of the elastic material of the wall is radially in the stroke Axially varying, showing a piston configuration that is pressurized at the beginning and end of the stroke, where the piston has its production size without pressure. Figure 207B shows an enlarged view of the piston of Figure 207A at the beginning of the stroke. Figure 207C shows an enlarged view of the piston of Figure 207A at the end of the stroke. Figure 208A shows a longitudinal section of a chamber having fixed different cross-sectional areas (having different circumferential lengths), and a third embodiment of a piston comprising a fiber reinforcement (without r-grid effect), wherein the elasticity of the wall The dimensions of the material change axially in the radial direction during the stroke, exhibiting a piston configuration that is compressed at the first longitudinal position and at the second longitudinal position, wherein the piston has its production size without pressure. Figure 208B shows an enlarged view of the piston of Figure 2A 8A at the beginning of the stroke. Figure 208C shows an enlarged view of the piston of Figure 2A 8A at the end of the stroke. Figure 208D shows a top view of the piston of Figure 2A with reinforcement in the wall, the reinforcement being in a plane passing through the central axis of the piston, left side: at the first longitudinal position, right side: at the second longitudinal position. Figure 208E shows a top view of a piston of the piston of Figure 2A with a stiffener in the wall, the reinforcement being in a plane partially through the central axis and partially outside the central axis of the piston, left: in the first longitudinal position At the right side: at the second longitudinal position. 159900. Doc-326-201235565 shows a top view of a piston of the piston of Fig. 2〇8a with a reinforcement in the wall, the reinforcement being located in a plane that does not pass through the central axis of the piston, left side: at the first longitudinal position , right side: at the second longitudinal position. Figure 208G shows production details of a piston with fiber reinforcement. 209A shows a fourth embodiment of a longitudinal section of a chamber having fixed different cross-sectional areas (having different circumferential lengths) and a piston comprising an "octopus" device that limits the extension of the container wall by the tentacle, The hand can be inflated, showing a piston configuration that is compressed at a first longitudinal position of the chamber and at a second longitudinal position of the chamber, wherein the piston has its production size without being pressurized. Figure 209B shows an enlarged view of the piston of Figure 2A 9A at a first longitudinal position of the chamber. Figure 209C shows an enlarged view of the piston of Figure 2〇9a at a second longitudinal position of the chamber. 210A shows an embodiment of FIG. 206 in which the pressure inside the piston can be inflated by a check valve in, for example, a Schrader valve located in the handle and/or, for example, a piston rod. The change, and wherein the enclosed space balances the change in the volume of the piston during the stroke. Figure 210B shows a bushing in place of an inflation valve that enables connection to an external source of pressure. Figure 210C shows details of the guidance of the stem of the check valve. Figure 210D shows the flexible piston of the check valve in the piston rod. Figure 210E shows an embodiment of Figure 206 in which a pressure source is used and used for 159900. Doc 327· 201235565 The pressure source causes one of the inlet valves of the piston to be inflated and the outlet valve for releasing the pressure to one of the pressure sources to exchange the volume of the enclosed space of FIGS. 210A to 21D, according to the valve actuator of FIG. 211D Enlarged detail of the combined body. Figure 210F shows the embodiment of Figure 10E in which a steerable valve and a spout or a nozzle are shown as black boxes. 211A shows an embodiment of FIG. 206 in which the pressure inside the piston can be maintained during the stroke, and wherein the second enclosed space can be inflated via a Schrader valve located in the handle, thereby passing a piston The configuration is in communication with the first enclosed space in which the piston can be inflated by a Schrader valve + valve actuator configuration, wherein the pressure of the chamber acts as a pressure source and the outlet valve of the chamber can It is manually controlled by a rotatable pedal. Figure 211B shows the piston arrangement and its bearings wherein the piston is disposed in communication between the second enclosed space and the first enclosed space. Figure 211C shows an alternative piston configuration that adjusts itself within the longitudinal direction of the piston rod to accommodate the varying cross-sectional area. Figure 211D shows an enlarged view of the inflated configuration of the piston of Figure 211A at the end of the stroke. Figure 211E shows an enlarged view of the bypass configuration of the valve actuator for closing and opening the outlet valve. Figure 211F shows an enlarged view of the automatic closed and open configuration of the outlet valve, showing a comparable system for obtaining a predetermined pressure value (dashed line) in the piston. 211G shows an enlarged view of the inflated configuration of the piston of FIG. 211A, the inflated configuration including a combination of a valve actuator and a spring-operated cover that makes it possible to automatically inflate the piston from the chamber to Specific pre-159900. Doc -328· 201235565 Constant pressure.

Figure 212 shows the pressure of a configuration. Wherein the pressure in the container may depend on the longitudinal section of the chamber having an elastic or flexible wall (having a product) and the combination of a fixed geometry at the beginning and end of the pump stroke, as shown in Figure 213A of the chamber. Configuration. The pistons of different cross-sections, Figure 2UB shows an enlarged view of the configuration of the combination at the beginning of the pump stroke. Figure 213C shows an enlarged view of the configuration of the combination during the pump stroke. Figure 213D shows an enlarged view of the configuration of the combination at the end of the pump stroke. Figure 214 shows a longitudinal section of a chamber having an elastic or flexible wall (having a different cross-sectional area) and a piston having a variable geometry showing the configuration of the combination at the beginning, during and at the end of the stroke. Figure 215A shows an example of a cross-section made by a Fourier series expansion of a pressurized chamber having a reduced cross-sectional area and a constant circumferential size. Figure 215B shows a variation of the pressurized chamber of Figure 207A, which now has a longitudinal section and a fixed cross-section such that the area of the section decreases during the pump stroke but the circumference of the section remains substantially constant Or reduce the design in a lower degree. Figure 215C shows a cross section G-G (dotted line) and a longitudinal section H_H of Figure 215B. Figure 215D shows a cross section G-G (dotted line) and a longitudinal wearing surface ι_ι of Figure 215C. Figure 215E shows another example of a cross-section made by a Fourier-Frequency expansion of a pressurized chamber. The cross-sectional area of the pressurized chamber is reduced while the circumference is kept constant. 159900.doc • 329- 201235565 Figure 215F shows an example of the best convex shape for a cross section under a particular constraint. Figure 2 shows the combination of the piston in the case where the piston moves through the center of the wedge in the cylinder. Figure 217A shows the optimal chamber for human engineering for systemic and manual operation. Figure 217B shows a corresponding forced stroke map. Figure 218A shows an example of a moveable power unit suspended under a parachute. Figure 218B shows details of the moveable power unit. BRIEF DESCRIPTION OF THE DRAWINGS In the following description, the foregoing features and other aspects of the present invention are explained in conjunction with the accompanying drawings in which: FIG. 301 shows valve actuation in a clip valve connector to which a Schrader valve can be coupled The first embodiment of the device. Figure 301A shows an enlarged view of the detail of Figure 301 and the passage around the piston. Figure 301B shows a section G-G of Figure 301A. Figure 3 02 shows a second embodiment of a valve actuator in a universal pinch valve connector having a streamlined start pin. 3A-2A shows an enlarged view of the detail of FIG. Figure 3 02:6 shows a section 1^-11 of Figure 302. Figure 3 03 shows a third embodiment of a valve actuator in a squeeze valve connector. Figure 303A shows an enlarged view of the detail of Figure 303. 159900.doc • 330- 201235565 Figure 304 shows a valve actuator that includes a firing pin and a wall of a cylinder in a permanent assembly (e.g., from a chemical plant). Figure 305 shows a fourth embodiment of a valve actuator in a universal valve connector. BRIEF DESCRIPTION OF THE DRAWINGS In the following, preferred embodiments of the invention will be described with reference to the drawings, in which the invention is explained in detail below by means of the drawings and drawings. The following is shown in the old figure, the cross section means the section perpendicular to the moving direction of the piston and/or the chamber, and the longitudinal section is the section in the direction of the moving direction: Fig. 401Α shows the foot of Fig. 401 A top view of a pump of the step pump type in which the combined body is rotatable about a line XX, γγ or 关于 about the ground surface, and the angle is not limited by the suspension. Figure 401A shows a rear view of the pedaling system of Figure 401. Figure 402A shows a top view of the foot pump type of Figure 402, where the joint can be moved in a three dimensional manner with respect to the surface and the angle is limited by the spring force of the transition between the combination and the base. Figure 402 shows a rear view of the foot pump. Figure 402C shows a top view of the pump of Figure 402 with the handle moved to a position forward of its rest position. Figure 402D shows a top view of the pump of Figure 402 with the handle moved to the rear of its rest position. Figure 402A shows a top view of the pump of Figure 402 with the handle moved to the left position in front of its rest position. Figure 402F shows a top view of the pump of Figure 402 with the handle moved to the left position of the rear of its rest position. 159900.doc - 331 · 201235565 Figure 402G shows a top view of the pump of Figure 402B with the handle moved to the right position in front of its inactive position. Figure 402H shows a top view of the pump of Figure 402B with the handle moved to the right position of the rear of its rest position. Figure 403 A shows a side view of a foot pump having a flexible transition between the chamber of the combination and the base. Figure 403B shows an enlarged view of the transition of Figure 403A. Figure 403C shows a rear view of a foot pump with another flexible transition between the chamber of the combination and the base. Figure 403D shows an enlarged view of the transition section of Figure 3C. Figure 404A shows a rear view of a foot pump with a cover that allows the piston rod to move in the lateral direction of the combination. Figure 404B shows an enlarged view of the cross section of the cover of Figure 4A when the piston rod is pulled out to its maximum value (without lateral movement). Figure 404C shows a cross section of Figure 404B when the piston rod is pulled out to its maximum value (with the piston rod rotating to the left). Figure 404D shows an enlarged view of the cross section of the cover of Figure 404A when the piston rod is not pulled out (without lateral movement). Figure 404E shows a cross section of Figure 404D when the piston rod is not pulled (with the piston rod translated laterally to the left). Figure 405A shows a top view of the foot pump type of Figure 405B, wherein the angle between the centerline of the handle portion opposite the centerline of the bond and the centerline of the combination is less than 180°. Figure 405B shows a side view of the handle of the foot of Figure 405A. 159900.doc • 332-201235565 Figure 406A shows a top view of the foot pump type of Figure 406B, wherein the angle between the centerline of the handle portion opposite the centerline of the chamber and the centerline of the chamber is greater than 180°. Figure 406B shows a side view of the handle of the foot pump of Figure 406A. [Main component symbol description] 1 Non-pressure chamber / meshing surface / contact point / constant maximum force chamber / pressurizing chamber 2 Engagement surface / contact point /wall part / chamber

3 Engagement surface / contact point / central axis / wall section 4 Base / convex wall section / wall section 5 Piston / rigid surface / transition section / wall section 5 ' Piston 5 * Piston 5 ' * Piston 5 " * Deformed piston 6 Combined body/wall part/longitudinal section/piston/piston rod 7 Chamber/concave wall part/longitudinal section/cover 8 Guide/seal part 8, sealing part 9 Piston rod/common boundary/loading part 9 'Loading part / piston rod 9 · 1 section 9.2 section 9.3 section 159900.doc -333 - 201235565 ίο 10* 11 12 13 14 15 15'* 15,M 16 17 18 19 20 20' 21 22 23 24 25 25. 26 26' 26" Cavity to / Handle / Longitudinal section / Support section Pressure chamber reinforcement / Common boundary / Locking member Rest position / Longitudinal section / Entry transition / Common boundary / Valve reinforcement / Start position / Longitudinal section / outlet channel piston / starting position / common boundary / component piston piston starting position / longitudinal section / transition section starting position / common boundary / transition section starting position / longitudinal section / transition section starting position / common boundary / center Axial/longitudinal central axis bushing / longitudinal section / piston Piston protrusion / common boundary / pressurized chamber groove / longitudinal section / cooling rib bushing / common boundary / piston rod projection / longitudinal section / cover groove / cover / common boundary / elastically deformable seal Elastically deformable sealing member guiding member / longitudinal section portion / member guiding member guiding member 159900.doc -334 - 201235565 27 center line / common boundary / portion 28 〇 ring / longitudinal section / support portion 28' compression ring 28" Compression ring 29 Space/longitudinal section/ring 29, space 29" Space 30 Center axis/longitudinal section/axis 31 Convex contact inner surface/longitudinal section/loading section/loading member 32 Center axis/longitudinal section / hole 33 space / longitudinal section / stop surface 33' space 33 " space 34 space / longitudinal section / guide member 34, 34 " 35 36

Space space contact surface / longitudinal section / spring surface / outer shape / piston 36' piston 37 surface / outer shape / sealing edge 38 wall / outer shape / sealing edge 39 central axis 40 pedestal / sealing member 159900.doc • 335. 201235565 40, sealing member 41 protrusion/seal member/skull ring/base 4Γ sealing member 42 reinforcement/spring/flexible pad/loading member 43 base/support member/hose 43' separate member 44 piston/shaft Rod/Outlet 45 Piston Rod/Piston 46 Spring/Piston Rod 46' Spring 47 Bracket/Check Valve 48 Sealing Edge/External Atmosphere 49 Piston/Expansion Pressure Groove 49' Piston 50 Piston Member/Inlet Check Valve 51 Left Part/ Reinforcement / Outer Wall 52 Handle / Clip / Inner Wall 53 Right Part / Protruding / Tip 54 Center Axis / Cover / Bottom 55 Combination / Lining / Cylinder Ring 56 Central Axis / Rib / Chamber 57 Central Axis / Rib 58 left part / sealing edge / gas seal thread 59 handle / piston / gas seal thread 159900.doc -336 - piston right part / chamber center point / center axis / wall / cylindrical wall part center point / conical wall Partial cone Wall section conical wall section cylindrical wall section / pipe transition section / closed space transition section / valve connector transition section / space transition section base / pressurized chamber flexible gasket / cylindrical section transition section inflatable piston / Continuous concave curved section transition section inlet check valve / almost cylindrical part outlet check valve / piston member piston member hose / outlet passage measurement space / check valve measurement space / basic elastic material conical chamber / Sealing member / Constant force chamber inner wall / reinforcement - 337 - 201235565 82 Reinforcement / convex wall 83 Sealing edge / common boundary 84 Support member / common boundary 85 Center axis / folding 86 Joint / specific internal concave shape 86.1 Concave subsection 86.2 Concave subsection 86.3 Concave subsection 87 Folding 88 Common boundary 89 Outer wall 90 Pressurizing chamber 91 Continuous convex curve 92 Piston 92' Piston/piston member 93 Outlet passage 94 Inlet passage 95 Check valve 96 check valve 97 piston rod 99 lining/skin 100 reinforcement/skin/chamber/chamber part 101 cover/skin/bottom part 102 sealing edge/pipe thread 159900.doc -338- 201235565

102' Sealing edge 103 Compressible medium 103 Bottom 103' Via compressed medium 104 Outlet 105 Hose connection 106 Piston 107 Hollow piston rod 108 Check valve 109 Space 110 Skin/hose/shape 111 Fiber/hose clamp 112 Sealing part / Hole 113 spring force ring 114 reinforcement ring 115 shape 117 sealing edge 118 piston 118, piston 120 piston rod 121 cover 122 cover 123 hole 124 incompressible medium 159900.doc -339. 201235565 124' incompressible medium 125 hollow channel 126 spring force operation Piston / Movable Piston / Flexible Piston 127 Spring 128 Piston Rod 129 Sealing Surface 129 ' Sealing Edge ' 130 Fiber 131 Cover 132 Pad, 133 Watertight Air Bag 134 Sealing Surface 135 Shoulder 136 Incompressible Media 137 Compressible Media 138 Piston 139 Sealing ring 140 Piston rod 141 Cylinder 145 Stopper 146 Piston 146' Piston 148 Piston 148' Load regulating member / piston 159900.doc -340- 201235565

149 Piston 149' Piston 150 Wearing surface GG 151 Transition section 152 Section HH 153 Transition section 155 Wall section 156 Wall section 157 Wall section 158 Wall section 159 Transition section 159 Transition section 160 Transition section 161 Transition section 162 Chamber 163 Piston 167' Sealed Surface 168 piston position 168, piston position 169 chamber 170 outer skin 170' outer skin 171 fiber 172 impervious layer 159900.doc -341 201235565 173 compressed medium 173' compressible medium 174 incompressible medium 174' incompressible medium 175 cover 176 piston rod 177 Movable cover 178 Spring 178' Spring 179 Washer 180 Piston rod 181 Cover 182 Projection 183 Spring force member 184 Center axis / fiber 185 Concave wall / convex wall / lining 185a Wall 185b Wall 186 Chamber / channel 186 ' Chamber 187 Wall/Top 188 Skin/Sealed Edge 189 Fabric reinforcement/fabric shaft! 189' Piston.342· 159900.doc 201235565

190 impervious layer 191 cover 192 cover 194 inner wall 195 piston rod 196 mechanical stop 197 stop 198 contact area 198' contact area 199 hole 200 hole 201 hole 202 〇 ring or the like 203 〇 ring or the like Cover 204 205 Incompressible Fluid / Not 205 ' Incompressible Fluid 206 Compressible Fluid / Compressible 206 ' Compressible Fluid / Compressible 207 Wall 208 Modified Piston / Vessel / Add 208, Modified Piston / Vessel 209 Chamber / Separate layer 210 rib/second chamber 159900.doc-343. 201235565 210' Enclosed space 211 Inner portion/contact area 21Γ Contact area 212 External portion 213 Inner portion 214 Mechanical stop/External portion 215 Chamber / Compressible medium 216 Skin/chamber 217 Container/piston rod 217' Container/piston 217" Piston 217" 'Piston 217B" Piston 218 Sliding bearing/container wall 219 Fiber reinforcement/incompressible medium 220 Sealing edge 220, sealed Edge 221 cylinder / wall 222 sheath / piston / elastic material 222 ' piston 222 " piston 223 reinforcement / orifice /Reinforcement member 223' Reinforcement member 224 Skin/piston rod/elastic material 159900.doc • 344· 201235565

225 contact area 225' contact area/contact surface 225" contact surface 225·, 'contact area 225"" contact surface 225"" contact area 225"" contact area 226 impermeable layer 227 reinforcement member 227' Reinforcement member 228 container/piston 228' container/piston 228" piston 229 reinforcement member 229' reinforcement member 230 piston 230' piston 231 chamber 232 compressible medium/compressible fluid 233 incompressible medium/incompressible fluid 234 outer casing 235 sealed edge 236 Center axis 237 Incompressible media 159900.doc •345 - 201235565 240 241 242 243 244 245 246 247 248 248' 249 250 251 252 253 253' 253" 254 255 256 257 258 258' 258" Handle valve / check valve /Piston second enclosed space bushing core pin bearing rod spring piston longitudinal pipe / stop pressure gauge wall / space reinforcement skin contact area contact area contact area support member common component Piston container / piston piston 159900.doc •346· 201235565

260 Schrader valve 261 valve actuator 262 base 263 outlet valve 264 shaft 265 pedal 266 shaft 267 piston rod 268 outlet passage 270 piston 271 piston rod 272 piston rod 273 wall 274 piston 275 non-circular hole 276 spring 277 initial Position 211 'Start position 279 Piston ring 280 Housing 281 Seal 282 Cylinder 283 Inner cylinder 284 Seal 159900.doc •347- 201235565 285 Wall 286 Channel 287 Channel 288 Channel 289 Channel 292 Piston 292' Closed position 293 Bearing 295 Channel 296 Center axis 297 Channel 301 Housing 302 Cylinder 303 Cylinder 304 Channel 305 Channel 306 Channel 307 Channel 308 Opening 309 Widening portion 310 Spring 311 Housing 312 Cover 312' Cover 159900.doc 201235565

313 Contact area 314 Opening 315 Valve actuator 320 Elbow piston rod 321 Piston 322 Piston 323 End of piston rod 324 Bearing 360 Signal 361 Converter 362 Signal 363 Actuator 364 Actuating member 365 Signal 366 Converter 367 Member 368 Inflated configuration 369 Controlling the configuration of the outlet valve 370 Central axis / control valve configuration 371 Piston rod / signal 372 Elastically deformable container 372 ' Container 373 Wedge wall 374 Cylindrical wall / cylinder wall 159900.doc -349- 201235565 375 Chamber 385 Piston 385' piston 400 rod 401 rubber gasket 450 container 470 cylinder 471 channel portion 472 channel portion 473 channel portion 474 channel portion 475 annular portion 475a enlarged wall portion 475b enlarged wall portion / channel portion 476 temporary thread 476a enlarged wall portion 476b wall 476c piston Control member 477 Piston 479 Central axis 480 Channel portion 481 Channel portion 482 First annular portion / Sealing surface 483 Second annular sealing portion 159900.doc • 350 - 201235565

484 Piston 485 Piston Rod 486 Central Axis 487 Enlarged Wall Section 488 Enlarged Wall Section 492 First End / Stopper 493 Clamp 495 Piston Stopper 496 Cylinder Sleeve 497 Spring Buckle 498 Step Surface 499 Cylinder 500 Housing 501 Wedge Conical 502 Opening 503 coupling portion 504 housing 507 channel portion (hole) 508 piston ring 510 coupling portion 511 cylinder wall portion 515 piston ring 520 assembly line housing member 521 assembly line housing member 159900.doc -351 - 201235565 522 valve 523 core pin 529 Piston 530 Coupling Portion 531 Piston Rod 532 Housing 533 Channel Section 534 Channel Section / Radial Drilling 535 Expansion 536 Cylinder 537 Opening 538 Cylinder Wall Section 539 Piston Ring 700 Ring 800 Crankshaft / Configuration / Piston Actuator Configuration 800, configuration 801 U-shaped shaft 802 shaft bearing / fiber 803 shaft bearing 804 anti-gravity 805 piston rod / enclosed space 806 chamber / inflatable piston 807 chamber 808 inner wall 159900.doc -352- 201235565

809 Cover 810 Flexible Wall 811 Reinforcement Member 812 Sliding Cover 813 Enclosed Space 814 Pressure Tank 815 Second Enclosed Space 816 Third Enclosed Space 817 Channel 818 Pump 819 Piston Rod 820 Crankshaft / Pump 821 U-Shaft Rod 821' Centrifugal Pump 822 Fluid/Second Enclosed Space 823 Fluid/Third Enclosed Space 824 Channel 825 Pressure Return Channel 826 Piston Pump 826' Centrifugal Pump 827 Fluid 828 Pressure Return Channel 829 Connected / Channel 830 motor 159900.doc -353 - 201235565 831 crankshaft 832 accumulator (or capacitor storage type) / battery 832A service battery 832B starting battery 832C service battery 833 solar battery / bearing 835 flywheel 836 clutch 837 gear box 838 electric switch 839 Pressure Sensor 840 Pressure Reducing Valve 841 Governor 84Γ Governor 850 Alternator 851 Configuration of Auxiliary Power Source 852 Spindle Rod 860 Chamber 861 Flange/Subchamber 862 Subchamber 863 Subchamber 864 Subchamber 865 Center axis 866 Shaft 159900.doc -354- 201235565

867 Center 868 Piston 869 Piston 870 Piston 871 Piston 872 Piston 873 Piston rod 874 Piston rod 875 Piston rod 876 Piston rod 877 Piston rod 878 Hole 879 Cutting 880 Flange 882 Housing 883 with 884 Pressure distribution center 885 Computer 886 Pressure reducing valve system 887 Signal 888 Signal 889 Pressure Tank / Fluid 890 Cover / Channel / Pressure Source 891 Cover / Signal - 355 - 159900.doc 201235565 892 Piston 893 Conical Chamber Wall 894 Conical Chamber 895 Conical Chamber Wall 896 Cone Shape chamber 897 Chamber wall 898 Expandable piston 899 Conical chamber 901 Reinforcement wall 902 Piston rod 903 Non-movable cover 904 Movable cover 905 Contact area 906 Space 907 Space 908 Space 909 Space 910 Ambient atmosphere 911 Tube 912 Tube 913 tube 914 tube 915 tube 918 tube • 356- 159900.doc 201235565

920 Clearance 921 Fluid 922 Conical chamber inner wall 923 Piston outer wall 924 Piston 960 Round chamber 961 Round subchamber 962 Subchamber 963 Subchamber 964 Subchamber 965 Center axis 966 Shaft 967 Center 968 Piston 968' Position/Piston 968" Position/Piston 970 Hole 980 Center Point 981 Surrounding Line 982 Quadrant 983 Quadrant 984 Surrounding Line 985 Center Point 986 Quadrant -357- 159900.doc 201235565 987 988 1000 1001 1002 1003 1004 1005 1006 1007 1008 1009 1010 1011 1012 1013 1014 1015 1016 1017 1018 1019 1020 1021 Radius line radius line Projection midpoint (center) Center center center axis Center axis movable cover movement direction force center (old) center (new) protruding part (old) Protruding part (new) Moving direction of the movable part Moving the center of the moving cover (old) Center (new) Protruding part (old) Protruding part (new) Reaction direction of the reaction force / center of the elastically deformable wall of the piston The direction of movement of the wall of the piston 159900.doc 201235565

1022 Projection part 1023 Center 1024 Movable cover movement direction 1025 Non-movable cover movement side 1026 Leakage 1027 Projection part 1028 Center 1029 Movable cover movement direction 1030 Piston wall movement direction 1031 Piston wall movement direction 1050 Actuation 1051 Pressure reducing valve 1052 Pressure reducing valve 1053 Actuator 1054 Control 1055 Actuator 1055' Piston chamber combination 1056 Actuator 1056' Control actuator 1057 Pressure reducing valve 1057' Pressure reducing valve 1058 Pressure reducing valve 1058 ' Pressure reducing valve 1059 piston 159900.doc -359- 201235565 1060 chamber 1061 piston chamber combination body / piston 1062 chamber 1063 fluid 1070 enclosed space 1071 〇 ring 1072 second enclosed space 1073 housing 1074 piston chamber Chamber combination 1074, T valve 1075 Pressure reservoir / pressure source 1076 Electrical signal 1077 Electrical / electronic control unit 1078 Signal 1079 Flange 1080 Suspension 1081 with 1082 Regenerative braking system 1090 Enclosed space 1091 Actuator piston 1092 Chamber 1093 System Reference / Cam Wheel Set 1094 System Reference / Cam 1100 Bearing 159900.doc -360- 201235565

1100' bearing 1100" bearing 1101 blind hole 1102 sub L 1103 separator 1104 0 ring 1104' 0 ring 1104" 0 ring 1104", 0 ring 1110 0 ring 1111 actuator center line 1112 bearing holder 1113 Bearing 1114 Bolt 1115 Piston 1116 0 Ring 1117 Wall 1118 Cylinder/Case 1119 Space 1120 Space 1121 Valve Actuator Configuration 1122 Valve Actuator Configuration 1123 0 Ring 1124 Bolt 159900.doc -361 - 201235565 1125 1126 1128 1129 1130 1131 1132 1133 1150 1151 1152 1160 1161 1162 1163 1164 1165 1200 1201 1202 1202, 1203 1204 1205 Bearing Holder Bearing Crankshaft Synchronous Toothed Belt Chamber Top / Crankshaft Pulley Crankshaft Pulley Shaft Actuator Centerline Return Channel Pump channel valve box valve valve valve valve piston pump chamber non-pressure side top first longitudinal position top 159900.doc -362- 201235565

1206 bearing 1207 piston rod / wall 1208 reinforcement 1209 reinforcement 1210 reinforcement 1211 diameter 1212 diameter 1213 diameter 1214 impervious layer 1215 clamp 1216 diameter 1217 piston top / bend 1218 • bend 1219 bend 1220 small curved end 1221 small curved end 1222 Small curved end 1223 Adjustment part 1224 Retainer 1225 Spring ring / clamp 1226 Spring ring 1227 0 ring 1240 Sub L 1241 Hole -363 - 159900.doc 201235565 1242 Sub L 1243 Hole 1244 Central axis 1245 Foam 1400 Slender container piston 1401 chamber 1402 central axis 1403 "start" ellipsoid 1404 final ellipsoid 1405 sphere 1420 immovable cover 1421 gland 1422 recess 1423 movable cover 1424 gland 1425 cover portion 1426 cover portion 1427 wall 1428 reinforcement layer 1429 Cover 1430 Third layer 1431 Third layer 1432 Sub L 1433 Central axis 159900.doc -364- 201235565

1434 Rounding transition section 1435 Rounding transition section 1436 Rounding transition section 1437 Rounding transition section 1440 Reinforcement belt 1441 Reinforcement pattern 1501 Piston 1502 Supporting member 1503 Oval ring 1504 Watertight sheet 1504' Watertight sheet 1505 Bubble 1505' Foam 1506 Chamber 1507 Piston rod 1508 Suspension 1509 Spring 1509' Spring 1510 Shaft 1511 Horizontal spring 1511' Horizontal spring 1512 Layer 1513 No reinforcement layer 1514 Refill • 365 159900.doc 201235565 1515 1516 Small curved flat surface 1517 Wall 1518 Central axis 1519 End 1520 Boundary 1521 Notch 1522 Spiral reinforcement 1523 Spiral reinforcement 1524 Spiral reinforcement 1525 Reinforcement part 1530 Piston 1531 Flexible impervious sheet 1533 Top layer 1534 Bottom 1600 Tank 1601 h2 1603 Channel/External 1604 External 1605 Channel 1606 h2 Fuel Cell 1607 Electrical Connection / Fuel Cell 1608 Check Valve 1609 Electrical Connection 159900.doc -366- 201235565 1610 Electrical Connection 1611 Electrical Connection 1612 Tank 1613 Water/Wire 1614 Channel/Output Electrical Connection 1615 aisle 1616 slot/bypass 1618 check valve 1620 combustion motor 1621 spindle rod 1622 outlet/channel 1623 electric starter motor / spindle rod / into 1624 alternator / crank shaft 1625 electrical connection / piston pump 1626 piston rod 1627 rotary pump 1628 shaft 1629 Wire 1630 Capacitor 1631 Battery 1632 Electrical Wire 1633 Channel 1634 Wire 1640 Channel 159900.doc -367- 201235565 1641 Wire 1642 Wire 1700 Actuator Piston 1701 Chamber 1702 Center Axis 1703 Piston 1704 Piston Rod 1705 Second Vertical / Second Circle Shape position 1706 first longitudinal/first circular position 1707 enclosed space 1708 pump portion 1709 actuator piston 1711 actuator piston 1713 position 1714 second longitudinal position 1716 pump stroke 1720 sub-chamber 1721 around central axis 1722 Actuator piston 1723 fluid 1724 pump 1725 piston 1726 piston rod 1727 chamber 159900.doc -368- 201235565 1728 cam wheel set 1729 cam surface 1730 second longitudinal position 1731 position 1732 actuator piston 1733 actuator piston 1734 cam surface 1735 End point 1736 actuator piston 1737 Actuator piston 1738 Cam wheel set 1739 Inclined cam surface 1740 Arrow/wall 1741 Hose 1742 Wall 1743 Fluid or fluid mixture 1744 Chamber 1745 Outlet 1746 Enclosed space 1747 Actuator piston 1749 Chamber 1750 Center axis Line 1751 Wheel 1752 Shaft 159900.doc -369- 201235565 1753 Roller bearing 1754 Subchamber 1755 Subchamber 1756 Subchamber 1757 Subchamber 1758 Piston 1759 Piston 1760 Piston 1761 Piston 1761' Dotted 1762 Piston 1763 Pump section 1764 Pump section 1765 Pump section 1766 Pump section 1767 Pump section 1768 Piston rod 1769 Piston rod 1770 Piston rod 1771 Piston rod 1772 Piston rod 1773 Cam wheel set 1774 Cam wheel set 1775 Cam wheel set

159900.doc -370- 201235565

1776 Cam wheel set 1777 Cam wheel set 1778 Camshaft 1779 Lower part 1780 Lower part 1781 Lower part 1782 Lower part 1785 Chamber wall 1786 Pipe 1787 Pipe 1788 Pipe 1789 Pipe 1790 Pipe 1791 Pipe 1792 Pipe 1793 Pipe 1794 Pipe 1795 Pipe 1796 Pipe 1797 Pipe 2000 Second longitudinal position 2001 First longitudinal position 2004 Valve position 2005 arrow 159900.doc •371- 201235565 2007 Position 2009 arrow 2010 arrow 2011 arrow 2020 entrance / exit configuration / arrow 2021 arrow 2022 arrow 2023 arrow 2024 Piston wall 2025 Position 2026 Position 2027 Shape 2028 Shape and size 5000 Main frame a Distance a' Distance a, Distance a" Distance b Distance b. Distance b' Distance c, Distance di Distance 159900.doc -372 - 201235565

h South degree I stage II stage III stage ss pitch ss' pitch ss" stitch length ss", stitch length tt stitch length tt' stitch length tt" stitch length tt'" stitch length X part X position X' part x&quot Distance XY hinge Y part Y, part z part z. Part Zl distance z2 distance z3 distance 159900.doc -373 201235565 zz αβ hinge angle angle

159900.doc -374-

Claims (1)

201235565 VII. Patent application scope: 1. A piston chamber assembly, including a chamber (162, 186, 231) delimited by the inner chamber walls (10), 185, 238, and contained in the chamber An internal-actuator piston movable relative to the chamber wall at least between a first longitudinal position of the chamber and a second longitudinal position, the chamber having a plurality of a section having at the first longitudinal position and the second longitudinal position; p being intercepted from the area and different circumferential lengths, and wherein the intermediate longitudinal position between the first longitudinal position and the second longitudinal position The position has at least substantially continuous different cross-sectional area and circumferential length, the cross-sectional area at the second longitudinal position and the circumferential length being less than the cross-sectional area at the first longitudinal position and the circumferential length, the actuator piston Containing a container (2〇8, 2〇8, 217, 217, 228, 22b 258 '258', 450, 450'), the container is elastically deformable, thereby providing different cross-sectional areas and circumferences of the piston Length to adjust the piston Adapting to the different cross-sectional areas of the chamber during the relative movement of the piston between the first longitudinal position and the second longitudinal position through the intermediate longitudinal positions of the chamber and such Depending on the circumferential length, the actuator piston is produced to have the container (2〇8, 2〇8, 217, 217, 228, 228', 258, 258, 450, 450·) without stress and a production size in a non-deformed state, the circumferential length of the piston being approximately equal to the circumferential length of the chamber (162, 186, 231) at the second longitudinal position in the unstressed and undeformed state, The container may expand from its production size in one of the lateral directions of the phase of the chamber 159900.doc 201235565, thereby providing the piston from the second longitudinal position to the first longitudinal position. The piston during the phase shifting movement expands from one of its production sizes, the barn (208, 208, 217, ? 1 〇 W 217 , 228 , 228 , 258 , 258 ' , 450 , 450 ') Elastically deformable for the actuator to live The different cross-sectional area and circumferential length, the piston chamber combination is characterized by the fact that the combination comprises a white female & ssaL A 3 for introducing fluid into the container from a position outside the remote valley Thereby, a member capable of squeezing the stagnation of the stalk and thereby expanding the container and displacing the container between the longitudinal position of the chamber and the first longitudinal position. 2. An inner chamber wall (156, 231) and contained in the piston chamber assembly, comprising a chamber (162, 186, cavity to inner actuator) delimited by 185, 23 8) a piston that is reciprocally movable relative to the chamber wall at least between a first longitudinal position of the chamber and a second longitudinal position, the chamber having a plurality of sections, the sections being The first longitudinal position and the second longitudinal position have a cross-sectional area and a length of the circumference, and have at least an intermediate longitudinal position between the first longitudinal direction and the second longitudinal position of the book The enamel has 4 different ❹ areas and a circumferential length, the cross-sectional area at the second longitudinal position and the circumferential length being smaller than the cross-sectional area at the first longitudinal position and the circumferential length, the actuator piston comprising a container (2〇8, 2〇8, 217, 217, 159900.doc 201235565 228, 228', 258, 258', 450, 450') 'The container is elastically deformable' thereby providing different cross-sectional areas of the piston And the length of the circumference, thereby adapting the piston to the piston The relative movement between the first longitudinal position and the second longitudinal position through the intermediate longitudinal positions of the chamber accommodates different cross-sectional areas of the chamber and the different circumferential lengths, the actuator The piston is produced to have one of the containers (2〇8, 208, 217, 217| '228, 228|, 258 '258', 45〇, 45〇|) in its unstressed and non-deformed state a production size in which the circumferential length of the piston is approximately equal to the circumferential length of the chamber (162, 186, 231) at the second longitudinal position, the container being contiguous with respect to The longitudinal direction of the chamber is expanded from its production dimension in one of the lateral directions, thereby providing the piston during the relative movement of the actuator piston from the second longitudinal position to the first longitudinal position One of the production sizes expands, and the barn (208, 208', 217, 217, 228, 228, 258, Lu 258, 450, 450,) is elastically deformable to provide the difference in the actuator piston Cross-sectional area and circumferential length, [including one The enclosed space, the piston chamber combination is characterized by the fact that the combination includes a change in the container from the position outside the container [the enclosed space in communication with the actuator piston] a member, thereby enabling the container to be pressurized, and thereby expanding the container and displacing the container between the second longitudinal position of the chamber and the first longitudinal position. 159900.doc 201235565 3. The piston chamber assembly of claim 1 or 2 wherein the actuator piston inside or outside the chamber is sealingly movable relative to the chamber wall. 4. The piston chamber assembly of claim 1, 2 or 3, wherein a portion of the chamber positioned adjacent to the actuator piston is in communication with each other via a passage or via the atmosphere. 5. The piston chamber assembly of any of claims 1 to 4, wherein the chamber is elongate. 6. The piston chamber assembly of any of claims 1 to 4, wherein the chamber is circular. 7. The piston chamber assembly of claim 6, wherein the chamber is formed around a central axis. 8. The piston chamber assembly of claims 1 to 7, wherein the actuator piston does not engage the wall of the chamber. 9. The piston chamber assembly of claim 8, wherein the piston moves from a first longitudinal position to a second longitudinal position. 10. The piston chamber assembly of claims 1 to 7, wherein a portion of the length of the wall of the chamber is parallel to the central axis of the chamber. 11. The piston chamber assembly of claim 10, wherein the wall of the chamber is located at one of the strokes of one of the actuator pistons. 12. As requested! a piston chamber assembly of up to 7, wherein the container (2〇8, 208', 217, 217', 228, 228', 258, 258', 450, 450') comprises a deformable material (205, 206) . 13. The piston chamber assembly of claim 12, wherein the deformable material (205, 206) is a fluid or a mixture of fluids such as water, steam 159900.doc 201235565 and/or gas, or a foam . 14. The piston chamber assembly of claim 12 or 13, wherein in a section through the longitudinal direction, the container has when the container is at the first longitudinal position of the chamber (186, 231) a first shape that is different from a second shape of the container when the container is at the second longitudinal position of the chamber. 15. The piston chamber assembly of claim 14, wherein at least a portion of the deformable material (2〇6) is compressible, and wherein the first shape has an area greater than the *-area of the first shape . 16. The piston chamber combination of claim 14, wherein the deformable material (2〇6) is at least substantially incompressible. 17. The piston chamber assembly of claims 1 to 7, wherein the container is inflated. 18_ The piston chamber assembly of claims 1 to 7, wherein the container (2〇8, 208', 217, 217', 228, 228, 258, 258, 450, 450,) additionally comprises The deformable container communicates with one of the enclosed spaces (21〇, 243). 19. The piston chamber assembly of claim 18, wherein introducing fluid into the container from a location external to the container is via a first enclosed space in communication with the enclosed space. 20. The piston chamber combination of claims 1, 3 to 7, further comprising means for removing fluid from the container to a position external to the piston thereby enabling contraction of the container. 21. The piston chamber assembly of claim 20, wherein the removal of the fluid is performed by a second enclosed space in communication with the enclosed space via 159900.doc 201235565. 22. The piston chamber assembly of claim 2 to 7 or 18, wherein the enclosing space of the members and the S plug is communicated by: changing the volume of the enclosed space, increasing the volume The volume and thereby the actuator piston is reduced, thereby enabling the contraction of the container. 23. The piston chamber assembly of claim 22, wherein the piston is movable relative to the chamber to the wall from at least a first longitudinal position of the chamber to a second longitudinal position. 24. The piston chamber assembly of claims 1 to 7, wherein the wall of the container, 208, 217, 217', 228, 228, 258, 258', 450, 450,) comprises a reinforcement layer. The piston chamber assembly of any of the preceding claims, wherein in the longitudinal direction, substantially just above the midpoint of the cross-section of the elastically deformable wall of the container, in a second longitudinal direction At the side of the location, the cross-section of the contact surface of the container with the wall of the chamber cuts the central axis of the container. 26. The piston chamber assembly of claim 25, wherein in the longitudinal direction, substantially outside the midpoint of the section of the elastically deformable wall of the container, at a side of the second longitudinal position, The section of the container and the contact surface of the wall of the chamber cuts the central axis of the container. 27. The piston chamber assembly of claim 12, 17, 2 or 22 wherein the actuator piston comprises a piston rod that includes the enclosed space. 28. The piston chamber assembly of claim 26, wherein the piston rod includes an engagement member external to the chamber. 159900.doc 201235565 29. The piston chamber assembly of claim 28, further comprising a crank adapted to shift motion of the piston between the second longitudinal position and the first longitudinal position of the chamber Rotate one of the cranks. 30. The piston chamber assembly of claim 28, wherein the crank rotates it into a movement of the piston from the first longitudinal position of the piston to the second longitudinal position. 31. The piston chamber assembly of claim 19, 21 or 28, wherein the crank comprises the first enclosed space and the second enclosed space. 32. The combination of claim 1 to 7, wherein the cross-sectional area of the chamber at the second longitudinal position thereof is 95% of the cross-sectional area of the chamber at the first longitudinal position thereof to 15%. 33. The combination of claim 丨7, wherein the cross-sectional area of the chamber at the second longitudinal position thereof is about 50% of the cross-sectional area of the chamber at the first longitudinal position thereof. 34. The combination of claim 丨 to 7, wherein the cross-sectional area of the chamber at the second longitudinal position thereof is about 5% of the cross-sectional area of the chamber at the first longitudinal position thereof . 35. The combination of claim 丨 to 6, wherein the chamber comprises a convex shaped wall of a longitudinal section proximate to a first longitudinal position, the portions being divided by a common boundary, two immediately following A distance between the common boundaries defines a height of the walls of the longitudinal section, the height being increased by an overvoltage rating with respect to one of the actuator pistons relative to the pressure in the chamber And decreasing, the lateral length of the common boundary of the sections is determined by the maximum working force of the actuator piston, which is selected by 159900.doc 201235565 to be constant for the common boundaries. 36. The combination of claims 1 to 6, wherein the chamber comprises a convex shaped wall of a longitudinal section proximate to a first longitudinal position, the portions being separated from one another by a common boundary, two immediately following Between the common boundaries - the height of the walls of the longitudinal section of the distance boundary m, the heights decreasing in the direction from one of the first longitudinal position to a second longitudinal position, the transverse direction of the cross-section (four) The length is determined by the maximum working force of the actuator piston 'this maximum working force is selected to be ambiguous for the common boundaries. 37. The combination of claim 35 or 36, wherein the chamber further comprises a wall parallel to the central axis of the chamber. 38. The combination of claim 35 to 37, wherein the chamber is in a (four) 7 匕 3 recess 39. The combination of claim 38, wherein the chamber further comprises between the convex shaped wall and the parallel wall A transition section wherein the transition section can comprise a concave shaped wall. 40. A shock absorber comprising: a combination of any one of δ-Claim 1 to 39, a member for engaging the piston from a position outside the chamber, wherein the engaging members have an outer portion a position and an internal position at which the piston is at the first longitudinal position of the chamber, at which the piston is at the second longitudinal position. 41. The shock absorber of claim 4, further comprising a confined space in communication with the container. 159900.doc 201235565 42 _ The shock absorber product 0 of claim 41, wherein the enclosed space has a variable volume 43. The shock absorber product 0 of claim 41 wherein the enclosed space has a constant volume 44. The shock absorber of claim 41, wherein the enclosure mi is adjustable. 45. For shock absorbers in claims 41 to 44, where T is required. The plurality of states and the enclosed space form a cavity containing a fluid that at least substantially dissolves the seal, and when the piston moves from the first longitudinal position of the chamber to the second longitudinal position of the main The fluid is compressed. 46. A pump for pumping a fluid, the fruit comprising: a combination of claims 1 to 39, one of the chambers for engaging a first piston member from a position outside the chamber, 47. One of the valve members is coupled to the first chamber and includes a valve member coupled to one of the fluid outlets of the second chamber. A pump for pumping a fluid, the pump comprising: a combination of items 1 to 39, for engaging a chamber member, a fluid inlet, and a piston from a position outside the chamber Connected to the chamber and includes a fluid inlet of one of the valve members and a fluid outlet connected to one of the chambers. 48. The pump of claim 46 or 47, wherein the engagement members have an outer position and an inner position at which the piston is at the first longitudinal position of the chamber, at the inner position The piston is in the second longitudinal position of the chamber of the 159900.doc -9-201235565 β 49. 50. 51. 52. 53. 54. 55. If the result of claim 46 or 47 'where the indulgence The member has an outer position and an inner position at which the piston is at the second longitudinal position of the chamber 'at which the piston is at the first longitudinal position of the chamber. Kind of. The use of the piston chamber assembly of the first or second embodiment in the motor, in particular in an automotive motor. A motor characterized by the fact that the motor comprises a piston chamber combination as claimed in claim 1 attached thereto. A motor ' is characterized by the fact that the motor comprises a piston chamber combination as claimed in claim 2 attached thereto. (d) The motor of claim 3 to 39, 46 to 51, wherein the crankshaft includes a first enclosed space, communicated with an external pressure source at one end, and at the other end with the actuator piston The enclosed space is connected. The motor of claim 53 wherein the crank shaft includes a third enclosed space, communicating with the enclosed space of the actuator piston, and communicating with a repressurizing pump at the other end. The pressure pump is in communication with an electric motor that derives its energy from a battery, and is charged by an energy source such as solar energy, or a fuel cell such as a fuel cell of one or two, or an alternator in communication with the spindle shaft. Battery. The motor of claim 54, wherein the alternator is in communication with an axis A of an auxiliary power source, such as a combustion motor, the combustion motor is burned from the electrolysis of the conductive water and the enthalpy in the air, The water comes from a can that can be filled externally. The motor of claim 54, wherein the pump mentioned last time is in communication with a shaft of an auxiliary power source, such as a combustion motor, which is burned from electrolysis of conductive water. % and the 〇 2 in the air, the water comes from a tank that can be filled externally. 57. The motor of claim 53 wherein the communication between the source of pressure and the enclosed space of the actuator piston occurs during a partial rotation of each crankshaft. 58. The motor of claim 54, wherein the communication between the enclosed space of the piston and the re-pressurization cascade occurs during a partial rotation of each crankshaft. 59. The motor of claims 57 and 58, wherein the communications are separated from each other in time. 60. The motor of claim 59 wherein the communication is performed by __τ阙. The valve is controlled by a computer in electrical communication with the spindle of the motor. 61. The motor of claim 60, wherein the pressure and/or volume of the supply passage to the τ valve is controlled by a pressure reducing valve that is controlled by a governor. 62. The motor of claim 61, wherein the pressure reducing valve is in communication with a pressure reservoir, the pressure reservoir being in cascade communication with a repressurizing pump, at least one of the repressurizing pump cascades and [the crank The shaft is connected via another crank shaft, and the at least one pump is in communication with an electric motor, the motor obtaining its self-b quantity from a battery, by one energy source such as solar energy, or such as a fuel cell A fuel cell, or one of the main shafts connected to the main shaft, is used to charge the battery. 63. The motor of claim 62, wherein the alternator is in communication with a shaft of an auxiliary power source, such as a combustion motor, the combustion motor is combusted from the conductive water The electrolysis of Ha and the air Ο" the water comes from a tank that can be externally filled. The motor of claim 63, wherein the pump of the last friend is connected to a shaft of an auxiliary power source, the auxiliary power source For example, a combustion motor that burns Ha from the electrolysis of conductive water and A in the air from a tank that can be externally filled. The motors of claims 62 to 64, wherein the pumps are piston pumps Or a rotary pump, wherein the motor of the items 2 to 39, 46 to 51, wherein the enclosed space, the second enclosed space and the third enclosed space form a closed cavity. The motor of 66, wherein the pressure in the cavity is controlled by a piston chamber combination, the piston chamber combination is in communication with a two-way piston chamber combination. Pressure valve to control, the pressure reducing valve is borrowed A governor for controlling the motor of claim 67, wherein the two-way actuator piston chamber assembly is in communication with a pressure tank that is in cascade communication with a repressurizing pump, the repressurizing pump cascade At least one of the pumps and [the crankshaft, via another crankshaft] the main shaft is in communication with, and at least, the pump is in communication with an electric motor that derives its energy from an f-cell, such as by solar energy Charging the moon, and/or by charging the battery from a battery such as a fuel cell, 159900.doc • 12- 201235565, and/or charging with an alternator connected to the spindle. 69. The motor of claim 68, wherein the last mentioned turn is in direct communication with the axis # of the auxiliary power source, such as a combustion motor, the combustion motor burning H2 obtained from electrolysis of conductive water And from the air 〇 2 'the water comes from a tank that can be filled and, if necessary, from a conductive member storage tank. 70. The motor of the items 67 to 69, wherein the pressure in the cavity is additionally borrowed • by the force The slot is connected to one of the piston chamber assemblies. 71. The motor of claim 65, wherein the pressure in the closed cavity of a piston is through a piston chamber in communication with the spindle shaft of the motor Controlling the electronic control by means of a computer. 72. The motor of claim 65, wherein the pressure in the closed cavity of a piston is via a cam wheel set and the spindle of the motor A piston chamber connected to the rod is connected to the coupling body, and the cam wheel set is in communication with a cam shaft. 73. A motor such as a 61- or 7-inch motor, which is a piston fruit or a rotary pump. 74. The motor of claim 1 to 4, 6 to 73, wherein a piston rotates about the central axis of the chamber. The motor of claims 1 to 4, 6 to 73, wherein the chamber is rotating. 76. The motor of claim 74 and 75, wherein the piston and the chamber are rotating. 77. The motor of claim 74 to 76, wherein the actuator piston chamber assembly 159900.doc -13 - 201235565 78. 79. 80. comprises at least two sub-chambers, the at least two sub-chambers The sub-chambers including the actuator pistons are continuously positioned relative to each other whereby the first circular position of the sub-chamber is adjacent to a second circular position of one of the other adjacent sub-chambers. The motor of claim 77 wherein the subchambers are identical. The motor of claim 78, wherein each of the subchambers includes an actuator piston, the pistons are identical, wherein each piston is located at a different circular position from each other in each of the subchambers. The motor of claim 74 to 79 wherein the shape of the piston does not change therebetween. 80. The motor of claim 62 or 68, wherein the pressure channel is pressurized by an external pressure source through an insertable connection. 81. The motor of claim 54, 62 or 68, wherein the battery is charged via an externally powered source via a pluggable connection. 82. A piston chamber to a combination comprising an elongated chamber (7〇) bounded by an inner chamber wall (71, 73 75) and contained in the chamber - a piston member (76, 76', 163), the piston member (76, 76, 163) is sealingly movable relative to the chamber at least between a first longitudinal position and a second longitudinal position of the chamber, the cavity having a plurality of The section 'the sections have different cross-sectional areas at the first longitudinal position and the first longitudinal position of the chamber, and an intermediate longitudinal position between the first longitudinal position and the second longitudinal position of the chamber Having at least substantially continuous different cross-sectional areas, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position, 159900.doc -14 - 201235565 the piston member is designed to adapt itself and The male member and the sealing member are armored to the piston member from the first thousand of the chamber to make the "relative material" through the intermediate longitudinal position to the second longitudinal position. Adapting the cavity to the different cross-sectional areas The piston chamber combination is characterized by the fact that the piston member (76, 76, 163, 189, swim) comprises: a plurality of at least substantially rigid support members (81, 82, _ rotatably Fastened to - common parts (6, 23, 45, 18 〇), The branch members are disposed in the elastically deformable member (79). The cough elastically deformable member (79) is supported by the support members for abutting against the inner wall of the chamber (70) (71, 73) Sealed, i55, I%, π, 158), the support members may be 10° and 40 with respect to the longitudinal axis (19) of the chamber (7〇). Rotating between, 6 Hai 4 standard components (8 1, 82, 184) are bendable. 83. The piston chamber assembly of claim 82, wherein the piston inside or outside the chamber is sealingly movable relative to the chamber wall. 84. The piston chamber assembly of claim 82, wherein the support members have a predetermined bending force. 85. The piston chamber assembly of claim 82, wherein the support members (81, 82, 184) are rotatable to be at least substantially parallel to the longitudinal axis (19). 86. The piston chamber assembly of claim 82, wherein the elastically deformable member (79) is made of a polyamine phthalate foam. 87. The piston assembly of claim 86, wherein the pu foam comprises a polyurethane foam and a polyurethane foam. 159900.doc • 15-201235565 88. The piston chamber assembly of claim 87, wherein the polyurethane foam comprises a majority of the polyamine phthalate memory foam and a small portion of the polyamine A carboxylic acid vinegar foam. 89. The piston chamber assembly of claims 86 to 88, wherein the polyamine phthalate foam has a flexible, water impermeable layer. 90. The piston chamber assembly of claim 89, wherein the water impermeable layer has an unstressed production size, the circumference of the unstressed production size being substantially the chamber at a second longitudinal or circular position The circumference of the wall. 91. The piston chamber assembly of claim 82 or 85, wherein the common component is attached to a crankshaft. 92. The piston chamber assembly of claim 82 or 87, wherein the common component is attached to a piston chamber combination, the piston chamber assembly being an external two-way actuator. 93. A piston chamber assembly comprising an elongated chamber (7〇) delimited by an inner chamber wall (71' 73, 75) and comprising a piston member in the chamber ( 76, 76', 163), the piston member (76, 76, 163) is sealingly movable relative to the chamber at least between a first longitudinal position of the chamber and a second longitudinal position, the chamber having a plurality of sections having different cross-sectional areas at the first longitudinal position and the second longitudinal position of the chamber and intermediate between the first longitudinal position and the second longitudinal position of the chamber The longitudinal position has at least substantially continuous different cross-sectional areas, the cross-sectional area at the first longitudinal position being greater than the cross-sectional area at the second longitudinal position, 159900.doc •16-201235565 The piston member is designed to be adapted The piston member passes from the relative movement period position of the second longitudinal position of the chamber to the different cross-sectional areas of the first chamber, and the sealing member passes through the intermediate longitudinal position in a longitudinal position Adapt to the cavity to live The chamber combination is characterized by the fact that the piston member (49, 49) comprises: a plurality of at least substantially rigid support members (43) rotatably secured to a piston by a shaft (44) Rod (45), The branch members are supported by a sealing member (4) which is supported by a spring 42 for abutting against the inner wall of the chamber (7, 73, 75, 155, 156, 157). , 158) sealed, the support members being at 01 with respect to the longitudinal axis (19) of the chamber (70). With p2. Rotating between, a flexible impervious film (sheet) (40) is mounted in the sealing member (ring) (41) and perpendicular to the central axis (19) of the chamber (1) Positioning, the film (flexible water-impermeable sheet) comprises a reinforcing layer, _ the supporting members (members), the sealing member (ring ring), the flexible water-impermeable film (sheet) and the (lying) The springs are vulcanized on each other. 94. The piston chamber assembly of claim 93, wherein the branch members (81, 82, 184) (members) are rotatable to be at least substantially parallel to the longitudinal axis (19). 95. The piston chamber assembly of claim 93, wherein the flexible reinforcement layer (sheet) comprises a spiral reinforcement. 96. The piston chamber assembly of claim 93, wherein the reinforcement layer (sheet) package 159900.doc -17-201235565 includes a concentric stiffener positioned about the central axis of the chamber. 97. The piston chamber assembly of claim 93, wherein the flexible, water impermeable membrane (sheet) has a greater than 9 turns with the central axis of the chamber. The degree of angle. 98. The piston chamber assembly of claim 97, wherein the flexible, water impermeable membrane (sheet) is mounted to the piston rod. 99. The piston chamber assembly of claim 97, wherein the flexible, water impermeable membrane (sheet) is vulcanized on the piston rod. 100. The piston chamber assembly of claim 82 or 93, wherein the common component is contained in a piston chamber combination. 101. The flexible watertight film of #, in the piston chamber assembly of claim 93, is supported by a foam. 102. The piston chamber assembly of claim 101, wherein the foaming system is reinforced by a rigid member, the (four) component being rotatably secured to the piston rod. 103. A piston chamber assembly comprising a chamber (162, 186, 231) delimited by an inner chamber wall ο%, 185, 238) and contained within the chamber - a piston The member 'the piston member is reciprocally movable relative to the chamber wall at least between a first longitudinal position of the chamber and a second longitudinal position, the chamber having a plurality of sections, the sections being at the a longitudinal position and the second longitudinal position having different cross-sectional areas and different circumferential lengths, and intermediate between the first longitudinal position and the second longitudinal position: having at least substantially continuous different cross-sectional areas at the position and Circumference length I59900.doc -18- 201235565 degrees 'The cross-sectional area at the second longitudinal position and the circumferential length being smaller than the cross-sectional area at the first longitudinal position and the circumferential length, the piston member comprising a container (2〇 8, 208, 217, 217·, 228, 228', 25 8, 258', 450, 450'), the container is elastically deformable, thereby providing different cross-sectional areas and circumferential lengths of the piston, thereby adapting the piston Make it in the piston The relative movement between the longitudinal position and the second longitudinal position through the intermediate longitudinal positions of the chamber accommodates the different cross-sectional areas of the chamber and the different circumferential lengths, the piston member being produced a production size of the container (2〇8, 2〇8, 217, 2W, 228, 228', 258, 258', 450, 450·) in its unstressed and undeformed state, In the stressed and undeformed state, the circumferential length of the piston is approximately equal to the circumferential length of the chamber (162, 186, 231) at the second longitudinal position, and the container may be in a longitudinal direction relative to the chamber Relating from its production size in one of the lateral directions, thereby providing one of the production sizes of the piston during the relative movement of the actuator piston from the second longitudinal position to the first longitudinal position Expanded, the container (208, 208, 217, 217, 228, 228, 258, 258, 450, 450') is elastically deformable to provide different cross-sectional areas and circumferential lengths of the actuator piston, the piston The chamber combination is characterized by The fact that the piston member (92, 92, 146, 146., ι68, 168ι, 2〇8, 208', 222, 222', 222") comprises an elastically deformable container, the 159900.doc -19- 201235565 The elastically deformable container comprises a deformable material (103, 103', 124, 124', 136, 137, 173, 173', 174, 174, 205, 205, 206, 206, 215, 215', 219, 219," 104. The piston chamber assembly of claim 1, wherein the piston in the chamber is sealingly movable relative to the chamber wall. 105. The piston chamber assembly of claim 1 to 3 or 104, wherein the deformable material (103, 103', 124, 124', 136, 137, 173, 173', 174, 174', 205, 205 , 206, 206, 215, 215, '219, 2 19') is a fluid or a mixture of fluids such as water, steam and/or gas 'or a foam. 106. The piston chamber assembly of claim 105, wherein the deformable material (124, 124', 136, 174, 174', 205, 205', 219, 219) is at least substantially incompressible. 107. The piston chamber assembly of claim 105 or 106, wherein the container is inflated. 108. The piston chamber assembly of claim ι〇3 or 1-4, wherein the combination further comprises a piston rod, the wall of the container comprising a flexible material on the piston rod Vulcanized. 109. The piston chamber assembly of claim ι8, wherein the wall of the container comprises at least one layer having a stiffener positioned closest to the piston rod and vulcanized on the piston bore, and There is a layer of a stiffener that is vulcanized on the layer with a stiffener. 110. The piston chamber assembly of claim 1-9 wherein the reinforcing strip is placed parallel to the central axis of the piston and is bendable. (1) The piston chamber assembly of claim U) 7 or 1 G8, wherein the wall of the container comprises two reinforcing layers that compete for a minimum of one another of the layers of the layers The angles intersect. The piston chamber assembly of any of the preceding claims, wherein the length of a container-type piston is enlarged such that the shape of the body piston maintains its shape at a second longitudinal position, but is located at a It is not the size of a vertical position. (1) The motor of claim 51, wherein one of the pressure regulators connected to the pressure tank and the third enclosure type is in communication with a governor. 114. The motor of claim 51, further comprising two cylinders, wherein the third enclosed space of each cylinder is in communication with each other via a connection of two sub-cranks, the two sub-cranks being included in the motor In the crank pumping, the second enclosure spaces of each alpha cylinder communicate with each other outside the crankshaft. (Fig. 19) 115. The motor of the present invention, i.e., the crankshaft configuration of the two piston chamber assemblies, is positioned 18G to each other. . (FIG. 19) I The motor of claim 114 and 115, further comprising two or more steams, wherein the second enclosed space is connected via the connection of the sub-curves of the existing two cylinders, wherein The second enclosed space of the sub-crankshaft of the cylinder. (FIG. 19) 117. The motor of claim 52, further comprising two cylinders, wherein the second longitudinal position of one cylinder is at the same geometrical level as the first longitudinal position of a second cylinder, two actuators The pistons are in communication with each other via a crankshaft. The crankshaft contains two connected sub-crankshafts, each actuator 159900.doc • 2U 201235565 piston a sub-crankshaft, where # ^ ^ ^ ^ ^ ^ , this 荨 actuator These connections of the piston are thus 〗8〇 by the 疋 position. . (图图) 118. If the horse of claim 117 is far away, it is further included in the piston of the cylinders for the actuation of the cylinders for the two cylinders.夕分 ["The enclosed space and the other of the actuator pistons are connected to form a pump, which is the same as the Λ 轴 shaft, 6 hai The enclosed spaces are connected to each other at the point of connection of the sub-crankshafts. (Fig. 17) The motor of 119 == 118 'the step of entering the valve' is open to the valve. The VT pump and the second circumference The connection between the enclosed space or the third enclosed space, and each connection of the It-nail two-way At connection has a check valve or check valve power t» 'The valves are by Yu Xuan The pressure of the pβ pump and/or by the tappet control '§/the taper rod is connected to a camshaft remotely ^ 褙 glaze, which is in communication with the spindle shaft of an auxiliary motor. (Fig. 17) The motor of items 117 to 119, wherein the step further comprises two or more steams 2, wherein each of the added cylinders is connected to the existing sub-crankshafts The motorized shaft of the sub-cranked shaft is connected to each other (Fig. 17) 121. The motor of claim 52, which further comprises two cylinders, wherein the first longitudinal position of the cylinder The first longitudinal position of the two cylinders is at the same geometrical level, and the two actuator pistons are in communication with each other via a crankshaft. The crankshaft includes two connected sub-crankshafts, each actuator: a plug-a crankshaft. The connections of the actuator pistons are then positioned to each other. (Fig. i8) 122. The request item 121$$, the motor to be removed, further comprising 159900.doc for the cylinders • 22- 201235565 each of the ESVT pumps, wherein the w seeks for the two steam red via the move: the live one of the enclosed space and the other of the actuator pistons The enclosed space of the enclosed space is combined into a pump, and the enclosed space is included in the crankshaft, and the enclosed space is connected to each other at a connection point of the special crankshaft. 123. Who is the motor of claim 122, who is half A heart #Μ# includes valves that open and close the connection between the ESVT pump and the second enclosed empty work space or the third enclosed space' and each connection and ^ Reverse pressing has a check valve or check valve function b 'the valves are controlled by the pressure of the VT 汞 mercury of the ESVT pump and/or by a tappet that is connected to a camshaft The π camshaft communicates with the spindle shaft of an auxiliary motor (Fig. 18). As described in the motors of claims 121 to 123, the step further includes two or more cylinders, each of which is added (lightly connected). The enclosed space is separated by a filler associated with the connection of the existing sub-red # # 寺 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且 且Return the stroke at the same time. (Fig. 18) (2) The motor of claim 52, wherein the step further comprises two steams*, wherein the: the joints are at 180 to each other. a position of the chamber having a same geometric position with respect to its longitudinal position and second longitudinal position 18) 126. The motor of claim 114 to 125, wherein the piston chamber assembly is for a sub-crank Each of the enclosed spaces in the shaft, each of the piston chamber assemblies changes the speed/pressure in a cylinder, and is in communication with each other via a two-way actuator (four) A road actuator moves the piston rod of each of the 159900.doc • 23· 201235565 piston chamber assemblies and is in communication with the external governor. 127. The motor of claim 114 to 126, wherein the piston rods of the pumps are powered by the fluid in the pistons by a two-way actuator piston powered by a battery. The battery is powered by an auxiliary power source. 128. The motor of claim 114 to 127, wherein the piston rods of the pumps pressurize the fluid in the pistons by one of the two-way actuator pistons powered by a battery, The battery is powered by an auxiliary power source. 129. The motor of claim 114, wherein the piston rods of the pumps pressurize the fluid in the pistons by a two-way actuator piston powered by a crankshaft. Powered by the auxiliary power source, the crankshaft is powered. No. The motor of claim 114 to 129, wherein the piston rods of the pistons pressurize the fluid in the pistons by a two-way actuator piston powered by a camshaft Powered, the camshaft is powered by an auxiliary power source. (3) The motor of claim 52, comprising: a circular chamber and an actuator piston, wherein the piston rod is sealingly movable in a cylinder, and the enclosed space and pressure inside the piston rod The controller is connected to a governor positioned at the distal end, and the enclosed air = small is adjusted by a pump having a - conical chamber, the end of the conical chamber being at the cam Running above the contour, the cam profile is driven by a 159900.doc •24·201235565 auxiliary electric motor that rotates the cam and rotates about the same main motor shaft independently of the motor. I32. The motor of claim 1, wherein the actuator piston has a wall, a stiffener mounted on the movable end that is slidable on the piston rod. The movable end can be sealed on the end and the piston rod 159900.doc 25.