RU2298105C2 - Reciprocating liquid machine - Google Patents

Abstract

FIELD: power engineering.

SUBSTANCE: invention is designed for use in power engineering as liquid device with triangular connecting rod provided with decoupling of pistons and in which each piston is furnished with its own pair of sliding surfaces and its own slider. Sliding surfaces of each piston are arranged at one side relative to support of lower end of connecting rod located on crank. Main axle of crank is made for travel along definite path which provides practically no lag or advance of piston. Effective center of masses of crank, piston and slider is motionless to axis of crank. Each piston includes guide to preclude movement of piston in direction other than along axis of piston. Guide is arranged across sliding surface and is made for engagement with guide members rigidly installed on case. Intermediate connecting device is provided which is made with possibility of connection of piston and sliders with means to adjust position of intermediate connecting device to change compression ratio of device. In device with pistons arranged opposite to each other, connecting rod unit connected to two pistons is split in two parts which are held together with possibility of detachment.

EFFECT: provision of dynamic balancing and possibility of use of odd number of pistons.

115 cl, 235 dwg

Description

The technical field to which the invention relates.

The present invention relates to such reciprocating fluid machines, which are called devices with a triangular connecting rod.

The background of the invention

Known devices with a triangular connecting rod include one or more pairs located in a horizontal plane opposite to each other pistons made with the possibility of reciprocating motion in the respective cylinders. Both pistons of the pair are rigidly interconnected, so that the movement of a pair of pistons is represented as the movement of a single body. The reciprocating movement of the pistons occurs along identically oriented axes, which can either be on the same straight line or be displaced relative to each other (while remaining parallel). In the center of the structural unit formed by such a piston pair, there is a crank mounted with an offset in the slider. The slider, in turn, is installed in the node of the piston pair between the opposite sliding surfaces, which are perpendicular to the axes of the pistons. The slider is limited in its movement perpendicular to the axes of the pistons in such a way that when the crank rotates, the reciprocating movement of the pistons along their axes is ensured according to the correct harmonic (i.e. sinusoidal) law. In certain circumstances, a correct sinusoidal movement is preferable to a quasi-sinusoidal movement provided by a structure consisting of a crank and a connecting rod, which is used in most internal combustion engines and pumps. However, such devices have certain disadvantages. Neither the slider, which is configured to perform reciprocating motion in a vertical plane, nor the pistons allow dynamic balancing with the help of some rotational mass. Despite the fact that this dynamic imbalance can be compensated to some extent in devices with several piston pairs, however, oscillating pairs remain.

In addition, in known designs, the slider is slidable between opposing sliding surfaces forming one pair and located on both sides of the support of the lower end of the connecting rod. Pistons should be located along parallel axes, and the distance between the sliding surfaces of the slider and the guide surfaces of the pistons should be greater than the diameter of the support of the lower end of the connecting rod on the crank.

The purpose of the invention is to correct at least some of the disadvantages of the prior art, and in preferred embodiments of the invention, to create a device in which paired pistons are not rigidly connected to each other and would not be necessarily located on one or parallel axes, and in which a higher degree of dynamic balancing would be provided. In addition, the present invention provides the possibility of using an odd number of pistons connected to one support of the lower end of the connecting rod.

In one embodiment of the invention, the actual decoupling of the pistons is provided, each piston having its own pair or group of sliding surfaces and its own slider. These sliding surfaces of each piston are not on both sides of the support of the lower end of the connecting rod, but are removed from the support of the lower end of the connecting rod by a certain distance. These sliding surfaces can be complex surfaces. Such a decoupling of the pistons means that each piston does not depend on communication with another piston or other pistons during its movement in both directions, and that the movement of each piston can be provided along its separate axis and in a different phase than the other pistons. Despite the fact that the pistons can be interconnected by means of some common connecting link, which is the carrier of the sliding surfaces of different pistons, however, the pistons are not rigidly connected to each other. A pair of pistons can form, for example, a V-shaped spatial configuration, or three pistons can be located star at an angle of 120 ° to each other.

An important feature of the invention is the use of restrictive means, which serve as guides for the piston or other parts of the piston structural unit. These restrictive means are located in a place that can be generally described as "towards the sliding surfaces, but not in one line with the sliding direction."

Description of the invention

In one of the General embodiments, the invention is a liquid device with a triangular connecting rod, which includes the following components:

- the crank, including the support of the lower end of the connecting rod, having an axis, for which it is possible to perform motion in orbit around the main axis of the crank;

- connecting means mounted on the axis of the support of the lower end of the connecting rod;

- at least one piston mounted with the possibility of reciprocating motion inside the cylinder along its axis, the piston having a cross-sectional area perpendicular to the axis of the piston and a guiding means including a linear surface located at the intersection of the axis of the piston, the guide means is engaged with the engagement means on the connecting means; and

- at least one restrictive means for restricting the movement of the piston along its axis;

wherein the piston guide means is configured to dissect the piston cross-sectional area into two equal parts, and at least a portion of each of the restrictive means is located within a certain volume swept away by the piston cross-sectional area as it moves along the piston axis, but is not located along the center line the above cut into two equal parts formed by the guide means of the piston.

The aforementioned guiding means advantageously includes surfaces made with a strike perpendicular to the respective axes of the pistons. However, this is not a mandatory requirement, and these guide surfaces can be made with respect to the respective axes of the pistons at a different angle than 90 °. We will consider the guiding surfaces “perpendicular” to the axes of the pistons, even when the angle they make with the axes of the pistons is compared from a straight line to 5 ° in one direction or another. The engagement means may be two or more parallel linear surfaces, which are respectively made to guide surfaces to slide along the latter. Alternatively, the engagement means may include two or more roller bearings or the like.

In this embodiment of the invention, opposed linear parallel guide surfaces may be located on the connecting means, and the engaging means may be located on the piston. In preferred embodiments of the invention, there are two or three pistons that are mounted on sliders on each support of the lower end of the connecting rod. If desired, the pistons can be located at equal angles to the main axis.

The guide means may be integral with the piston, or may be performed on a separate structural unit connected to the piston. When such a separate structural unit is used, it can be pivotally connected to the piston, and in preferred embodiments of the invention, using the piston pin structural unit. This makes it possible to use known pistons with connecting rods including guide means.

The crankshaft can be fixed relative to the cylinders or can be made movable with the possibility of changing the degree of compression and / or synchronization of the movement of the pistons inside the cylinders. With a V-shaped configuration of the cylinders, the movement of the crankshaft along the bisector of the internal angle formed by the cylinders changes the compression ratio without any phase changes. In an alternative embodiment of the invention, it is possible to rotate the crankshaft around a distant axis with raising or lowering the crankshaft. Such a constructive solution can be used in a single-piston engine. The movement of the crank can be carried out in any direction.

When using two pistons on each support of the lower end of the connecting rod, the pistons can be arranged in a V-shape. The angle of such a V-shaped configuration may be 90 °, 60 °, 72 °, or any other desired size. The number of pistons per one lower support of the end of the connecting rod is limited only by the physical dimensions of the components. Each support of the lower end of the connecting rod may have one connecting means on which several pistons are mounted, or there may be several connecting means on each bearing of the lower end of the connecting rod, each of these connecting means being connected to a piston mounted on it.

When several pistons are installed on one support of the lower end of the connecting rod, they can be located at the same distance from the main axis, or at different distances from the main axis.

Although, in preferred embodiments of the invention, the guiding means and the engaging means associated therewith include simple linear surfaces in cross section, other options are possible in which there are additional localizing surfaces perpendicular to the orientation lines provided by the guiding means.

Several embodiments of the present invention provide liquid devices with a triangular connecting rod, in which each piston can be decoupled with respect to another piston connected to the same bearing of the lower end of the connecting rod on the crank, thereby allowing each piston to move along the axis of the cylinder, which can be located at any angle to the axis of any other cylinder. In the manufacture of such devices according to the invention, it was found that the pistons can scroll in cylinders about an axis perpendicular to the axis of the cylinder, which leads to damage to the device. To prevent such damage, it was proposed to use restrictive means mounted on the piston, connected to the piston, or made integral with the piston, to maintain the correct orientation of the pistons and prevent unwanted rotation or distortion of the pistons. In some embodiments, the invention also provides a second restrictive means located outside the piston and cylinder bore. This requires additional space inside the crankcase, which leads to an increase in the size of the liquid device.

In preferred embodiments of the invention, all restrictive means are located in a volume swept away by the cross-sectional area of the piston as it moves along the axis of the cylinder. However, the guiding means, or restrictive means, or both, can also be performed with a strike beyond this volume. In addition, the restrictive means, being located inside the above volume, may not be located along the center line of dividing the cross-sectional area into two equal parts.

The restrictive means may be integral with the piston body, or may consist of one or more separate parts bonded to the piston body. In the case when the restrictive means is made separately from the piston body, it can be a single unit connected to the piston body rigidly or pivotally. The restriction means may include one or more guide elements, for example tubes or rods oriented parallel to the axis of the piston. In the case where the restriction means includes two or more guide elements, these guide elements may be located symmetrically or asymmetrically with respect to the center of the cross section of the piston.

In preferred embodiments of the invention, the guiding means is made to extend through the center of the cross-sectional area of the piston.

In the event that two or more pistons are installed on one support of the lower end of the connecting rod, these pistons may be located in one plane or in two or more planes.

In preferred embodiments, the device of the invention includes a stabilizing means adapted to engage with the connecting means to provide a single orientation of the connecting means while moving the latter in orbit around the main axis.

The above stabilizing means may provide coupling of the connecting means to at least one piston. The stabilizing device may include a separate connecting link pivotally connected to both the connecting means and the crankcase.

The crank mechanism may be a simple crank with a protruding support of the lower end of the connecting rod, or it may be a complex mechanism that provides something other than a simple rotational movement of the support of the lower end of the connecting rod with a constant angular velocity. Examples of complex crank mechanisms are described in international patent applications PCT / AU 97/00030 and PCT / AU 98/00287, which are incorporated into this patent application by reference.

In another embodiment, the invention includes a feature that the main shaft of the crank mechanism is movable along at least one path with respect to the cylinder or cylinders, and the engagement means is configured in such a way that there is no delay or an advance operation of at least one piston.

In the case when the pistons are V-shaped in the device according to the invention, the main axis of the crank mechanism is preferably provided with the possibility of moving along a linear path along the bisector of the internal angle of the obtained V-shaped figure. In an alternative embodiment of the invention, the main axis of the crank can be allowed to move along the arc.

In another embodiment of the invention, the center of mass of the connecting means is located on the axis of the support of the lower end of the connecting rod, or in close proximity to it.

In preferred embodiments of the invention, the crank includes a counterweight configured to provide static and / or dynamic balancing of the mass of the connecting means relative to the axis of the crank.

In preferred embodiments of the invention, the effective center of mass of the crank together with the connecting means and at least one piston, while rotating the crank, remains stationary or substantially stationary relative to the axis of the crank.

In yet another embodiment, the device according to the invention has two pistons located not opposite to each other, while the connecting means and gearing means are configured in such a way that the movement of each piston is ensured according to a simple harmonic law.

In yet another embodiment, the device according to the invention has at least one pair of pistons, each pair of pistons having a mass whose movement is equivalent to the movement of a material point in a certain orbit.

In preferred embodiments of the invention, the path of the above orbital movement is a circle, but it can also be elliptical.

In preferred embodiments of the invention, the movement of each of the pistons is a simple harmonic motion.

In another general embodiment, the invention also provides a liquid device that includes the following components:

- the crank, including the support of the lower end of the connecting rod, having an axis, for which it is possible to perform motion in orbit around the main axis of the crank;

- connecting means mounted on the axis of the support of the lower end of the connecting rod;

- at least one pair of pistons, each piston mounted with the possibility of reciprocating motion inside the corresponding cylinder along the corresponding axis, while the axis of the pistons of each piston pair are located relative to each other at an angle of 90 °, while each piston is connected with gearing means on the connecting means;

in which each piston pair has a mass whose movement is equivalent to the movement of a material point in a certain orbit;

the center of mass of the connecting means is located on the axis of the support of the lower end of the connecting rod, or in close proximity to it;

the crank includes a counterweight, which is located almost diametrically opposite the support of the lower end of the connecting rod, and the center of mass of which is located at a distance from the axis of the crank, while the counterweight provides the equivalent:

some first mass, designed to provide static and / or dynamic balancing of the entire mass of the support of the lower end of the connecting rod or part thereof with respect to the axis of the crank;

some second mass, designed to provide static and / or dynamic balancing of the entire mass of the connecting means or part thereof with respect to the axis of the crank; and

some third mass, designed to provide static and / or dynamic balancing of the entire mass of each pair of pistons or part thereof with respect to the axis of the crank.

In preferred embodiments of the invention, the angle is 90 °.

In preferred embodiments of the invention, the orbital path is a circle, and the third mass is selected with the possibility of static and / or dynamic balancing of the mass of the pistons.

In the case when the orbital motion path is not circular, the third mass can be selected with the possibility of balancing the mass of the pistons in the first direction. In preferred embodiments of the invention, this is the first direction perpendicular to the bisector of the angle between the axes of the corresponding pair of pistons.

In all embodiments of the invention, the connecting means (if any) can be configured to perform a non-rotational movement relative to the piston. In preferred embodiments, the implementation of the invention should dispense with any kind of rotational movement of the connecting means, except as taking place due to the presence of backlash.

In another general embodiment, the invention is a piston type liquid device that includes the following components:

- a crank having a main axis and including a support element of the lower end of the connecting rod having an axis for which rotation around the main axis is provided;

- at least one piston structural unit having at least one piston mounted for reciprocating motion inside the cylinder along the axis of the piston, the piston having a cross-sectional region that is oriented perpendicular to the axis of the piston;

- at least one driven transmission element located between the supporting element of the lower end of the connecting rod and the piston and designed to transmit the movement of the supporting element of the lower end of the connecting rod to the piston, while the driven transmission element is configured to reciprocate along a linear path having a central a line located between two end points; and

- at least one restrictive means designed to prevent a piston from moving otherwise than moving along the axis of the piston;

in which at least a portion of each restrictive means is located inside the volume swept away by the cross-sectional region as it moves along the axis of the piston, but is not located on the center line between the two end points.

The device according to the invention can have piston structural units, each of which has two surfaces, while on one surface there is a protruding support element, and on the other surface there is a support of the driven transmission element.

The device according to the invention may have only one driven transmission element having a support on both surfaces, or it may have two driven transmission elements, each of which is supported on a corresponding one plane.

Each piston assembly may have one piston, or it may have two pistons. In preferred embodiments of the invention, in cases where two pistons are provided for each piston assembly, there is at least one driven transmission element located below the pistons.

In preferred embodiments of the invention, the support element of the lower end of the connecting rod is a round cam, the center of which is offset from the axis of the crank.

In the device according to the invention, for each supporting element of the lower end of the connecting rod may have two or more piston structural units.

In cases where two or more piston structural units are provided for each supporting element of the lower end of the connecting rod, they are configured to reciprocate along the axes of the pistons oriented at an arbitrary angle with respect to each other. In a preferred embodiment of the invention, for each protruding support element of the lower end of the connecting rod there are two piston assemblies that are oriented at an angle of 90 ° with respect to each other.

In another general embodiment, the device of the invention is a liquid device with a triangular connecting rod, which includes the following components:

- the crank, including the support of the lower end of the connecting rod, having an axis for which the possibility of making orbital movement around the main axis of the crank, and which is parallel to the main axis of the crank;

- at least one piston structural unit, comprising the following components:

- a piston mounted with the possibility of reciprocating movement inside the cylinder along the axis of the piston, which is located in a plane perpendicular to the axis of the support of the lower end of the connecting rod and the main axis, while the piston has a cross-sectional area that is perpendicular to the axis of the piston; and

- an element of the type "triangular connecting rod" selected from the group including: channel, beam, channel and beam, bored hole and bored hole and beam, while the element of the type "triangular connecting rod" is configured to specify a longitudinal path, the support of the lower end of the connecting rod is made with the possibility of reciprocating movement along this path relative to the piston between the two end points, the element of the type "triangular connecting rod" is made integral with the piston or connected to the latter by means of a type of connecting rod; and

- restrictive means made with the possibility of making movement along a given path and preventing another movement of one or more pistons, an element of the type "triangular piston" and means and means such as a connecting rod, rather than movement along a given path,

characterized in that at least part of the restrictive means is located with the intersection of the longitudinal path of the element of the type "triangular connecting rod" inside the volume swept away by the cross-sectional area of the piston.

In preferred embodiments of the invention, the triangular connecting rod element includes surfaces oriented substantially perpendicular to the respective axes of the piston, as discussed above.

The restrictive tool, which has also been discussed above when considering the previous embodiment of the present invention, is intended to prevent piston jamming in the cylinder, which can occur at sufficiently high temperatures. It is desirable that the position of the piston is maintained on the axis of the piston. Several preferred embodiments of the invention are described herein with reference to the accompanying drawings. It should be noted that when the restrictive means is located inside the "trace" of the piston, minimization of the metal mass of the liquid device according to the invention is ensured.

As can be seen from the accompanying drawings, in some embodiments of the invention, restrictive means form pairs, and a line drawn from one element of such a pair to another is perpendicular to the longitudinal path. In other embodiments of the invention, the restrictive means includes elements that are located on opposite sides of the longitudinal path, but obliquely, not perpendicularly.

Restrictive means can be installed on the block inside the "trace" of the piston, so that the dimensions of the device according to the invention can be minimized.

In another general embodiment, the device according to the invention is also a liquid device, which includes the following components:

- a crank, including the support of the lower end of the connecting rod, having an axis, for which the possibility of orbital movement around the main axis;

- connecting means mounted on the axis of the support of the lower end of the connecting rod;

- at least one piston installed with the possibility of reciprocating motion inside the cylinder along the axis of the piston;

- an intermediate connecting means installed with the connection of at least one piston with a connecting means; and

- means for adjusting the position of the intermediate connecting means relative to at least one piston, or relative to the connecting means, or relative to both.

The aforementioned means for adjusting the position of the intermediate connecting means may include a groove, groove or surface that is engaged with this intermediate connecting means.

In a preferred embodiment of the invention, the aforementioned intermediate connecting means is included in the guide means or is engaged with the latter in order to stabilize at least one piston in the cylinder. In addition, in a preferred embodiment of the invention, the means for adjusting the position of the intermediate connecting means includes a guiding means, but this is not a prerequisite, the guiding means can be performed separately.

The aforementioned means for adjusting the position of the intermediate connecting means can be arranged to move relative to the axis of the cylinder in the transverse or longitudinal direction, or in both directions. The guide means may be configured to rotate about a certain axis.

The means for adjusting the position of the intermediate connecting means may include (in a single or in a larger quantity) grooves, grooves, surfaces, etc., which can be straight or curved, having one radius of curvature, or several radii of curvature. The above intermediate connecting means may include sliding or roller contact elements designed to interact with means for adjusting the position of the intermediate connecting means.

The means for adjusting the position of the intermediate connecting means may be configured to move in order to change the effective stroke of the pistons, the effective compression ratio provided by the device, or the path (both in the position parameter and in the time parameter) traveled by the pistons, or any combination of the above.

In yet another embodiment, the device of the invention includes means for adjusting the distance between the piston and the engagement means.

The aforementioned means for adjusting the distance between the piston and the engagement means used in this embodiment may include a compressible connecting rod.

It is described above how the liquid device according to the invention can be completely or practically balanced statically or dynamically, or both statically and dynamically with respect to the axis of the crank. It should be noted that in accordance with the above, the additional mass of the restrictive means can be balanced. In addition, it should be noted that, although the balancing of the pistons mounted on the same crank is the norm, balancing the device with pistons mounted on separate bearings of the lower end of the connecting rod is possible only when the bearings of the lower end of the connecting rod are on the same axis.

The above described variants of the device according to the invention, in which the movement of the pistons is provided with the help of sliders mounted on the bearings of the lower end of the connecting rod, and in which two or more pistons can be installed on one slide, but for each of them it is possible to move along a separate path to each other.

Since no piston is directly connected to any other piston, the pistons tend to rotate inside the cylinders around an axis almost parallel to the axis of the crank. This may cause the device to malfunction. However, with restrictive means oriented parallel to the axis of the cylinder, such unwanted rotation is prevented as described above. In some embodiments of the invention, the restrictive means is located above the swept volume of the crankshaft and the lower end support of the connecting rod. Restrictive means can be placed so that at different stages of the cycle they are directed to the projection of the area swept away by the crank and slider. This allows you to make the device more compact.

In known piston fluid machines with a triangular connecting rod, the slider is mounted to rotate on the support of the lower end of the connecting rod on a crank, which is configured to move around the main axis. The movement of the slider is limited by the movement along a straight groove made in the piston structural unit, which is oriented almost perpendicular to the axis of the cylinder. Thus, when the crank is rotated, the piston is forced to reciprocate along the axis of the cylinder.

In known devices with one piston, the aforementioned straight groove is located on the axis of the cylinder so that when the piston is at the top dead center, the support of the lower end of the connecting rod occupies a position between the piston and the main axis.

The present invention allows to create various new and non-obvious options for a liquid machine that do not comply with these standards.

In another embodiment of the invention, when the piston is at top dead center, the main axis is between the piston and the support axis of the lower end of the connecting rod.

This is actually the opposite of normal.

In another embodiment of the invention, the main axis is not located on the axis of the cylinder or on any of the axes of the cylinders.

In a preferred embodiment of the invention, when the piston or one of the pistons is at the top or bottom dead center, the line connecting the main axis and the axis of the support of the lower end of the connecting rod is parallel to and offset from the axis of the corresponding cylinder.

In the prior art, in internal combustion engines or pumps with a triangular connecting rod, two opposing pistons are usually rigidly interconnected by means of a connecting rod assembly. In this case, the slider, which is installed with the possibility of performing rotational motion on the support of the lower end of the connecting rod on the crank, is made to slip inside this connecting rod assembly, while forcing the reciprocating movement to the pistons.

The aim of the invention is the creation of improved designs of the connecting rod assembly, which allow, in preferred embodiments of the invention, to use two identical parts to build the connecting rod assembly. This connecting rod assembly can be split in the longitudinal or transverse direction relative to the axis of the cylinder. In preferred embodiments of the invention, the number of required fixing parts is reduced, which simplifies the manufacturing process of the components of the device.

In one of the general embodiments of the invention, in a liquid device of a triangular-connecting rod type, in which the pistons located opposite each other are arranged to reciprocate in opposite cylinders, the axes of which are parallel, it is provided that the connecting rod assembly is mounted on two pistons and includes a gearing section designed to interact with a gearing member mounted to rotate on a support izhnego end of the connecting rod at the crankshaft, and wherein the engagement means is configured to reciprocating motion by the rotation of the crank, wherein said engaging portion is split into two parts.

The aforementioned engagement portion may be split along a plane substantially parallel to the axes of the cylinders, or along a plane substantially perpendicular to the axes of the cylinders.

The above two parts into which the engagement portion is split can be either identical or different.

In preferred embodiments of the invention, only two locking parts are required to securely hold the two parts together.

In preferred embodiments of the invention, the engagement portion includes two opposed channels in which the reciprocating means are provided for engagement. The boundaries of each of these channels can be formed by only one of the parts, or the borders of each channel can be formed by both parts.

In preferred embodiments of the invention, in cases where the parts are identical and the borders of each channel are formed by only one part, or the borders of each channel are formed with the participation of both parts, each part includes a leg that is elongated towards the other part with engagement with her. These legs can be located on opposite ends of the channel, on the same side of the channel, or on the same end of the channel, but on its opposite sides, or on opposite ends and on the opposite sides of the channel. In preferred embodiments of the invention, the retention of two legs, each of which belongs to the corresponding one part, can be achieved using one fixing part.

In cases where non-identical parts are used, one of the parts may have two or more protruding legs located next to the channel, while the other part may not have legs at all or have one leg located next to the channel.

In preferred embodiments of the invention, the legs are located at the ends of the channel, but a solution is possible when a single leg is located near the channel at a midpoint. In this design, the crank is made with the inability to pass through the site of engagement.

It was found that the devices according to the invention (with decoupling of pistons, with paired pistons or a triangular-connecting rod type) can be perfectly balanced, so that the center of mass of the moving parts of the machine (crank, pistons and their elements, as well as connecting elements between the lower support end of the connecting rod and pistons) remains absolutely motionless and centered on the main axis when these parts of the machine perform rotational movements, orbital movements and reciprocating movements during its working of the cycle. A pair of pistons located at an angle of 90 ° to each other and mounted on the same axis of the support of the lower end of the connecting rod can be perfectly balanced. A pair of pistons located at an angle of 90 ° to each other and mounted on the coaxial bearings of the lower end of the connecting rod can also be perfectly balanced (although a swinging pair can be installed in this embodiment).

A machine with V-shaped pistons (at an angle other than 90 °) can also be perfectly balanced. This can be achieved by splitting the support of the lower end of the connecting rod in such a way that for a pair of masses made with the possibility of reciprocating motion, that is, pistons, there would be two axis of support of the lower end of the connecting rod. These two axes of the support of the lower end of the connecting rod have an angular displacement relative to each other around the main axis.

Brief description of the attached drawings

The invention will be better understood by considering some preferred embodiments thereof (to which the scope of the invention is not limited), which are described below with reference to the accompanying drawings.

Figure 1 in cross section shows a liquid device according to the invention.

In Fig.2, the device shown in Fig.1 is shown in perspective view with a partial cutaway.

Figure 3 in a perspective view shows a three-piston device according to the invention.

Figure 4 in a top view shows the device according to the third embodiment of the invention.

Figure 5 is a partially cutaway perspective view of a device according to a fourth embodiment of the invention.

6, a top view shows a connecting device related to the device shown in FIG. 5.

In Fig.7, the device shown in Fig.6 is shown in a perspective view.

On Fig in a top view shows the device, which is a variation of the device shown in Fig.6.

Figure 9 is a perspective view of the device according to the fifth embodiment of the invention.

In Fig. 10, the device shown in Fig. 9 is shown in a plan view.

11, a top view shows a device according to a sixth embodiment of the invention.

On Fig top view shows the device according to the seventh embodiment of the invention.

On Fig top view shows the device according to the eighth embodiment of the invention.

On Fig - Fig shows various configurations of the guide surfaces related to the device according to the invention.

On Fig shows an internal combustion engine with two V-shaped cylinders, which is an embodiment of the invention, provided with restrictive means.

On Fig shows a kinematic diagram of an internal combustion engine with two V-shaped cylinders, which is an embodiment of the invention, equipped with restrictive means.

On Fig - Fig shows longitudinal sections through the support of the lower end of the connecting rod and embodiments of the connecting means in the device according to the invention.

On Fig - Fig shows other options for the connection between the connecting means and means of engagement of the piston.

On Fig and Fig shown in top view embodiments of an internal combustion engine with a triangular connecting rod according to the invention.

On Fig and 51 schematically in cross section shows other embodiments of the invention.

On Fig top view shows another embodiment of the invention.

On Fig top view shows another embodiment of the invention.

On Fig and 55 in a top view shows another embodiment of the invention.

On Fig in a perspective view shows another embodiment of the invention.

On Fig in a perspective view shows another embodiment of the invention.

In Fig. 57a, the embodiment shown in Fig. 57 is shown in a plan view.

On Fig in top view shows another embodiment of the invention.

In Fig. 59 and Fig. 60, the embodiment shown in Fig. 58 is shown in perspective view.

On Fig in a perspective view shows another embodiment of the invention.

In Fig. 62, the embodiment shown in Fig. 61 is shown in a plan view.

On Fig - Fig in top view shows other embodiments of the invention.

In Fig. 69 - Fig. 78, Fig. 78a, Fig. 79 and Fig. 80, a top view shows the structural units of the sliders used in various embodiments of the invention.

On Fig in a perspective view shows a piston related to the device according to the invention.

On Fig, the piston shown in Fig, shown at a different angle.

On Fig in a perspective view shows a liquid device according to the invention, in which there is a piston shown in Fig and Fig.

On Fig shows a detailed view of a portion of the device shown in Fig.

On Fig - Fig 126 in the bottom view shows the various pistons related to the invention.

In Fig.127 - Fig.129 shows in different projections other variants of the piston related to the invention.

In Fig.130 - Fig.132 shows in different projections other variants of the piston related to the invention.

In Fig.133 - Fig.135 shows in different projections other variants of the piston related to the invention.

In Fig.136 - Fig.138 shows in different projections other variants of the piston related to the invention.

In Fig.139 - Fig.141 shows in different projections other variants of the piston related to the invention.

In Fig.142 - Fig.144 shows in different projections other variants of the piston related to the invention.

In Fig.145 - Fig.147 shows in different projections other variants of the piston related to the invention.

In Fig.148 - Fig.150 shows in different projections other variants of the piston related to the invention.

In Fig.151 - Fig.153 shows in different projections other variants of the piston related to the invention.

In Fig.154 - Fig.156 shows in different projections other variants of the piston related to the invention.

In Fig.157 - Fig.159 shows in different projections other variants of the piston related to the invention.

In Fig.160 - Fig.162 shows in different projections other variants of the piston related to the invention.

In Fig.163 - Fig.165 shows in different projections other variants of the piston related to the invention.

In Fig.166 - Fig.168 shows in different projections other variants of the piston related to the invention.

In Fig.169 - Fig.171 shows in different projections other variants of the piston related to the invention.

In Fig.172 - Fig.174 shows in different projections other variants of the piston related to the invention.

In Fig.175 - Fig.177 shows in different projections other variants of the piston related to the invention.

In Fig.178 - Fig.180 shows in different projections other variants of the piston related to the invention.

In Fig.181 - Fig.183 shows in different projections other variants of the piston related to the invention.

In Fig.18 - Fig.186 shows in different projections other variants of the piston related to the invention.

In Fig.187 - Fig.189 shows in different projections other variants of the piston related to the invention.

In Fig.190 - Fig.192 shows in different projections other variants of the piston related to the invention.

In Fig.19 - Fig.195 shows in different projections other variants of the piston related to the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig in cross section shows another embodiment of the invention.

On Fig embodiment of the invention, shown in Fig, shown in cross section in a different position.

On Fig one of the embodiments of the invention is shown in plan view in the first position of the duty cycle.

In Fig.211 - Fig.213 an embodiment of the invention, illustrated in Fig.210, is shown in plan view at other stages of the working cycle.

In Fig.214, an embodiment of the invention, illustrated in Fig. 210, is shown in perspective view.

In FIG. 215, a portion of the apparatus illustrated in FIG. 214 is shown on an enlarged scale.

On Fig shows a view of the device illustrated in Fig, in a projection in the direction perpendicular to the axis of one of the cylinders, when one of the pistons is at bottom dead center.

In Fig.217 shows an embodiment of the invention, similar to that illustrated in Fig.216, while one of the pistons is in top dead center.

On Fig in axial top view shows another embodiment of the invention.

On Fig in axial top view shows another embodiment of the invention.

On Fig in axial top view shows another embodiment of the invention.

On Fig in axial top view shows another embodiment of the invention.

On Fig in axial top view shows another embodiment of the invention.

On Fig in top view shows another embodiment of the invention. To avoid piling up parts, some components are not shown.

In FIG. 22, an embodiment of the invention, illustrated in FIG. 1, is shown in perspective view.

On Fig the first embodiment of the invention is shown in a perspective view with exploded elements.

On Fig in perspective view shows another embodiment of the invention.

On Fig in perspective view shows another embodiment of the invention.

In FIG. 228, an embodiment of the invention illustrated in FIG. 227 is shown in exploded perspective view.

In FIG. 229, an embodiment of the invention, illustrated in FIG. 227, is shown in a plan view.

In Fig.230 - Fig.233 in a perspective view schematically shows the design options of the rocker.

On Fig in a perspective view shows a crank with a pair of split supports of the lower end of the connecting rod.

On Fig top view shows an embodiment of the invention, a device with a triangular connecting rod with a V-shaped arrangement of cylinders, in which the bearings of the lower end of the connecting rod are coaxial, and pistons made with the possibility of reciprocating motion are located at an angle of 75 ° relative to main axis.

On Fig top view shows an embodiment of the invention, a device with a triangular connecting rod with a V-shaped arrangement of cylinders, in which the bearings of the lower end of the connecting rod are coaxial, and pistons made with the possibility of reciprocating motion are located at an angle of 90 ° relative to main axis.

On Fig top view shows an embodiment of the invention, a device with a triangular connecting rod with a V-shaped arrangement of cylinders, in which the bearings of the lower end of the connecting rod are coaxial, and pistons made with the possibility of reciprocating motion are located at an angle of 120 ° relative to main axis.

On Fig in perspective view shows a connecting rod designed to operate as part of a single-piston structural unit.

On Fig in a perspective view shows a single-piston structural unit designed to work with the connecting rod shown in Fig. 238.

The optimal implementation of the invention

Figure 1 and figure 2 shows a liquid device 10, which includes a crank 12 made with the possibility of making a rotational motion around the axis 14 of the crank. The crank on the crankshaft 12 has a protruding support 16 of the lower end of the connecting rod, which is removed from the axis 14 of the crank in the radial direction. Thus, the support 16 of the lower end of the connecting rod is configured to perform orbital motion with a circular path around the axis 14 of the crank when the crankshaft 12 rotates around its axis 14.

Connecting means 18 are mounted on the support pin 16 with a possibility of rotation. Connecting means 18 has two protrusions - a protrusion 20 and a protrusion 22.

The connecting means 18 is made with a strike almost perpendicular to the axis 14 of the crank, and the protrusions 20 and 22 are almost parallel to the axis 14 of the crank. As can be clearly seen in figure 2, the sliding surface is axially stretched on different sides of the main section 24 of the connecting means 18, as a result of which the resulting structure has the shape of the letter "T" in cross section.

Both protrusions 20 and 22 are adapted to mesh with a cross-section T-shaped grooves 30 made in the pistons 32. Each of the pistons 32 is mounted in the corresponding cylinder 34 with the possibility of linear movement along the corresponding axis 36 of the cylinder. In preferred embodiments of the invention, each of the grooves 30 is made with a strike, almost perpendicular to the axis 36 of the cylinder with a passage diametrically through the center of the piston. Both ends of the groove 30 are open. Thus, the connecting means 18 is made with the possibility of lateral movement on either side of the piston, but at the same time with the possibility of axial movement with the piston 32 along the axis 36 of the cylinder. In those cases when the groove 30 is not at an angle of 90 ° to the axis 36 of the cylinder, due to the lateral movement of the protrusion 20 or 22 relative to the piston 32, the piston 32 is forced to perform axial motion. This allows you to control the movement of the piston 32, deviating from the movement according to a simple harmonic law.

The piston 32 is made with the possibility of its limited movement along the axis 36 of the cylinder, and when the crank is rotated on the crankshaft 12, the connecting means 18 are rotated around the crank axis 14. The movement of the protrusions 20 and 22 has a component parallel to the corresponding axis 36 of the cylinder, and a component perpendicular to the corresponding axis 36 of the cylinder. Thus, the pistons 32 are arranged to reciprocate within the corresponding cylinder 34, while the protrusions 20 and 22 slide in the lateral directions in the respective grooves 30. Thanks to the combination of the linear movement of the piston 32 and the protrusion 20 or 22 in the groove 30, the support the constant orientation of the connecting means 18 during rotation of the crank on the crankshaft 12 independently of other pistons. In the embodiment of the invention, illustrated in figure 1, there are two pistons 32 located at an angle of 90 ° to each other, but since it is ensured that the orientation of the connecting means 18 is maintained constant during its orbital movement around the crank axis 14, the angle between the pistons 32 may to be other than 90 °. In addition, the number of pistons can be increased.

Figure 3 in a perspective view shows a three-piston device according to the invention. In order to avoid accumulation of parts, cylinders and crankcase are not shown. As can be seen from figure 3, the device 110 includes a crank 112 with a support pin 116 made with a strike between the cheeks 117. Three pistons are located around the crank 112 at an angle of 120 ° to each other. A three-protrusion device 118 is installed on the support pin 116, which can either be a monolithic body or consist of separate components mounted on the support pin 116. As you can see, each piston is equipped with a T-shaped groove 130, which can be engaged with the corresponding protrusion 120. In this embodiment, the pistons are displaced relative to each other in the axial direction, but if desired, they can be made located in the same plane.

Since the pistons are decoupled relative to each other, the orientation and position of each piston can be selected at will by any. There is no need for the axis of the cylinders to be oriented radially from the axis of the crank. The axis of the cylinders can be made with a radial orientation relative to some axis, but this axis can be offset relative to the axis of the crank. In addition, the axis of the cylinders can be parallel and located on both sides of the axis of the crank.

FIG. 4 shows a fluid device 50 having a crank 52 configured to rotate about a crank axis 54. A slide mechanism 57 is installed on the support pin 56, which has two shoulders - a shoulder 58 and a shoulder 60, made with horizontal wiping with engagement with grooves 62 and 64, respectively, made in pistons 66 and 68, respectively. Pistons 66 and 68 are arranged to reciprocate in a two-chamber cylinder 70 or 72, respectively. Cylinders 70 and 72 are closed at both ends, and thus combustion chambers 74 are formed between the pistons and cylinder ends.

When the crank 52 is rotated, the pistons 66 and 68 are forced to reciprocate in the vertical direction inside the cylinders 70 and 72, respectively, while the arms 58 and 60 are moved in the lateral directions relative to the pistons 66 and 68.

Figure 5 - figure 7 shows a reciprocating reciprocating device 210 having two pistons 232, made with the possibility of making reciprocating motion inside the respective cylinders 234 located at an angle of 90 ° to each other. Both pistons are connected to the support of the lower end of the connecting rod by a support pin 216 of the crankshaft 212 using the connecting means 218 through the protrusions 220 and the grooves 230 made in the pistons 232. The connecting means 218 has two cheeks 240, one for each piston, which are axially offset direction relative to each other. Due to this, the possibility of mutual overlapping of the space of the pistons 232 and their closer to the axis 214 of the crank. Oil pipelines 242 are provided for supplying lubricating oil under pressure from the support pin 216 to the sliding surfaces of the protrusions 220 and grooves 230.

The connecting means 218 includes a counterweight 244, which is made on the opposite side from the support pin 216 with a downward extension to the projections 220 along the bisector of the angle between the two cheeks 240. The dimensions of the counterweight 244 are such that the center of inertia, and in the preferred embodiments of the invention, the center of mass of the connecting means 218 are located on the axis 246 of the support of the lower end of the connecting rod. It should be noted that in cases where the pistons are at the same distance from the axis 214 of the crank 248, mutual balancing of the cheeks 240 is provided, and there may be no need for a separate counterweight.

When the connecting means 218 performs orbital movement around the axis 214 of the crank 248, there is no torque relative to the axis 246 of the support of the lower end of the connecting rod, which could cause the connecting means 218 to rotate around the support of the lower end of the connecting rod, and which would require the creation of an oppositely directed torque in conjunction the groove 230 is the protrusion 220. In addition, since the center of inertia of the connecting means 218 remains on the axis 246 of the support of the lower end of the connecting rod, it is relatively easy to add to p otivovesu 244 on the crankshaft 212 diametrically opposite the proper mass axis 246 of the lower end of a rod support for dynamic balancing crank system - connection means. It should be noted that dynamic balancing can be provided for other structural variants of the piston assembly, provided that the center of inertia of the connecting means 218 is located on the axis 246 of the support of the lower end of the connecting rod.

The mass of pistons 232, made with the possibility of reciprocating motion, remains unbalanced. The speed of each piston 232 varies according to a simple harmonic law, and the resulting motion of both pistons 232 is equivalent to the rotation of some material point. This movement can be balanced by adding the appropriate mass to the crankshaft 212, whereby a dynamically balanced device can be obtained. For a two-piston device with a V-shaped arrangement of cylinders, the mass of one piston must be added to the rear side of the crankshaft 212. For a four-piston device with a star arrangement, a mass of two pistons must be added to the counterweight of the crank.

On Fig shows a liquid device 50, which is a modification of an embodiment of the invention, illustrated in figure 1. For ease of understanding, the same notation is used for identical components. The pistons 32 are only capable of linear movement along the axes of the cylinders 36, while the protrusions 20 are only capable of linear movement relative to the corresponding piston 32, and the possibility of any rotational movement of the connecting means 18 relative to the piston 32 is theoretically excluded. technical tolerances in the manufacture of the inevitable presence of certain backlashes, and hence some rotation of the connecting means 18 relative to the corresponding the piston 32. This, in turn, generates torques in the interface between the protrusions 20 and the grooves 30. To eliminate this phenomenon, the device illustrated in Fig. 8 is provided with a connecting link 40. One end of this connecting link 40 is rotatably connected about an axis 42 with connecting means 18, and its other end is rotatably connected to a crankcase (not shown). Thus, the connecting link 40, the connecting means 18, the crank on the crankshaft 12 and the crankcase form a four-link lever mechanism. The distance between the axles 42 and 46 is equal to the distance between the axis of the crank 14 and the axis 11 of the support 16 of the lower end of the connecting rod. Thus, regardless of the restrictions imposed by the connection of the connecting means 18 with the pistons 32, it is ensured that the connecting means 18 performs orbital movement around the axis of the crank 14 without changing the orientation.

Figure 9 and figure 10 shows a two-cylinder liquid device 260, in which the pistons 262 are arranged to reciprocate in the cylinders 264. Each of the pistons 262 is equipped with a piston pin 266, which is installed in the bearing 268 of the corresponding piston. A connecting rod 270 is mounted on the piston pin 266. However, the connecting rod 270 does not rest on the support of the lower end of the connecting rod on the crank on the crankshaft 12, but on the connecting means 18. The lower end 272 of the corresponding connecting rod 270 has a groove 74 of the T-section in which the corresponding protrusion is mounted 20, also T-shaped in cross section, related to the connecting means 18. The connecting rod 270 is configured to freely rotate around the piston pin 266 relative to the piston, however, the combination of the mating flat surfaces of the grooves 272 and the protrusions 20 provide of preventing any rotation, causing movement of the connecting rod 270 is provided and a connecting means 18 as a whole. It may seem that this gives the design unnecessary complexity, but this allows the use of pistons known from the prior art.

11 shows a two-cylinder fluid device 80 with two pistons 82 mounted on the connecting means 18 with the possibility of reciprocating movement inside the cylinders 84. The connecting means 18 is mounted on the crankshaft 12, but the axis of the crankshaft 12 is not fixed relative to the cylinders 84. Instead, the crankshaft 12, and with it the connecting means 18 and pistons 82, are configured to move up and down in the direction shown by arrows 86. With a vertical shift By cranking the crankshaft 12, the pistons 82 are lifted in the cylinders 84, which makes it possible to change the compression ratio. The movement of the crankshaft 12 does not affect the temporal characteristics of the movement of the pistons in the cylinders 84 relative to the crankshaft 12 or to each other. This is the difference between the device according to the invention from known internal combustion engines with a V-shaped arrangement of cylinders, in which, in the presence of movable crankshafts, the temporal mode of movement of the pistons does not remain unchanged, but one piston moves ahead of schedule and the other late.

The vertical movement of the crankshaft 12 can be achieved using known means, such as, for example, hydraulic rams. The line indicated by arrow A is directed along the bisector of the angle between the pistons 82.

It should be noted that the movable crank can be used in a single-cylinder device, and this movable crank can be arranged to move along a path that is not specified in a certain way, such as, for example, the bisector of the angle between the cylinders in a V-shaped internal combustion engine cylinders. The crank can be made with the possibility of moving, for example, at an angle of 15 ° to the vertical. This only leads to the need for more movement of the crank to achieve the same compression ratio.

On Fig shows a device that is a modification of an embodiment of the invention, illustrated in Fig.11. In this device, the crankshaft 12 is mounted on the supporting arms 90. The supporting arms 90 are mounted on the crankcase, being pivotally connected thereto with the possibility of rotation around axes coinciding with the axis 94. It is possible to rotate the bearing arms around the axis 94 using suitable means, as a result which ensures the raising or lowering of the crankshaft relative to the cylinders. At the same time, there is some lateral displacement of the crankshaft, and as a result, an advance in the movement of one piston and a lag of the other, however, this effect has a very weak manifestation.

13 shows another embodiment of the present invention, which is a two-cylinder fluid device 100 having pistons 102 configured to reciprocate in cylinders 104. Pistons 102 are equipped with connecting rods 106 that are mounted on piston pins 108, having swivel with them. The lower end of the connecting rod 106 has two parallel surfaces opposite each other on which the slider 110 is mounted. The opposite ends of the slider 110 are connected to the hydraulic rams 112. These hydraulic rams 112 are an integral part of the connecting means 18 and are configured to selectively supply hydraulic liquids (oils) through oil lines 114. Thus, the hydraulic rams 112 are configured to exert an effort on the slider 110 to rotate it around its prices pa 116 raising or lowering the connecting means 118, and hence relative to the cylinder 104, or a combination of both. In this case, the piston 102 is raised or dropped relative to the corresponding cylinder and / or the connecting rod 106 rotates around the piston pin 108, as a result of which the phase of the piston movement is changed.

On Fig - Fig shows a number of varieties of the guide surfaces of the piston and the corresponding surfaces of the means of engagement.

FIG. 14 shows a slider 100 having a Y-shaped engagement surface for engaging with one piston surfaces 104 and 106.

FIG. 15 shows a slider 110 provided with an engagement means 112. This engagement means 112 has a Y-shaped cross section and has surfaces 114 and 116 extending from the base 118.

FIG. 16 shows a slider 120 provided with an engagement means 122. As you can see, this engagement means has a T-shaped cross section and it has two arms — a arm 124 and a arm 126. These arms 124 and 126 have a common upper surface 128, bent in cross section.

17 shows a slider 130 provided with an engaging means 132 having a cross-sectional shape of an arrowhead. This engagement means 132 has two arms 134 made with a strike downward with divergence in different directions with the possibility of engagement with the piston.

FIG. 18 shows engagement means 140 having a W-shaped cross section.

19 shows engagement means 150 having a T-shaped cross section, with the upper surface 152 and the lower surface 154 of the arms 156 provided with V-shaped grooves 158 into which the V-shaped protrusions 160 are inserted. These V-shaped grooves 158 and protrusions 160 may be located at the other end of the piston and engagement means.

FIG. 20 shows engagement means 170 having a T-shaped cross section and having an upper surface 172, in the center of which a groove 173. A corresponding surface 174 belonging to the piston includes a protrusion 176 that has a rectangular cross section and is inserted into the groove 173 .

21 shows an engagement means 190 having a T-shaped cross section and having a protrusion 192, the cross section of which is in the form of a semicircle located in the center of the upper surface 194. But it is not necessary that this protrusion 192 is located in the center of the surface, and additional projections can be made located on one or both sides of the center of the engagement means 190 on the upper surface 194, or on the lower surfaces 196 and 198, or on the upper and lower surfaces.

FIG. 22 shows a structure similar to that illustrated in FIG. 17, except that the upper engagement surface 180 belonging to the piston is not continuous but has a gap 182.

23, an engagement means 200 is shown having a T-shaped cross section.

24 shows an engagement means 210 having a T-shaped cross section and having arms 212 and 214. The side surfaces 216 and 218 of the arms 212 and 214 are curved so that the distance between the side surfaces 216 and 218 in the middle of the engagement means 210 is greater. than the distance between them at both its ends. It should be noted that the width of the corresponding groove in the piston must have a width at least equal to the widest part of the upper surface of the shoulders 212 and 214.

26 shows an engagement means 230 having a T-shaped cross section and having shoulders 232 and a central leg 234. Leg 234 has linearly spaced teeth 236 and 238 on its two surfaces. Teeth 236 and 238 can be used to propel others devices through means of rotatable gears mounted on pistons.

FIG. 28 shows engagement means 250 having a T-shaped cross section and having linearly spaced teeth 252 located in the middle of its upper surface 254. As in the embodiment illustrated in FIG. 26, these teeth can be used to drive devices mounted on the piston or inside the piston.

On Fig shows a two-cylinder internal combustion engine 300 with a V-shaped arrangement of cylinders having pistons 302, crank 304 and connecting means 306 mounted on the supporting lower end of the connecting rod support pin 308 on the crank 304. Pistons 302 are pistons of known design, each of them has a piston pin 310 on which the connecting rod 312 is mounted for rotation. However, unlike the known structures, each connecting rod 312 has a groove 314 at its lower end into which the connecting means 306.

Each connecting rod has a laterally extended shoulder 316, which is engaged with a slider 318, which is slidable in the guides 320 parallel to the axis of the corresponding cylinder. The connecting rod 312 can be made integral with the slider 318, or can be connected to it using the heel joint 322, as in the considered embodiment. The heel joint 322 can be either uniaxial or ball. In the present embodiment, the shoulders 316 are made with a strike parallel to the grooves 314. However, they can be oriented at any other angle.

The guides 320 are designed to help stabilize the respective pistons 302, since as a result of manufacturing tolerances there is a risk of some rotation of the piston 302 inside the channel, which could lead to jamming or other undesirable situations. If very strict tolerances were used in the manufacture, then guides 320 may not be needed. The guides 320 can be made integral with the crankcase, or they can be individual parts attached to the crankcase using screw connections or other known means.

The piston fingers 310 mounted on the pistons 302 can be located at an angle of 90 ° to the crank axis, since any rotational movement of the connecting rod 312 with respect to the corresponding piston 302 is excluded. Using pistons 302 with piston fingers 310 allows the use of pistons removed from production.

On Fig shows a kinematic diagram of a two-cylinder internal combustion engine with a V-shaped arrangement of cylinders having a main crank 330, the support of the lower end of the connecting rod 332 and the connecting means 334 mounted on the support of the lower end of the connecting rod. As in the previously discussed options, the pistons 336 are mounted on the connecting means 334.

There is an auxiliary crank 338 configured to rotate about an axis 340 parallel to the axis 331 of the main crank. There is a link 342, which is pivotally connected on one side with both connecting means 334 and 344, and on the other hand with an auxiliary crank 338 at the pivot point 346. The distance between the pivot point 346 and the axis 340 of the auxiliary crank is equal to the distance between the axis of the support of the lower end of the connecting rod 332 and axis 331 of the main crank. Thus, the auxiliary crank 338 and the link 342 are configured to help maintain a constant orientation of the connecting means 334 while rotating the main crank 330. It should be noted that this spatial orientation stabilization technology can be used in any embodiment of the invention described herein.

On Fig schematically shows an axial section through the support of the lower end of the connecting rod 350 and the connecting means 352. The connecting means 352 has an engagement means 354, which is engaged with the engagement means 356 and 358 of two separate pistons (not shown).

FIG. 32 schematically shows a structure similar to that illustrated in FIG. 31, different from the last configuration of the engagement means 360 mounted on the connecting means 362, and the corresponding engagement means 364 and 366 of the two pistons.

FIG. 33 shows a connecting means 370 having two grooves — a groove 372 and a groove 374 into which engagement means 376 and 378 are inserted having a T-shaped cross section, respectively. Means of engagement 376 and 378 can be attached to one piston as well as to different individual pistons.

FIG. 34 shows a connecting means 380 having two grooves — a groove 382 and a groove 384. These grooves have a Z-shaped cross section and engagement means 386 and 388 are introduced into them, respectively.

On Fig shown connecting means 390, having two grooves - a groove 392 and a groove 394, which introduced means of engagement 396 and 398, respectively. In the grooves are roller bearings 400, designed to facilitate the movement of the clutch means 396 and 398 along the grooves 392 and 394. It should be noted that the roller bearings are spaced throughout the grooves 392 and 394.

On Fig shows the connecting means 410, while belonging to the piston (or different pistons) means of engagement 412 and 414 are located around the connecting means 410 and made with the possibility of engagement with open downward slots 416 and 418.

On Fig shows the connecting means 420, having two grooves - a groove 422 and a groove 424, open in the lateral directions.

On Fig shows the connecting means 430, which is meshed with the means of engagement 432 having a T-shaped cross section and having shoulders 434 and 436, made with the divergence down. The upper surface 438 and the lower surface 440 of the arms 434 and 436 may be parallel, as shown in the present embodiment, but may also be made diverging. The piston is provided with rows of opposed to each other roller bearings 442, which are in cooperation with the upper surface 438 and the lower surface 440. The center line of the arms 434 and 436 with respect to the axis of the support of the lower end of the connecting rod can be oriented, for example, at an angle from 35 ° to 50 °.

On Fig - Fig shows other possible modifications of the connection between the connecting means and means of engagement of the mounted piston or pistons. In the modification illustrated in FIG. 41, roller bearings are used (indicated by the letter “B”).

On Fig shows a two-cylinder liquid device 500 having two opposed to each other pistons 502 and 504, made with the possibility of reciprocating motion inside the cylinders 506, which are located on the same axis. Pistons 502 and 504 are rigidly interconnected using a connecting link 507. There are two crankshafts - a crankshaft 508 and a crankshaft 510 connected by connecting means 512, which is mounted on the respective bearings 514 and 516 of the lower end of the connecting rod. The aforementioned connecting means is installed with passage through a channel 518 made in the connecting link 507, which is designed to prevent the connecting means 512 from sliding sideways relative to the connecting link 507. In preferred embodiments of the invention, the movement of the connecting means 512 is perpendicular to the axis of the cylinders, but this is not necessary requirement.

In preferred embodiments of the invention, two crankshafts 508 and 510 are connected, for example, by a gear train, so that they rotate together. When the crankshafts 508 and 510 rotate, the connecting means 512 move in the vertical direction according to a harmonic law, due to which the pistons 502 and 504 are forced to a similar movement.

On Fig shows another modification of an embodiment of the invention, illustrated in Fig. 48. Similar components have the same numerical designations.

Although in this embodiment, the connecting means 512 is installed without limiting the possibility of sliding to the sides relative to the connecting link 507, nevertheless, certain lateral loads are applied to the connecting link 507. Accordingly, on both sides of the connecting link 507, guide surfaces 520 and 522 are provided to prevent lateral movement.

On Fig shows another modification of the variant illustrated in Fig and Fig. 49. In this embodiment, four pistons 530 are pivotally connected to the slider 540 via connecting links 542. These pistons form an oblique cross configuration. Adjacent pistons can be oriented at an angle of 90 ° to each other, as shown in Fig. 50, but uneven distribution of the pistons is also possible. Each of the connecting links 542 is made by providing with its help a hinged connection of the corresponding piston 530 with the slider 540. The slider 540 is configured to perform movement in harmonic law in the vertical direction and to prevent movement in other directions, provided by means of guides 520 and 522.

On Fig shows a device 600, which is similar to the device illustrated in Fig.48 - Fig, in that it has two crankshafts 602 and 604, which are made with the possibility of joint rotation. There is a cross-shaped connecting means 606, which is installed on the bearings 608 and 610 of the lower end of the connecting rod related to the crankshafts. There are four pairs of connected pistons 612, 614, 616 and 618 mounted respectively on the branches 620, 621, 622 and 623 of the connecting means 606. Each of these branches together with the associated pair of pistons forms an assembly equivalent to the device illustrated in FIG. 48 . In preferred embodiments of the invention, adjacent branches of the connecting means are oriented at an angle of 90 ° to each other, but this is not a prerequisite. It is not a prerequisite that one of the supports of the lower end of the connecting rod should be installed in the center of the connecting means. In preferred embodiments of the invention, two crankshafts 602 and 604 are located on opposite sides from the center of the connecting means 606.

On Fig shows another embodiment of the invention, which includes a two-cylinder device 700 with opposed pistons 702, arranged to perform reciprocating motion inside the cylinders 704. The pistons 702 are rigidly interconnected using a connecting link 706, resulting in the possibility of their joint movement. A crank 708 is mounted between the pistons and rotatable about an axis 710. The crank 708 has a circular disk 712, the center 714 of which is offset from the axis 710. Thus, when the crank 708 is rotated, an eccentric movement is ensured, which can be decomposed into horizontal and vertical vibrations. directions. Two follower elements 716 are mounted on the connecting link. These follower elements 716 are adapted to be supported on vertical surfaces 717 related to the connecting link 706, and with the possibility of moving relative to the connecting link 706 in the vertical direction, but without the possibility of movement in the horizontal direction. The tracking elements 716 have curved surfaces 720 configured to interact with the periphery of the disk 712.

On Fig shows a single-cylinder device 730, which is a disk internal combustion engine. Essentially, this device is similar to the device illustrated in FIG. 52, in which one cylinder is removed, therefore, the same numerical designations are used for similar components. The main bearing 732 of the crank 708 has a split element 734. This split element 734 is located in the groove of the piston structural unit and is designed to help stabilize this structural unit. The main axis of the crank is indicated by the letter "A".

On Fig shows a two-cylinder device 800, having two pistons - piston 802 and piston 803, which are oriented at an angle of 90 ° to each other. However, this is not a prerequisite, the angle may be different. The pistons 802 and 803 are not located in the same plane, but are offset relative to each other along the axis 804 of the main crank 806. The main crank 806 has a cylindrical eccentric 808. The first piston 802 has two arms - a shoulder 810 and a shoulder 812 located on opposite sides of the cylindrical eccentric 808 On these arms 810 and 812, tracking elements 814 are mounted which are adapted to interact with the cylindrical eccentric 808 and convert the vibrational motion of the cylindrical eccentric 808 into a reciprocating movement parallel to about the axis of the cylinder 816. The second piston 803 has a similar pair of shoulders (not visible in the drawing) on which the tracking elements 820 are mounted. These tracking elements are also configured to convert the oscillatory motion of the cylindrical eccentric 808 into a reciprocating motion along the axis of the cylinder 822. This the device also has guide elements that are configured to interact with the pistons in order to create restrictions for lateral movement of the pistons.

On Fig shows a four-cylinder internal combustion engine 830 having two pairs of connected piston structural units 832. Each of the piston structural units 832 has a piston 834, rigidly connected to the other piston of the same unit using a connecting link 838. Pistons 834 of each structural unit are made with the possibility of making a reciprocating movement inside the cylinders 836.

Each connecting link 838 has a groove 839 oriented in a vertical plane passing through the connecting link 838. Each groove 839 has parallel vertical end walls 841, and in each of the grooves there is a slider 844 having parallel vertical end walls 846. Each of the sliders 844 made with the possibility of making movement in relation to the corresponding groove 839 in the vertical direction.

The crank 840 is oriented horizontally with the passage through the connecting links 838 and the sliders 844. Each of the sliders 844 has a circular hole 848, made with the possibility of passage through it of the crank. The crank 844 has a round cam 842, which has a size corresponding to the size of the hole 848. The center of the cam is offset from the axis of the crank, and when the crank 840 rotates, the center of the cam 842 makes orbital motion around the axis of the crank. In this case, coercion of the slider 844 to perform movement relative to the axis of the crank in the vertical and horizontal directions is provided.

The movement of the sliders 844 in the vertical direction is useless because the sliders 844 in the vertical direction are free relative to the piston structural units, while their horizontal movement is a factor in forcing the piston structural units to oscillate in the horizontal direction according to a simple harmonic law.

This design has several advantages over the known similar designs. The main advantage is that thanks to the introduction of a slider between the cam 842 and the walls of the groove 841, the elimination of point loads that would otherwise have occurred is ensured. Instead, load transfer from cam 842 to slider 844 and from slider 844 to groove 839 is provided across large surface areas.

On Fig and Figa shows a two-cylinder internal combustion engine 850, similar to that illustrated in Fig.56, therefore, similar components have the same numerical designation. In this embodiment of the invention, two sliders 852 are provided, one on each side of the cam 842. The sliders 852 are not in contact with each other, and each of them is in a “floating” state with respect to the other. In the embodiment illustrated in FIG. 56, when the slider 844 rotates relative to the groove 839, there is a tendency for it to collapse into the groove. When using a "split" slider, using two sliders 852, this unwanted tendency is prevented. By rotating one of the sliders 852 relative to the groove 839, all this rotates around the center of the cam 842.

On Fig - Fig shows a four-cylinder device 860, having a pair of pistons 862a and 862b, which are located at an angle of 90 ° to each other. Each piston has an extension 864 having end walls 868 and 870 oriented perpendicular to the axes of the respective pistons. The extensions 864, as best seen in FIG. 59, are made with the piston axis oriented in the same direction, so that the pistons of each pair can be located in the same plane perpendicular to the crank 866.

The crank 866 includes a circular eccentric cam 872, which is configured to interact with the four walls 868a, 868b, 870a and 870b. When the crank rotates, the action of the cam 872 is ensured by forcing both pistons to reciprocate in the respective cylinders, which are not shown in the drawings.

Although in the embodiment illustrated in FIGS. 58 to FIG. 60, a cam is used having a support directly on the end walls, it should be noted that a structure can be used as in the embodiment illustrated in FIGS. 56 and 57.

In Fig.61 and Fig.62 shows an embodiment of the present invention, which is a modification of the variant illustrated in Fig.58 - Fig.60, therefore, similar components have the same numerical designation.

Two sliders 880 are inserted between the cam 872 and the end walls 868a, 868b and 870a, 870b. Each slider is mounted based on the inner surface 868 of one piston and the outer surface 870 of another piston. When the crank 866 rotates, the sliders 880 are forced to drive both pistons. It should be noted that when the piston 862 moves towards the crank 866, the slider, which is supported by the corresponding end wall 870, is forced to push the piston 862 towards the crank, while when the piston 862 moves from the crank 866, another the slider 880, having a support on the inner wall 868, to push the piston in the direction from the crank. As in the embodiment illustrated in FIG. 57, the likelihood of collapse is reduced since each slider is supported by only one end wall of the corresponding piston.

On Fig shows a two-cylinder device 882 with a V-shaped arrangement of cylinders, similar to the device illustrated in Fig.58 - Fig.60, in which the cam has a support directly on the end walls of the pistons. Similar parts have the same numerical designations. To help stabilize the pistons 8 62, guides 884 are provided that are designed to interact with both sides of the extensions 864 to prevent the piston from moving sideways from the corresponding axis of the cylinder.

On Fig shows a two-cylinder device 890 with a V-shaped arrangement of cylinders having inlet channels I / P and outlet channels O / P. Each extension 864 is provided with a longitudinal groove 892 made with the passage of the crank 866 through it. The groove 892 is configured to provide longitudinal, but not transverse, movement. If desired, a sliding unit can be installed on the crank, designed to interact with the walls of the groove.

On Fig shows a two-cylinder internal combustion engine 910 with a triangular connecting rod, the pistons 912 which are located opposite each other. The crank 914 has a support for the lower end of the connecting rod 916, on which a slider assembly 918 is mounted, which is slidable along the guide surfaces 920 and 922 when the crank 914 is rotated, while forcing the pistons to move in the horizontal direction. The slider assembly includes two separate parts — part 924 and part 926. These two parts 924 and 926 are configured to interact with guide surfaces 920 and 922, respectively. The gap between the parts 924 and 926 in the considered embodiment is oriented at an angle of 30 ° to the vertical, but this is not a prerequisite, the angle can be any other.

On Fig shows a cross-shaped internal combustion engine 930 with a triangular connecting rod, having two piston assemblies - a piston assembly 932 and a piston assembly 934. There is a "split" slider assembly 936, which is configured to interact with the sliding surfaces of both piston assemblies. The slider assembly includes two parts - part 938 and part 940, which are both configured to interact with both piston assemblies. However, this interaction consists only in the contact of each part with one sliding surface of each piston assembly.

Fig. 67 shows a two-piece slider assembly 942 mounted on a support of the lower end of the connecting rod 944 on the crank 946. Although the slider assembly is divided into parts 948 and 950, these parts are rigidly interconnected by screws 952, as a result of which the slider assembly can be considered a single body.

68 shows a slider assembly 954 mounted on a support of the lower end of the connecting rod 956. This slider assembly has two components — component 958 and component 960, each of which is mounted on one side of a groove in an internal combustion engine with triangular connecting rod. Each of these component parts has a clamp 962 made around the support of the lower end of the connecting rod, ensuring that the corresponding component can rotate around the support of the lower end of the connecting rod independently of the other component. It should be noted that this clamp can be made separately from the body 964 of the component and attached with screws or other suitable means.

On Fig shows a slider unit 965, including two component parts 966 mounted on the cam 968. Each of the component parts 966 is configured to interact with one side of the guide groove of the piston unit. Each of the components 966, in turn, includes two parts - part 969 and part 970, interconnected by connecting links 972. The connecting link 972 can be connected to each of the fastened parts rigidly or pivotally.

On Fig shows a part of one side of the slider unit, in which two parts - part 969 and part 970 belonging to the component part of the slider unit are interconnected pivotally along the axis 974.

71 shows one part of a slider assembly including a component 976 configured to interact with an eccentric cam 978. This component has a main body 980 and rollers 982 that are configured to interact while in a normal state with a groove surface 984 and with the possibility of maintaining the main body 980 above the surface 984. When the eccentric cam 978 rotates, it is ensured that the component 976 performs movement along the surface 984 with a variable speed. The distance between the main body 980 and the surface 984 is small enough so that at high speed of the main body 980 it is ensured that it glides along the oil film in the "floating" mode, and at low speed it is supported by rollers 982.

On Fig shows a slider unit in which the component 986 is configured to interact with the cam 988 through the rollers 990.

On Fig shows a composite slider assembly 992, including parts 993 and 994, made with the possibility of interaction with one side of the groove 995. These two parts are interconnected by jumpers 996 and 997, which are made with the ability to accurately follow the surface of the cam 998 in order to facilitate maintaining the hydrodynamic lubrication of the sliding surfaces on the cam. There are connecting links L, which can be attached to the parts of the structure connected by them rigidly or pivotally.

74 shows a slider assembly 1000 including two components — component 1002 and component 1004 located on opposite sides of cam 1006. There are connecting links 1008 configured to connect adjacent ends of components 1002 and 1004. These connecting links can be attached to the parts connected by them rigidly or pivotally.

On Fig shows a slider assembly 1012, including a connecting link 1010, pivotally attached to two parts connected to them at points located opposite each other diagonally.

On Fig shows a crank 1014 having a first cam 1016, which has a circular shape and is configured to interact with two parts of the slide - part 1018 and part 1020. There is also a second cam 1022, which is located next to the first cam 1016 or is superimposed on the first cam 1016 and is configured to interact with a tracking element 1024, which is mounted on the corresponding component, once for each revolution of the crank.

On Fig shows a slider assembly consisting of two parts 1031, each of which has a sliding surface 1030, made with the possibility of interaction with the surface 1032. In addition, each component 1031 is equipped with a roller 1034, through which mediated interaction of the corresponding component with a surface with a profiled surface 1036 related to the piston assembly, in such a way that the piston assembly is forced to move away from the crank.

78 shows a slider and a piston assembly having sliding surfaces 1044 and 1046, respectively. The piston assembly has profiled surfaces 1048 that are adapted to interact with servo elements 1050. These servo elements 1050 are connected to pistons 1052 on a slider so that grease can be pumped out if necessary. It should be noted that the sequence of the profiled surface - the tracking element - the pistons can be made reverse, so that the profiled surface can be performed on a slider.

Fig. 78a shows a crank 1060 that has a first cam 1062, which is the main cam and has a circular shape configured to interact with the slider assembly constituent parts 1064. Each of these constituent parts 1064 has a cam follower 1066. These cam the tracking elements 1066 are configured to periodically come into contact with the second cam 1068 when the crank is rotated.

On Fig shows a device, which is a modification of the device illustrated in figa, in which the cam follower element 1066 is made with the possibility of driving a pump 1070, designed to periodically supply oil to various bearing areas.

On Fig shows a structural unit of a fluid device with a triangular connecting rod, including a slider 1072 made in the form of a single body mounted on a support 1074 of the lower end of the connecting rod. The slider 1072 is equipped with an oil pump, which is configured to intermittently engage with a cam 1078 located on the crank. The letter "V" indicates the surface of the cam, and the letter "N" is the cam follower connected to the piston S, the letter "X" indicates the channel for lubrication.

It should be understood that in other embodiments of the invention, different types of sliders and the engagement means used with them can be used in any combination possible and practical for practical reasons, and that this variety is not limited to use only with such components as are shown in the specific drawings. .

On Fig - Fig illustrates a two-cylinder liquid device 2010 with a V-shaped arrangement of cylinders (fully shown in Fig, partially in Fig), two pistons 2012 which are made with the possibility of reciprocating movement inside the cylinders 2014, which are oriented at an angle of 90 ° to each other, which is not a prerequisite, the angle may be different. There is a connecting tool 2016, which is installed with the possibility of rotation on the support of the lower end of the connecting rod on a crank (not shown) and with the possibility of sliding relative to two pistons 2012.

Each of the pistons 2012 has a groove 2018 T-shaped, made diametrically across the piston. The connecting means 2016 is equipped with the corresponding T-shaped protrusions 2020, made with the possibility of engagement with the grooves 2018. Each of the protrusions 2020 has a composite structure - it has two parts - a transverse plate 2024, which forms the transverse shoulders of the protrusion, and a longitudinal plate 2026, which are fastened between by itself using screws 2028.

On different sides of the groove 2018 are two plates 2030, oriented in the axial direction. These plates 2030 are located diametrically opposite each other and are oriented perpendicular to the groove 2018, while they are made without going beyond the piston zone. Plates 2030 are made integral with the piston body.

The considered liquid device has a series of U-shaped guides 2032, which are configured to interact with the plates 2030, as can be seen in Fig and Fig. 84. The guides 2032 are rigidly mounted on the crankcase (not shown), and thus they are used to limit the swing of the pistons when they make a reciprocating movement inside the respective cylinders.

In preferred embodiments of the invention, these guides are located on the crankcase, on which their position is adjusted using a positioning pin 2034 and to which they are attached using screws installed in holes 2036.

Guides 2032 are designed to limit the movement of the pistons both parallel to the groove 2018 and in the direction perpendicular to it, so that, if desired, the possibility of reducing the piston skirt can be provided.

The plates 2030 are located on opposite sides of the groove, and not at one or both of its ends, so there is no need for the size of the crankcase to be larger than conventional crankcases known from the prior art. In addition, due to the fact that the plates 2030 are made with a strike within the zone of the piston, the known crankcase can be relatively easily adapted to accommodate the crank and the piston assembly.

The plates and groove 2018 can be made integral with the piston 2012 and from the same material as the piston. But in an alternative embodiment, the above components can be made as separate parts, and the piston assembly can be assembled from these parts. In preferred embodiments of the invention, the bearing surfaces of the groove 2018 and the plates 2030 are subjected to appropriate processing in order to ensure their wear resistance, or provided with separate wear-resistant inserts and / or overlays. It should be understood that oil must be supplied to the bearing surfaces through the lubrication channels or by pouring in oil.

On Fig - Fig 126 shown in bottom view of various variants of the piston plates or vertical guide means that can be used with the connecting means 2016 shown in Fig and Fig. 84. The guides used as analogues of the guides 2032, corresponding to the vertical plates 2030 on each of the pistons shown in Figs. 81 - 84, are not always shown in this group of drawings, but it should be understood that these guides must have a shape corresponding to the surface of the plates .

On Fig shows a piston 2040 having one axial plate 2042. The plate 2042 is oriented perpendicular to the groove 2018 and thus made with a strike along the radius line. In addition, the plate 2042 is made with a strike beyond the periphery of the piston. The plate 2042 may be integral with the piston or may be made as a separate part.

Fig. 86 shows a piston 2044 having two parallel plates 2046 oriented perpendicularly to a groove 2018 along a diameter line. The plates 2046 are made to extend beyond the piston channel with the possibility of interaction with the guides 2032. Each plate is a separate part and introduced into the axially oriented groove 2048 made on the piston.

On Fig shows the piston 2050, having two made in the form of separate parts, and not at the same time, the plate 2052, which are inserted into the grooves 2054 made in the piston. The rest of this design is similar to that illustrated in Fig and Fig.

On Fig shows the piston 2056, the design of which is similar to that illustrated in Fig and Fig, except that the plate 2058 is made with a strike outside the channel of the piston.

89 shows a piston 2060 having axially oriented grooves 2062 into which axially oriented plates 2064 mounted on a crankcase are inserted.

On Fig shows a piston 2066 having an axially oriented plate 2068, which is located at one end of the groove 2018 and is engaged with the U-shaped guide 2070.

On Fig shows the piston 2072 having one made at the same time the plate 2074.

92 shows a piston 2076 having three plates — 2077, 2078 and 2079. The plate 2077 is oriented perpendicular to the groove 2018 along the center line of the piston 2076, and the plates 2078 and 2079 are oriented perpendicular to the groove extending from the opposite side to the plate 2077. Plates 2078 and 2079 are located at a distance from each other with a strike towards the ends of the groove 2018. All three plates are made with strike outside the periphery of the piston.

On Fig shows a piston 2080, similar to that illustrated in Fig, except that the two plates 2078 and 2079 are located much closer to each other and are oriented towards the center of the groove 2018. In addition, the unpaired plate 2077 is made without leaving out of the piston area.

On Fig shows the piston 2082, having two protrusions 2084 of a T-shaped section, which are diametrically opposite to each other and directed in different directions perpendicular to the groove 2018.

On Fig shows a piston 2086, similar to that illustrated in Fig, but with only one protrusion 2088 T-shaped section, which is made with a strike from the middle of the groove 2018.

96 shows a piston 2090 having two T-shaped protrusions 2092 that are offset from the center of the groove 2018. In this embodiment, this offset is symmetrical about the center of the piston, but this is not a prerequisite.

On Fig shows the piston 2094, similar to that illustrated in Fig, except that the protrusions 2096 of the T-shaped section are made without going beyond the zone of the piston.

FIG. 98 shows a piston 2098 having axially oriented protrusions 20100 of a Y-shaped cross section that extend with a strike from the center of groove 2 018.

On Fig shows the piston 20102, having two plates 20104, made with a strike from the center of the groove 2018, but not perpendicular to it, but with an angle of 45 °.

On Fig shows a piston 2072, similar to that illustrated in Fig, except that in this embodiment there are two made at the same plate 2074.

101 shows a piston 20105 having four plates 20106 that are oriented perpendicular to the groove 2018. Each of the plates is engaged with a guide member (not shown).

On Fig shown piston 20107, which has two pairs of protruding elements 20108 L-shaped section, with the arrangement of the elements of each pair is such that between the elements are formed grooves 20110 T-shaped section into which the guide elements of the T-shaped section ( not shown).

FIG. 103 shows a piston 20112 having two cheeks 20114, each of which has a concave surface 20116 designed to interact with a guide element of a complementary shape. The profile of concave surfaces 20116 may be elliptical, circular, or other shape.

104 shows a piston 20118 having two cheeks 20120 with convex surfaces 20122. The profile of these convex surfaces 20122 may be elliptical, circular, or some other shape.

105 shows a piston 20124 having two cheeks 20126, similar to that illustrated in FIG. 104, but whose cheeks 20126 are offset in opposite directions from the center of the groove 2018. This offset can be either symmetrical or asymmetric.

106, a piston 20128 is shown having two cheeks 20130 that have convex surfaces 20132. A cut 20134 is made from each convex surface 20132 towards the center of the groove 2018.

107 shows a piston 20136 oriented perpendicular to the groove 2018. Both plates 20138 are offset from the center of the piston and are located opposite each other.

On Fig shows the piston 20140, having two cheeks 20142, made with an extension in the axial direction. Each cheek has a wavy surface 20144 configured to interact with a corresponding guide surface. The cross-section of these undulating surfaces 20144 may be a wave-like curve composed, for example, of circular or elliptical arcs, but may also have any other suitable shape. This form can be both correct and irregular.

On Fig shows the piston 20146, similar to those illustrated in Fig and Fig, in that it has plates 20148, in which the cross section is a rectangle. However, the plates 20148 are not made with the possibility of interaction with the walls of the groove 2018 and are not made along with it. Plates 20148 are oriented away from the bottom of piston 20146.

110 shows a piston 20150 having two cheeks 20152 that are oriented from the main body of the piston and are made separately from the walls of the groove 2018. Each cheek is formed by two plates — plate 20153 and plate 20154, which are oriented relative to each other at an angle of 90 ° . It should be noted that they can be oriented at a different angle.

FIG. 111 shows a piston 2072 similar to that illustrated in FIG. 100, except that in this embodiment, the plates 20155 are projected beyond the projection (end view) of the piston 2072.

FIG. 112 shows a piston 20156 having two cheeks 20158 made axially extending. The cross section of these cheeks is mushroom-shaped.

FIG. 113 shows a piston 20160 having two plates 20162 made axially extending without being able to interact with the walls of the groove 2018.

On Fig shows the piston 20166, similar to the piston illustrated in Fig, but having, in contrast to the piston 20160, four plates 20168, made with an axial extension. Two plates 20168 are located on one and the other side of the groove 20188. In preferred embodiments of the invention, these four plates are located symmetrically with respect to the center of the piston.

FIG. 115 shows a piston 20170 having two pairs of guide cheeks. The first pair 20172 is made with a strike from the lower part of the main body of the piston and has an outer surface 20174, the cross section of which has the form of a circular or elliptical arc. The second pair 20176 is made with a strike from the cross-section of the outer surface of the piston.

FIG. 116 shows a piston 20178 having four axial guide plates 20 0180 made with a strike from the outer surface of the piston having a circular cross-sectional shape.

On Fig shows a piston 20182 having a guide element 20184, essentially representing a rod, which is oriented in the axial direction. Guide element 20184 is installed on the outer surface of the piston or is made integral with it.

FIG. 118 shows a piston 20186 similar to that illustrated in FIG. 90, except that in this embodiment there are two guide plates 20188 at one end of the groove 2018.

On Fig shows a piston 20190, having two guide cheeks 20192, made with an axial strike and with a departure from the walls of the groove 2018 as a whole in the radial direction. Each of the guide cheeks 20192 has a wavy side surface 20194. The shape of these wavy surfaces can be any.

FIG. 120 shows a piston 20196 having three guide plates — a plate 20197, a plate 20198 and a plate 20199. The guide plate 20197 is perpendicular to the groove 2018 and the plates 20198 and 20199 are oriented from the groove 2018 with diverging in different directions. In preferred embodiments of the invention, all three plates are made radially extending from the groove 2018.

On Fig shows a piston 20200 having only one guide element 20202, made with a strike in the axial direction. The guide member 20202 has concave lateral surfaces 20204 and a flat outer surface 20206. In preferred embodiments of the invention, the surface 20206 is parallel to the groove 2018.

FIG. 122 shows a piston 20207 having three guide members — a guide member 20208, a guide member 20210, and a guide member 20212 that are axially extended. The guide element 20208 in the cross section has a simple rectangular shape, the guide element 20210 in the cross section is F-shaped, and the guide element 20212 consists of a central plate and ribs 20216 and 20218 formed from the side that extend away from it. The ribs 20216 and 20218 can be both the same and different sizes.

123 shows a piston 20220 having at least two rollers 20222 mounted on opposite sides of the groove 2018 on the axial studs 20224. The rollers 20244 are in cooperation with an axially oriented guide element 20226 mounted on the crankcase. A piston can have two or more rollers on either side of the groove 2018.

FIG. 124 shows a piston 20228 having two hollow rectangular elements 20230, made axially extending and located on opposite sides of the groove 2018. These hollow elements 20230 are open at least from one end and are arranged to have guides therein. rods mounted on the crankcase.

125 shows a piston 20232 having triangular section guiding elements 20234 made with axial strike and located on opposite sides of groove 2018.

FIG. 126 shows a piston 20236 having a guide member 20238, the cross section of which has angular recesses 20240 on each side.

Fig.127 - Fig.129 shows a piston 20242 having a vertically oriented guide rail 20244 and a horizontally oriented slider 20246. The guide rail 20244 is made to extend from the lower surface of the main body 20248 of the piston 20242. The horizontal slider 20246 is mounted on the inner (facing to to the center of the piston) of the lateral surface of the guide rail 20244. The horizontal slider 20246 is configured to interact with a suitable gearing means available on the connecting means, while the tub vertical guide rail 20244 is configured to interact with a suitable guide surface present on the crankcase.

130 to FIG. 132, a piston 20250 is shown having a vertical guide member 20252 and a horizontal member 20254. The horizontal member 20254 has a female groove 20256 for sliding to engage with a corresponding protrusion on the connecting means.

FIGS. 133 - FIG. 135 show a piston 20258 having a main body 20260. Using a piston pin 20262, the engaging means 20264 is rotatably connected to the main body 20260. This engaging means includes a horizontal part 20266 and a vertical part 20268. The horizontal part has a groove 20270, configured to locate a corresponding protrusion on the connecting means with the possibility of sliding, and the vertical part 20268 is configured to interact with the guide element installed and the crankcase. It should be noted that the vertical part is made with a strike both above the horizontal part and below it.

In Fig.136 - Fig.138 shows a piston assembly 20272 having a horizontally oriented element 20274 Z-shaped section, which is configured to interact with the corresponding surface on the connecting means, with the possibility of sliding. There are also guide elements 20275 configured to interact with the guide elements on the crankcase.

In Fig.139 - Fig.141 shows a piston assembly 20276 having a vertical guide element 20278, made with a strike from the base of the main body 20280 of the piston. There is also a horizontal member 20282 that is mounted on the main body 20280 independently of the vertical guide member 20278.

Fig.142 - Fig.144 shows a piston assembly 20283 having a main body 20284 and a guiding means 20286, configured to also perform the functions of the engagement means mounted on the main body using pins or screws 20288. The guiding means 20286 has two vertical guiding elements 20290 and cross member 20292. On the cross member 20292 there is a T-shaped engagement element 20294 oriented perpendicular to the plane of two vertical guide elements 20290. This engagement element 20294 is made with possibly interaction with the connecting means.

In Fig.145 - Fig.147 shows a piston assembly 20296, similar to that illustrated in Fig.142 - Fig.144, having a similar guide means 20300, configured to also perform the functions of the gear mounted on the main body 20298 of the piston 20296 The guiding means 20300 is mounted on the main body 20298 by means of a piston pin 20302, which is arranged to extend in the plane of two legs 20290. The guiding means 20300 is rotatable about the axis of the piston pin 20302.

In Fig.148 - Fig.150 shows a piston assembly 20304 having a main body 20306, on which a guide means 20308, having an H-shaped cross section is mounted. The guiding means 20308 is attached to the main body 20306 by means of pins 20310. On the cross member 20309, related to the guiding means 20308, the engagement element 20312 is mounted with horizontal extension. The engagement element 20312 is attached to the cross member 20309 with the help of a stud 20314 that can be rotated about this axis hairpins. The engagement member 20312 has a T-shaped groove 20316 for locating therein the corresponding protrusion of the T-shaped section present on the engagement means.

FIGS. 151 to FIG. 153 show a piston assembly 20318 having a guiding means 20320 configured to also perform the functions of an engaging means attached to the main body 20322 by means of a stud 20324. There is a cross member 20326 made with a strike between the vertical elements 20328 and having Groove 20330 T-section.

FIGS. 154 - FIG. 156 show guide means 20332, also adapted to perform meshing functions, having a cross member 20334, four vertical guide elements 20336 and a central connecting element 20338. Two guide elements 20336 are located on different sides of the cross member 20334. Cross member has a groove 20339 T-shaped section.

In Fig.157 - Fig.159 shows the guiding means, which also performs the function of means of engagement, similar to that illustrated in Fig.154 - Fig.156, with the difference that the cross member 20340 is not provided with a groove of a T-shaped section, and has a T-shaped section.

In Fig.160 - Fig.162 shows the guiding means 20342, which also performs the function of the engagement means, similar to that illustrated in Fig.157 - Fig.159, with the difference that it is attached to the body of the piston 20344 with two studs 20346 so that cranking is excluded.

Fig.163 - Fig.165 shows a piston assembly 20350 having a guide means 20352, configured to also perform the functions of the means of engagement, mounted on a stud or cross member 20354 of the body of the piston 20356. The stud or cross member 20354 can be made as a separate part, and at the same time with the body of the piston 20356. The retention of the guiding means on the cross member 20354 is provided by means of a screw 20358.

In Fig.166 - Fig.168 shows the guiding means 20360, which also performs the function of the means of engagement, similar to that illustrated in Fig.154 - Fig.156, with the difference that the retention of this tool on the body of the piston 20362 is provided with two hairpins 20364.

In Fig.169 - Fig.171 shows the piston assembly 20366, functionally identical to that illustrated in Fig.166 - Fig.168, but with the difference that it has only one unitary structure and only one vertical guide element 20368 on each side of the horizontal engagement element, not two.

In Fig.172 - Fig.174 shows the piston assembly 20370, similar to that illustrated in Fig.127 - Fig.129, but with the difference that it has a horizontal groove 20372 designed to engage with the connecting means.

In Fig.175 - Fig.177 shows a piston assembly 20374 having only one vertical guide element 20376 and an engagement element 20378 T-shaped, made with a branch from the guide element 20376.

In Fig.178 - Fig.180 shows a piston assembly, functionally identical to that illustrated in Fig.130 - Fig.132, but with the difference that the surrounding groove 20380 is much closer to the body of the piston 20382.

In Fig.181 - Fig.183 shows a piston assembly 20450 having two vertical guide elements 20452, made with a strike from the body of the piston 20454. There is a cross member 20456, which is installed with recession in the guide elements 20452 and is made with a strike in the horizontal direction. This cross-member has an enclosing groove 20458, configured to accommodate a corresponding protrusion therein on the connecting means.

In Fig.18 - Fig.186 shows a piston assembly 20460 having a piston body 20462 and a guiding means 20464, configured to also perform the functions of the means of engagement. This guiding means 20464 includes a T-shaped in cross-section engagement element 20466, which has a cross member 20468, in which a groove 20470 of the L-shaped section is made, designed to accommodate a corresponding protrusion having a L-shaped cross section located on the connecting means. There is a vertical guide element 20442 connected to the body of the piston 20462. In preferred embodiments of the invention, the guide element 20472 is integral with the engagement element 20466, but this is not a prerequisite, it can be made as a separate part. In preferred embodiments of the invention, the guide member 20472 is made to extend to a level below the horizontal cross member 20468.

In Fig.187 - Fig.189 shows a piston assembly 20474 having a piston body 20476 and a guiding means 20478, made with the possibility of performing the functions of the gearing means, which is attached to the body of the piston 20476 with a piston pin 20480 with the possibility of rotation around the axis of this piston pin . The guide means 20478 has a T-section, including a vertical leg 20482 and a horizontal cross member 20484. This horizontal cross has a T-section groove 20486 made in the side wall 20488 with the possibility of accommodating a corresponding protrusion on the connecting means.

In Fig.190 - Fig.19 shows a piston assembly 20490 having a piston body 20492 and four vertical parallel guiding elements 20494, made with the strike down.

These four guiding elements 20494 are located at the corners of a square whose center coincides with the center of the circumference of the piston.

There is a gearing means 20496, which is mounted on a piston, to which is attached with a piston pin 20498 with the possibility of rotation around the axis of the latter and is located between the vertical guiding elements 20494. The gearing means includes a flat cross member 20500, made with the possibility of introducing into the groove of the T-shaped section, made on a connecting tool.

In Fig.19 - Fig.195 shows a piston assembly 20502 having a piston body 20504 and a guiding means 20506, configured to also perform the functions of the gear attached to the body of the piston 20504 with two studs 20512. The guiding means 20506 has a shaft 20510 and the first a cross member 20512 having four vertical guiding rods 20514 - one in each of its corners. On the underside of the first cross member 20512, a second cross-section 20516 of a T-section is installed, which is configured to interact with a corresponding T-section groove made on the connecting means.

FIG. 196 shows a reciprocating piston device 3010 having a crank 3012, pistons 3014 configured to reciprocate within the cylinders 3016, and a connecting mechanism 3018 mounted to rotate on a lower end support 3020 of the connecting rod associated with the crank 3012. . The connecting mechanism 3018 is configured to interact with the intermediate elements 3022. The connecting rods 3024 are configured to connect the intermediate elements 3022 to the corresponding pistons 3014, while the connecting rods 3024 to the corresponding pistons 3014 and the intermediate elements 3022 are pivotally connected.

Each intermediate element 3012 has a slider arm 3026 installed in the slider 3028. The slider 3028 is formed with a straight groove parallel to the axis 3030 of the corresponding cylinder. Thus, the movement of the intermediate element 3022 is limited to only parallel to the axis 3030 of the cylinder. The connecting mechanism 3018 has a restriction in movement relative to the intermediate elements 3022, while the direction of its movement is perpendicular to the axis 3030 of the cylinder, and when the crank 3012 is rotated, the pistons 3014 are forced to move according to the correct sinusoidal law.

In Fig.197 shows an embodiment of the invention, similar to that illustrated in Fig.196, therefore, similar components have the same numerical designation. In the embodiment illustrated in FIG. 179, the intermediate elements 3022 are adapted to interact with sliders 3040, which are interconnected on a common axis 3042. This common axis is located on a line passing through the crank axis 3044 and being the bisector of the angle between the axles 3030 two cylinders. The sliders 3040 are rotatable about a common axis 3042, so that the axes 3046 of the sliders are not necessarily parallel to the axes 3030 of the cylinders. When the sliders rotate around a common axis, the intermediate elements are forced to move to a certain angle towards the respective axes of the cylinders, thereby ensuring a decrease in the effective stroke of the pistons of the device. Lateral movement of the intermediate elements 3022 relative to the pistons is ensured by the articulation of the corresponding connecting rod 3024 with the piston on one side and with the intermediate element 3022 on the other side. The effect of this movement is to introduce a secondary sinusoidal movement due to the aforementioned lateral movement superimposed on the main sinusoidal movement due to the rotational movement of the crank 3012.

In Fig.198 shows an embodiment of the invention, similar to that illustrated in Fig.197, but with the difference that the sliders 3040 are installed on separate axes - axis 3050 and axis 3052. As in the embodiment illustrated in Fig. , during the rotational movement of the sliders 3040 around their axis of rotation 3050 and 3052, coercion is provided to change the stroke length and the nature of the movement of the pistons 3014.

On Fig shows a modification of the previous version, in which the intermediate elements 3022 are made with the possibility of interaction with a unitary slider 3060, which is mounted on the axis 3044 of the crank with the possibility of rotation around it. Otherwise, the operation of this device is identical to the embodiment illustrated in FIG.

On Fig shows another variant of the device according to the invention, in which the intermediate elements 3022 are installed in the sliders 3062, which are mounted on the axles 3064 with the possibility of rotation around them. Like the devices illustrated in FIGS. 179 and 198, when the sliders 3062 are rotated, coercion is provided to change the nature of the movement and the stroke length of the pistons.

On Fig shows a variant of the device according to the invention, which has a composite piston 3070, including an external piston 3072 and an internal piston 3074. The external piston 3072 is equivalent to the piston 3014 from the previous embodiment. The inner piston 3074 is slidably mounted inside the outer piston 3072 with the possibility of moving parallel to the axis of the cylinder. There is a connecting system 3076, made with the possibility of connecting the internal piston 3074 with a secondary slider element 3077, which is installed in the secondary slider 3078. Both sliders, primary and secondary, are pivotally mounted on separate axes - axis 3080 and axis 3082 independently of each other.

When the axes of the primary and secondary sliders are parallel, the internal piston 3074 is not able to move relative to the external piston. When these axes are not parallel, it is possible to move the internal piston relative to the external piston during rotation of the crank, while the movement of the slide elements along the respective sliders is also provided.

It should be noted that the intermediate element 3022 is pivotally connected to the piston 3072 together with the connecting rod. To provide the necessary degrees of freedom, a separate sliding element 3084 is provided, which is articulated with an intermediate element 3022.

Two sliders also have the ability to perform lateral movement along the axis 3086, which makes it possible to change the working volume or compression ratio in the device in question. Two sliders are configured to perform this lateral movement independently of each other. The axial points in FIG. 201 are designated A, B, C, and D.

On Fig shows a mirror version of the device illustrated in Fig, in which two sliders are made without the possibility of rotation, but with the possibility of lateral movement (there are no axial points A, B, C and D shown in Fig. 201).

On Fig shows another variant of the device according to the invention, in which there is an L-shaped intermediate element 3090 mounted for rotation on the slide element 3092. The slide element 3092 is made to slide in the slider 3094, which is made to rotate around the axis 3096. The axis 3096 is not located on the axis of sliding 3098.

(The description of FIG. 204 follows after the description of FIG. 209).

On Fig shows a variant of the device according to the invention, similar to that illustrated in Fig, in which there is a connecting mechanism for the valve 3101, equipped with a tracking element 3100, which is made with the possibility of rolling along a curved groove 3102. Thus, with the movement of the follower element along the groove 3102 provides the ability to change the position of the valve 3101. The housing 3104 is mounted with the possibility of rotation around the axis 3106, which provides additional control over the valve position.

On Fig shows a variant of the device according to the invention, similar to that illustrated in Fig. 203. In the embodiment of the device shown in FIG. 207, the groove 3110 has an arc shape and has an arcuate tracking element 3112 that is slidable along the groove 3110. The housing 3114 is rotatably mounted about an axis 3118 to which it is connected via an eccentric 3116. This it is possible to change the lateral position of the groove 3110. The radius of curvature of the groove 3110 can be any.

On Fig shows another variant of the device according to the invention, which is generally similar to that illustrated in Fig. 207, but has the difference that the groove 3120 in the housing 3122 is not just arcuate, but has a more complex shape with several radii of curvature. To adapt to this shape of the groove, the slider 3124 has two sliding elements 3126, made with the possibility of rolling. Thus, when the slider 3124 moves along the groove 3120, its movement to the side relative to the axis of the cylinder is ensured. The movement of the slider 3124 relative to the intermediate elements 3022 is ensured by the articulation of two follower elements along the axis 3128.

On Fig shows another variant of the device according to the invention, in which the connecting rod 3130 is pivotally connected to the piston 3132 and the intermediate element 3134. As in other embodiments, the intermediate element 3134 is configured to perform lateral movement relative to the connecting means 3136, which is mounted on support 3138 of the lower end of the connecting rod related to the crank 3140. The intermediate element 3134 is pivotally connected to the slide element 3142 at a point 3143, which is made with the possibility of sliding in the groove 3144 made in the primary housing 3146. The primary housing 3146 is pivotally connected to the secondary housing 3148 at a point 3150. The secondary housing 3148 is configured to move along axis 3152. This axis 3152 may be perpendicular to the axis of the cylinder, but may be oriented to it and at a different angle, different from 90 °. As you can see, the intermediate element 3134 is made with the possibility of lateral movement, so that a straight line 3154, which is the connection line of points 3156 and 3158, in which the connecting rod has a pivot joint, can be oriented with respect to the cylinder axis 3159 at an angle different from 90 °.

On Fig shows a variant of the fluid device with a triangular connecting rod according to the invention, in which there is a crank 3200, connecting means 3202 mounted on the support 3204 of the lower end of the connecting rod, and pistons 3206, pivotally connected to the intermediate element 3208 using rods 3210. The intermediate element 3208 is located in the frame 3212, consisting of four elements - 3214, 3215, 3216 and 3217, which are pivotally connected to each other at points A, B, C and D. The frame has the same height as the intermediate element 3208, but the width of the frame is larger than the width of the intermediate th element 3208, making possible to lateral motion of the intermediate member 3208, and hence the pistons 3206. The frame is movable in the vertical direction. When the frame is vertically moved, the intermediate element 3208 is forced to move upward and, therefore, the connecting rods 3210 are forced to turn upward with the pistons pulled toward the center of the device. Thus, in the device under consideration, it is possible to change the compression ratio while maintaining the same piston stroke.

Fig.210 - Fig.217 shows a liquid device 4010 with a V-shaped arrangement of cylinders, having a crank 4012, made with the possibility of rotation around the axis 4013, and two pistons 4014, made with the possibility of reciprocating motion inside the cylinders 4016. Both pistons 4014 are connected to the crank 4012 by means of a single slider mechanism 4018, which is mounted with the possibility of rotation with the support 4020 of the lower end of the connecting rod related to the crank 4012. Support 4020 of the lower end of the connecting rod is made with a strike between the cheeks 4022 (one of them is shown). The slider mechanism 4018 has two cross-sectional T-shaped protrusions 4024, which are adapted to interact with the corresponding grooves 4026 (can be seen in FIG. 215) made in the pistons 4014. When the crank is rotated, the slider mechanism 4018 is forced to slide relative to the pistons 4014 and forcing the latter to reciprocate inside the cylinders.

There are two guide elements 4028 made with a strike downward from the base region of each piston. These guide elements 4028 are located on opposite sides of the slide mechanism 4018 and the groove 4026. In addition, each of these guide elements is made to extend below the groove 4026 towards the crank axis 4013. It should be noted that although in the present embodiment two guide elements 4028 per piston are used, their number may be different, for example, one or more two guide elements per piston can be used. In cases where the number of guide elements is two or more per piston, it does not matter whether they are located symmetrically with respect to the axis of the cylinder (it is also the axis of the piston). The guide elements can be located on one side of the groove 4026 or asymmetrically on both sides.

The guiding elements 4028 are in interaction with the corresponding number of guides 4030 (can be seen in FIG. 215), which are attached to or made integral with the crankcase. In this embodiment of the invention, each rail 4030 has a U-shaped channel configured to reciprocate in it with a corresponding rail 4028.

As best seen in FIGS. 216 and 217, the lower end support 4020 is supported by two cheeks 4022. Guide elements 4028 are located on the piston 4014 between the two cheeks 4022, seen from the side. In addition, as best seen in FIGS. 210 - 213, the guiding elements are made with a strike along a plane parallel to the axis of the cylinder, towards the crank axis 4013. Thus, the introduction of guide elements into the design of the device does not require an increase in crankcase volume.

When the crank 4012 rotates, the pistons 4014 are forced to reciprocate in the cylinders 4016 and, as can be seen in Fig. 210 - Fig. 211, the guiding elements 4028 are forced to move up and down with the pistons 4014 within the volume swept by the support 4020 lower end of the connecting rod.

When the piston is at bottom dead center (Fig. 210), the guide elements 4028 can be located away from the sleeve 4038 of the slide mechanism 4018, but in close proximity to it, thereby ensuring the location of the guides 4030 in the closest proximity to the volume swept by the crankshaft.

FIG. 218 shows a fluid device 5010 having a crank 5012 rotatably about an axis 5014 and having a support 5016 of the lower end of the connecting rod with an axis 5018. On the support 5016 of the lower end of the connecting rod, connecting means 5020 are mounted that can rotate on the support 5016 of the lower the end of the connecting rod around the axis 5018. The connecting means 5020 includes a straight groove 5022 configured to accommodate the engaging means 5024. This engaging means is adapted to move along the groove 5022 by cleaving lashing by rolling on rollers or otherwise.

There is a piston 5026, which is mounted on gear means 5024 or is made integral with it. The piston 5026 is located in the cylinder 5028 with the possibility of reciprocating along the axis 5030 of the cylinder.

The engagement means 5024 is in the shape of a triangular loop, and the connecting means 5020 is positioned so that the straight groove 5022 is always positioned so that the axis 5018 of the lower end support of the connecting rod is between the linear groove 5022 and the piston 5026. The piston 5026 can only move along axis 5030 of the cylinder, and when the crank 5012 rotates, the straight groove 5022 is held in a horizontal position, while the connecting means 5020 are allowed to move in both the vertical direction (with the movement of the piston), and in the lateral directions relative to the gear means 5024.

Thanks to this design, it is possible to move the crank axis closer to the cylinder head 5032 than with another design.

FIG. 219 shows a variant similar to that illustrated in FIG. 218, which has the same components and the same structure, with the exception of the engagement means. Therefore, for similar components, the same numerical designations are used.

In the device shown in FIG. 219, the engagement means 5040 is not a closed loop, but open on one side. This may be convenient for assembly, but functionally this design is identical to that shown in Fig.218.

On Fig shows another embodiment of the invention, which in some respects can be considered derived from the variant illustrated in Fig. 219.

The device 5050 illustrated in FIG. 220 includes a crank 5052 rotatably about an axis 5054 and a support 5056 of a lower end of the connecting rod having an axis 5058. A connecting means 5060 is rotatably mounted on an axis 5058.

There are two coaxial cylinders 5062 in which pistons 5064 are arranged to move along a common axis 5066. The crank axis 5054 is located at a distance from the axis 5066.

Both pistons 5064 are mounted on or integral with the engagement means 5068, this engagement means is generally T-shaped and consists of a shoulder 5070 and a shaft made with a strike along the axis 5066, while the shoulder 5070 is made as a branch from this shaft . In preferred embodiments of the invention, the shoulder 5070 is oriented at an angle of 90 ° with respect to the axis 5066, but this is not a prerequisite. In addition, in preferred embodiments of the invention, the shoulder 5070 is located between the pistons 5064 approximately in the middle, but this is also not a prerequisite.

The shoulder 5070 is configured to interact with the connecting means 5060, in preferred embodiments of the invention, by means of a sliding protrusion-groove pair (or groove), allowing the connecting means to move along the shoulder 5070. In the preferred embodiments of the invention, the shoulder 5070 is straight, but this is not a prerequisite.

The shoulder 5070 is made to extend beyond the connecting means 5060 and at its free end has a guide element 5072, which is mounted on the guide means 5074 or inside it. Guide means 5074 has a groove 5076, which is parallel to axis 5066 and is designed to provide parallel direction of movement of pistons 5064 and means of engagement 5068 of axis 5066. To stabilize the movement of pistons 5064, guide elements 5078 are also installed along axis 5066. In this embodiment, pistons 5062 are installed with the possibility of reciprocating movement on the other side of the support 5056 of the lower end of the connecting rod than the guiding means 5074.

In Fig.221, as another embodiment of the invention, a device 5080 is shown which is based on the embodiment illustrated in Fig.218, but in contrast has two coaxial pistons 5090 located opposite each other.

In this embodiment, there is a common engagement means 5082, which is configured to interact with the connecting means. In its action, this means of engagement is equivalent to two means of engagement of the device illustrated in FIG. 218, connected by means of a common transverse element 5084.

FIG. 22 shows yet another embodiment of the present invention — a device 5100, in which the pistons, crank, and cylinder arrangement are similar to those shown in FIG. 211. In this embodiment, the engagement means 5102 has a zigzag shape, and otherwise this device is functionally equivalent to that illustrated in FIG. 221.

223 and 224 show a device 6010 with a triangular connecting rod and an opposed cylinder arrangement having a crank 6012, cylinders 6014 located on opposite sides of the crank 6012, and two pistons 6016 mounted on the crank assembly 6018. The crank assembly 6018 has a groove 6020, in which a slider 6022 is arranged to slide along this groove. The slider 6022 is mounted to rotate on a support 6024 of the lower end of the connecting rod related to the crank. In order to avoid accumulation of parts, only half of the crank is shown, and in practice, the support of the lower end of the connecting rod is stretched through the slider 6022.

The connecting rod assembly includes two identical parts - part 6026a and part 6026b. Each of these parts has a centrally located mounting hardware 6028, on which a piston 6016, a transverse member 6030, and a longitudinal member 6032 are mounted.

The transverse element 6030 is made with a strike almost perpendicular to the axes of the cylinders, and the longitudinal element 6032 is made with a strike almost parallel to the axes of the cylinders.

There is a channel 6034, which is made in the transverse element 6030 and in the longitudinal element 6032 and in which the slider 6022 is located. At the free end 6036 of the transverse element 6030 there are holes 6038 for screw connection, and at the free end 6040 of the longitudinal element 6032 there are holes 6042, also designed for screw connection. Two identical parts are connected to the free ends 6036 of the transverse elements 6030 adapted to engage with the free ends 6040 of the longitudinal elements 6032 of the other part. The holes 6038 and 6042 of the two parts coincide in location, which ensures the fastening of the two parts using bolts 6044 and nuts 6046.

There are spacer sleeves 6048 installed in the channels for bolts 6044 and designed to prevent the tightening of bolted joints and the destruction of the groove.

As best seen in FIG. 224, the longitudinal members 6032 have closed ends 6050.

In Fig.225 and Fig.226 shows a device functionally identical to the device illustrated in Fig.223 and 224, with the difference that for both parts making up the connecting rod assembly, the end 6050 is not closed. Instead, there is a channel 6034 passing through this end. This solution facilitates the manufacture of the device, since the channel 6034 can be easily processed with a grinding wheel, and the movement of the grinding wheel will not be limited by the ends of the longitudinal element 6032. From the end 6050 of the longitudinal element 6032, it is not necessary to hold the slider 6022 in the channel 6034.

On Fig and 228 shows another variant of the connecting rod assembly. In this embodiment, the connecting rod assembly 6060 is split along the axis of the cylinder to form two identical parts — part 6062a and part 6062b. These parts are U-shaped, each of them consists of a central body 6064 and made with a branch from it in the axial direction of the shoulders 6066. Each of these parts is symmetrical with respect to a central line perpendicular to the axis of the cylinder.

On each of the opposite surfaces of the two pairs of arms 6066, holes 6068 are provided for inserting pins into them, and there are pins 6070 for fixing the assembled position of both halves of the connecting rod assembly. These two halves are fastened to each other using screws 6074 installed with passage through holes 6076, which are made at both ends of the shoulders 6066, with each screw screwed into the opposite shoulder. In the assembled state, the ends of the arms 6066 form a socket 6078 in which the piston is mounted. Due to the presence of this socket, the possibility of rotation of the piston around the axis of the cylinder is provided.

The connecting rod assembly also includes connecting elements 6080. These connecting elements are located inside the channel and have threaded pins 6082 installed in the holes 6084. The connecting elements 6080 are fastened to two halves of the connecting rod assembly using nuts 6086 and are designed to resist bending of these two halves of the connecting rod assembly. in which their flatness would be violated.

In Fig.230 - Fig.233 shows the components from which the connecting rod assembly is assembled.

FIG. 230 shows a connecting rod assembly 6090 including two different parts — the first part 6092 and the second part 6094. The first part 6092 has a transverse arm 6096, mounting hardware 6098 for installing the piston, and a central arm 6100. The ends of the transverse arm 6096 have holes 6102, designed for bolts that are designed to extend through the transverse arm 6098, and the free end of the central arm 6100 has one hole 6104.

The second part 6094 has a transverse arm 6106, mounting hardware 6108 for installing the piston, and two arms 6110 made with a strike from areas located in close proximity to the ends of the transverse shoulder 6106. The shoulders 6110 are made with a strike from the same side of the transverse shoulder 6106, and at their free ends there are holes 6112. The transverse shoulder 6106 has a Central hole 6114, designed for screw connection.

In the assembled state, the central arm 6100 is attached to the transverse arm 6106 with a screw installed with a passage through the hole 6104 and screwed into the hole 6114. The holes 6102 and 6114 can be either threaded or without thread. Three screws are required for assembly.

It should be noted that such a configuration can only be used when the support of the lower connecting rod is made without passing through the connecting rod assembly.

FIG. 231 shows another embodiment of the two-arm part 6094 illustrated in FIG. 230. This option provides the ability to connect two identical components. Component 6120 has a transverse arm 6122, mounting fittings 6124 for installing the piston, and two arms 6126 made with a strike from the same side of the transverse arm 6122. At the free ends of the arms 6126 there are holes 6128 for screw connection, and holes 6130 are provided at the ends of the transverse arm 6122. The two components 6120 can be assembled together by matching the corresponding holes 6128 and 6130 and fastened with screws screwed in or inserted through the holes 6130. Four are required for assembly re screw.

On Fig shows a variant similar to that illustrated in Fig. 231. FIG. 232 shows a connecting rod assembly component 6140, consisting of two parts — a first part 6142 and a second part 6144. The first part 6142 includes a transverse arm 6146, mounting hardware 6148 for installing the piston, and one longitudinal arm 6150. The second part 6144 corresponds to arm 6150 and is provided with holes 6152 for screw connection and holes 6154 for connection to the transverse arms 6146. Although this structure has four components, while the structure illustrates shown in Fig. 231, has only two components, however, its assembly requires the same number of screws — only four.

FIG. 233 shows a connecting rod assembly 6160 including two identical components 6162. Each of these components includes a transverse arm 6164, mounting hardware 6166 for installing the piston, and two longitudinal arms — a first longitudinal arm 6168 and a second longitudinal arm 6170. In contrast to the variants illustrated in Figs. 221 and 223, in this embodiment, the longitudinal arms 6168 and 6170 are made with stretching from opposite sides of the transverse arm 6164. At the free ends and on the bases of the longitudinal arms 6168 and 6170 there are holes 6172 and 617 4, designed for screw connections, due to which it is possible to connect the components of the connecting rod assembly.

On Fig shows a crank mechanism having a main axis 7001, including two cheeks 7002 and 7003, made with a strike beyond the periphery of the main journal 7025. Cheeks 7002 and 7003 are made with the possibility of supporting supports 7005 and 7004, each of which has its own axis. These axes of the supports 7005 and 7004 are offset by 30 ° with respect to each other. This crank assembly is used in the fluid device illustrated in FIG. 235, in which the cylinder axes are oriented relative to each other at an angle of 75 °. As can be seen from FIG. 235, the piston has a clutch surface in the form of a T-bar, and the recess is made on the connecting means, that is, the technical solution is applied inverse to that used in the previously considered options.

FIG. 236 shows another embodiment of the present invention, which is a fluid device with a triangular connecting rod, in which the pistons 7008a and 7008b are mounted with the possibility of reciprocating at angles of 90 ° relative to the main axis 7001, and at least a crank one support of the lower end of the connecting rod, which (of which) has only one axis 7010. It should be noted that the pistons are made with the possibility of only reciprocating motion along the respective directions eny designated on fig.236 letters "A" and "B", the directions A and B are oriented at 90 ° to each other. Pistons 7008a and 7008b are connected to a support (s) 7010 of the lower end of the connecting rod by means of slide means of engagement 7012.

In the present embodiment of the invention, the engagement means 7012 are centered on the axis 7010 of the support (s) of the lower end of the connecting rod. For both pistons 7008a and 7008b, engagement means 7012 are located on one side of the lower end support rod axis 7010.

FIG. 237 shows another embodiment of the present invention, which is a two-cylinder liquid device with a V-shaped arrangement of cylinders in which the pistons 7008a and 7008b are oriented from the main axis 7001 at an angle of 120 ° to each other. The direction B in this embodiment is rotated counterclockwise 30 ° from the 90 ° position from direction A. In addition, the axis 7004 of the lower end support rod is rotated counter-clockwise 60 ° from the axis 7005 of the lower end support rod. As in the previous embodiment, the support 7100 of the lower end of the connecting rod is designed to provide movement of the piston made with the possibility of reciprocating along the direction B, and the support 7110 of the lower end of the connecting rod is designed to provide movement of the piston made with the possibility of reciprocating along directions A.

It should be noted that in preferred embodiments of the invention, the pistons are configured to reciprocate with a half-wave phase shift. In this case, provided that the pistons have the same mass, the device will be perfectly balanced. It is also obvious that the crank disk and the triangular connecting rod of a two-cylinder liquid device with a V-shaped arrangement of cylinders can be balanced in the same way, and that devices with a cross-shaped arrangement of cylinders or devices with a horizontal arrangement of cylinders at an angle of 180 ° to each other can be balanced in the same way. way.

It is also clear that when designing internal combustion engines, there may be a desire to develop a fluid device with a triangular connecting rod according to the invention according to one of the options described here, but in which some imbalance is desirable. Thus, the present invention also includes devices in which the phase shift in the movement of the pistons is not exactly a quarter wave, but differs from the balanced position, for example, 10-20% or even 50% of the wave. Similar options are also included in the scope of the claims of the invention.

For the purposes of this discussion, let us assume that there is a two-cylinder internal combustion engine with a V-shaped arrangement of cylinders at an angle of 90 ° to each other, while the axes of the cylinders are directed at an angle of 45 ° from the vertical to one side or the other. Suppose that the internal combustion engine in question is configured to provide clockwise rotation, i.e., when the crankshaft is vertically positioned, the left piston is allowed to move upward, and the right piston is allowed to move downward at the same relative position inside the cylinder.

It is assumed that the internal combustion engine in question includes the following components:

- a crankshaft, the mass of which will be considered concentrated at two points, namely, in the counterweight and in the support of the lower end of the connecting rod;

- a connecting rod, the mass of which will be considered concentrated at three points, namely, in the left slider, in the right slider and in the counterweight directly under the support of the lower end of the connecting rod;

- the left and right pistons, the mass of each of which will be considered concentrated in the center of the corresponding channel at a certain distance above the corresponding slider;

- we assume that the stationary engine parts (crankcase, block, etc.) are installed rigidly and do not affect the engine balancing.

Imagine that the assembly of the internal combustion engine under consideration is as follows.

A crankshaft is installed, which itself is balanced, that is, its center of mass is located on its axis of rotation. It is clear that when mounted on the main bearing, the crankshaft is perfectly balanced.

Now a component called a "connecting rod" is added. Since the left and right slide mechanisms will be located above the support of the lower end of the connecting rod, the connecting rod must have its own counterweight located directly under the support of the lower end of the connecting rod, if we want its center of gravity to be located in the support of the lower end of the connecting rod. If a counterweight calculated from the total mass of the connecting rod is added to the crankshaft, it can be achieved that the center of gravity is located on the main axis, and then the assembled unit at this stage will be perfectly balanced.

It should be noted that the connecting rod always has the same orientation, that is, it is made with the possibility of actually “orbital” movement. Since its center of mass is on the support of the lower end of the connecting rod, it will not have any tendency to rotate when the crankshaft rotates. If the mass of the connecting rod counterweight is reduced so that the center of mass of the connecting rod is higher than the support of the lower end of the connecting rod, then the connecting rod will tend to swing when the crankshaft rotates. And if the conditions are provided under which the real swing of the connecting rod will not be allowed, then the conditions for describing it by the center of mass of the circle of the same radius will be preserved, and it will be possible to balance it perfectly with the help of the counterweight of the crankshaft.

Thus, the designer faces an alternative - either to reduce the load on the slide mechanisms by balancing the connecting rod, or to reduce the mass of the connecting rod and the mass of the counterweight of the crankshaft, thereby reducing the inertia forces in general. But preventing the rotation of the connecting rod can also be provided by other means, for example, such as a second crank mechanism.

If pistons are added now, the balancing of the device will be impaired. However, since the movement of the pistons is ensured according to a simple harmonic law with a phase shift of 90 °, the joint movement of the pistons is equivalent to the movement of one mass of the piston in a circle. Therefore, for balancing, it is enough to simply add to the crankshaft counterweight the masses calculated from the mass of one piston (taking into account the ratio of the crankshaft bend to the distance to the crankshaft counterweight), and the considered internal combustion engine as a whole will be perfectly balanced.

This can be most easily visualized by tilting the head to the left, so that the illusion of movement of the left piston in the vertical direction, and the right piston in the horizontal direction. When the left piston is at its highest point, the counterweight of the crankshaft is at its lowest point. At the same time, the right piston is in the middle of its stroke on the way to the right. As for the horizontal movement of the counterweight of the crankshaft, this counterweight is in the middle of its course on the way to the left. Therefore, the counterweight of the crankshaft can be adjusted so that accurate balancing of both pistons is ensured.

The center of mass of all moving parts of the considered internal combustion engine remains absolutely motionless. There is no influence of higher order harmonics, as is the case with known internal combustion engines. In known engines, they arise because the movement of the pistons is not according to a simple harmonic law, and the movement of the piston driven by known methods is not purely harmonic, and the movement of the piston driven by known methods is not symmetrical near the upper and lower dead points.

It should also be noted that the internal kinetic energy of the device according to the invention is also constant throughout the entire working cycle. If the angle of the cylinders is 90 °, then the total kinetic energy of the pistons is constant. This means that the mechanism has no tendency to resist rotation with a constant angular velocity.

The following is a theory justifying the balancing of an internal combustion engine with offset bearings of the lower end of the connecting rod.

The letter "A" indicates the angle between the channels of two V-shaped cylinders of the internal combustion engine.

The letter "D" indicates the angle between the lines drawn from the main axis to the bearings of the lower end of the connecting rod.

If we assume that the angle D is 2 × (A-90), then it turns out that the center of gravity of the two pistons moves in a circle, and this movement can be easily balanced by introducing a counterweight on the crankshaft.

If the connecting rods are rotatable relative to the pistons, then it can be considered that the connecting rods have a sufficiently large length, so that the movement of the pistons is ensured according to a simple harmonic law. In those cases when the connecting rods are made without the possibility of rotation relative to the pistons or if the possibility of rotation is limited by a very small value, the movement of the pistons will essentially occur according to a simple harmonic law.

The mass of rods is neglected.

Angles are considered positive when measured counterclockwise from the positive direction of the X axis.

We accept that the first channel is oriented at an angle of 0 degrees.

The second channel is oriented at an angle of A degrees.

When the connecting rod lower end support relating to the first piston is at an angle of 0 degrees (so that the first piston is at top dead center), the connecting rod lower end bearing related to the second piston is at an angle of D degrees.

Consider the general case when the support of the lower end of the connecting rod, related to the first piston, is at an angle R degrees, and the support of the lower end of the connecting rod, related to the second piston, is at an angle D + R degrees.

The X coordinate of the first piston is Cos (R) when measured relative to its middle position.

The Y coordinate of the first piston will always be zero.

The radius of the crankshaft for the second piston is also a unit of length, but in the general case, the projection of the radius on the axis of the second channel will be Cos (A-D-R).

Since interest is only a change in the position of the center of gravity of the pistons, we can assume that the coordinates of the second piston are determined from the following expressions:

X = Cos (A-D-R) × Cos (A);

Y = Cos (A-D-R) × Sin (A).

And the coordinates of the center of gravity of both pistons are determined from the following expressions:

X = Cos (A-D-R) × Cos (A) + Cos (R);

Y = Cos (A-D-R) × Sin (A) +0.

It should be noted that both must be divided by 2, but we did not do this to simplify the form of algebraic expressions.

It turns out that for any value of A, if we assume that D = 2 × (A-90), the center of gravity of both pistons moves in a circle, and this movement can be easily balanced by introducing a counterweight mounted on a crankshaft.

This can be proved by substituting in the expression above 2 × A-180 instead of D, and then we have

X = Cos (A-2 × A + 180-R) × Cos (A) + Cos (R);

Y = Cos (A-2 × A + 180-R) × Sin (A) +0.

After the transformations we have:

X = Cos (-A + 180-R) × Cos (A) + Cos (R);

Y = Cos (-A + 180-R) × Sin (A) +0;

what equals

X = -Cos (A + R) × Cos (A) + Cos (R);

Y = -Cos (A + R) × Sin (A).

Opening in each expression Cos (A + R), we have

X = -Cos (A) × Cos (A) × Cos (R) + Cos (A) × Sin (A) × Sin (R) + Cos (R);

Y = -Cos (A) × Cos (R) × Sin (A) + Sin (A) × Sin (R) × Sin (A).

Simplifying, we get:

X = Sin (A) × (Cos (R) × Sin (A) + Sin (R) × Cos (A));

Y = Sin (A) × (-Cos (A) × Cos (R) + Sin (A) × Sin (R))

or

X = Sin (A) × Sin (A + R);

Y = Sin (A) × Cos (A + R).

This is the equation for the motion of a point in a circle of radius Sin (A).

Thus, the joint movement of two pistons can be balanced by introducing one mass equal to the mass of one piston moving in a circle with a radius equal to the radius of the crankshaft times Sin (A). It should be noted that the fact that there are actually two pistons is compensated by a factor of 2, which was omitted in the above expressions for X and Y.

It should be noted that when A = 90 °, that is, when two V-shaped cylinders are located at an angle of 90 ° to each other, D = 0 °, that is, both bearings of the lower end of the connecting rod are not offset, but are coaxial. Thus, the V-shaped configuration of the device with an angle between the cylinders of 90 ° and with one support of the lower end of the connecting rod is just a special case when the angle D = 0 °.

FIGS. 238 and 239 show a connecting rod assembly 7200 and a piston assembly 7300 for sharing in a fluid device (not shown) having only one piston assembly 7300 mounted on the connecting rod assembly 7200. The connecting rod assembly 7200 has a T-shaped clutch 7202 section designed to interact by sliding with a groove having a T-shaped cross-section 7304 related to the piston assembly 7300. There is a counterweight 7204 located on one side of the journal pin 7206 of the lower end of the connecting rod and designed to partially or complete balancing weight connecting rod and piston assemblies disposed on the other side of the spigot end of a rod 7206 of the lower support. The piston assembly 7300 also includes a piston head 7302 and longitudinally oriented guide elements 7306, designed to interact with the guiding means designed to restrict the movement of the piston assembly 7300 only reciprocating along a certain straight line. It should be noted that the piston assembly is a prefabricated assembly consisting of various components fastened together with screw connections. The piston head 7302 is attached to the central node 7310 with a screw 7308; the guiding elements 7306 are attached to the central node 7310 with screws 7312.

As should be clear to the average specialist of the corresponding profile, various modifications and variations of the embodiments of the invention described above are possible without deviating from the spirit of the invention and without going beyond it.

Industrial applicability

The present invention has industrial applicability in relation to liquid machines in general, and in particular in relation to internal combustion engines and pumps.

Claims (124)

1. A fluid device with a triangular connecting rod, comprising a crank, including a support for the lower end of the connecting rod, having an axis for which it is possible to move in orbit around the main axis of the crank, a connecting means mounted on the axis of the support of the lower end of the connecting rod, at least one piston mounted with the possibility of reciprocating movement inside the cylinder along the axis of the piston and having a cross-sectional area perpendicular to the axis of the piston, the piston being provided with guide media with a flat surface arranged across the axis of the piston, the guide means being able to engage with the coupling means located on the connecting means, at least one restrictive means designed to prevent other movement of the piston than the movement along the axis of the piston, the piston guiding means is made by dissecting the piston cross-sectional area into two equal parts and at least a part of each of the restrictive means is located inside the volume swept by the cross-sectional area of the piston when moving along the axis of the piston, but not along the central line of dissection of the cross-sectional area of the piston into two equal parts, carried out using the piston guide means. 2. The device according to claim 1, in which the guiding means includes surfaces made with a strike almost perpendicular to the corresponding axis of the piston. 3. The device according to any one of claims 1 or 2, in which the restrictive means includes a pair of elements, and a straight line drawn from one element of the pair to another is perpendicular to the Central line of dissection of the cross-sectional area of the piston into two equal parts, carried out using guide means piston. 4. The device according to any one of claims 1 or 2, in which the restrictive means includes an element located on different sides from the center line of the cross-sectional area of the piston into two equal parts, carried out using the guide means of the piston, but not along this center line. 5. The device according to any one of claims 1 or 2, in which each restrictive means is made integrally with the piston. 6. The device according to any one of claims 1 or 2, in which each restrictive means is made separately from the piston and connected to it. 7. The device according to any one of claims 1 to 6, in which the restrictive means is made with the possibility of engagement with one or more rails with the possibility of sliding, while the rails are mounted on the crankcase of the device. 8. The device according to any one of claims 1 to 7, in which the number of pistons is two, three, four, five or six. 9. The device of claim 8, in which each piston is equipped with two restrictive means located symmetrically relative to the axis of the piston. 10. The device of claim 8, which is equipped with at least two pistons and in which the guiding means of the piston are located on one side of the axis of the support of the lower end of the connecting rod. 11. The device according to any one of claims 1 to 10, in which the guide means is made with meshing means of engagement on the connecting means with the possibility of sliding. 12. The device according to any one of claims 1 to 11, in which when the crank is rotated, at least one restrictive means extends into the volume formed by the region swept by the crank that moves along the main axis of the crank. 13. The device according to any one of claims 1 to 12, in which the flat surface is located in a plane perpendicular to the axis of the corresponding piston. 14. The device according to any one of claims 1 to 12, in which the flat surface is located in a plane oriented with respect to the axis of the corresponding piston at an angle other than 90 °. 15. The device according to any one of paragraphs.13 or 14, in which the means of engagement includes two or more parallel flat surfaces corresponding to the guide surfaces and made with the possibility of sliding relative to the latter. 16. The device according to any one of claims 1 to 14, in which the linear surface and / or means of engagement includes two or more roller bearings, and the guide means is made with the possibility of engagement with the means of engagement on the connecting means with the possibility of sliding. 17. The device according to clause 15, in which parallel guide surfaces located opposite each other are located on the connecting means, and the engagement means are located on the piston. 18. The device of claim 10, comprising two or three pistons mounted on a slide means on each support of the lower end of the connecting rod. 19. The device according to claim 10, in which the pistons are located at equal angles to the main axis. 20. The device according to claim 10, in which the guiding means is made integrally with the piston. 21. The device according to claim 10, in which the guide means is located on a separate structure mounted on the piston. 22. The device according to item 21, in which the aforementioned separate design is connected to the piston by a swivel. 23. The device according to any one of claims 1 or 10, in which the main axis of the crank is fixed relative to each cylinder. 24. The device according to any one of claims 1 or 10, in which the main axis of the crank is movable relative to the cylinder or each cylinder with the possibility of changing the degree of compression in the cylinders and / or synchronizing the movement of each piston. 25. The device according to any one of claims 1 or 10, in which the main axis of the crank is made with the possibility of movement relative to at least one cylinder, providing as a result of such a movement the ability to change the compression ratio without changing the phase. 26. The device according to any one of claims 1 or 10, in which the main axis of the crank is made with the possibility of rotation relative to the cylinder or each cylinder around an axis located at a distance from the main axis, with the possibility of raising or lowering the crank relative to the cylinder or each cylinder. 27. The device according to any one of claims 1 or 10, in which the crank is arranged to move in a plane perpendicular to the axes of the pistons or at least one of them. 28. The device according to claim 1, in which the connecting means is made with the possibility of making relative to the piston movement without a rotational component, the device includes stabilization means made with engagement with the connecting means to prevent deviation of the connecting means from a single orientation when it performs orbital movement around main axis. 29. The device according to p, in which the stabilization tool is made to ensure engagement of the connecting means with the piston. 30. The device according to p, in which the stabilization means includes a separate connecting link mounted using a swivel joint simultaneously on the connecting means and the crankcase of the device. 31. The device according to claim 1, in which the main axis of the crank is arranged to move relative to the cylinder along at least one path, and the gearing means has such a configuration that when the main axis of the crank is moved along this path, the piston is moved practically without delay and no lead. 32. The device according to p, in which the path along which the possibility of movement of the main axis of the crank is straightforward. 33. The device according to p, in which the path along which the possibility of movement of the main axis of the crank is arcuate. 34. The device according to claim 1, in which the center of mass of the connecting means is located on the axis of the lower end of the connecting rod or in close proximity to it. 35. The device according to clause 34, in which the crank includes a counterweight, which is made with the possibility of static and / or dynamic balancing of the mass of the connecting means relative to the main axis. 36. The device according to claim 1, in which the resulting center of mass of the crank together with the connecting means and the piston or each piston during rotation of the crank remains stationary or almost stationary relative to the main axis. 37. The device according to claim 1, in which there are at least two pistons and in which the configuration of the connecting means and means of engagement is such that the movement of each piston is ensured according to a simple harmonic law. 38. The device according to claim 1, in which there is at least one pair of pistons and in which the mass movement of each pair of pistons is equivalent to the orbital motion of the mass of one material point. 39. The device according to § 38, in which the trajectory of the orbital motion is a circle. 40. The device according to § 38, in which the path of the orbital motion is an ellipse. 41. The device according to § 38, in which the movement of each piston is a movement according to a simple harmonic law. 42. The device according to claim 1, in which the support of the lower end of the connecting rod and connecting means are combined in the form of a circular cam. 43. The device according to § 42, which includes two pistons. 44. The device according to item 43, in which the axis of the pistons are located at an angle to each other. 45. The device according to item 44, in which the angle at which the pistons are located is 60, 72, 90, 120 or 180 °. 46. The device according to claim 1, comprising means for adjusting the distance between the piston and the gearing means. 47. The device according to item 46, in which the means for regulation includes a connecting rod mounted on the piston, and means of engagement. 48. The device according to claim 1, in which when the piston is at top dead center, the main axis is between the piston and the axis of the support of the lower end of the connecting rod. 49. The device according to claim 1, in which when the piston is in top dead center, a straight line drawn from the main axis to the axis of the support of the lower end of the connecting rod is parallel to the axis of the piston and is located at a distance from it. 50. The device according to 49, in which when one of the pistons or each piston is in the top dead center or bottom dead center, a straight line drawn from the main axis to the axis of the support of the lower end of the connecting rod is parallel to the axis of the corresponding piston and is located at a distance from her. 51. A fluid piston type device comprising the following components: a crank having a main axis and including a support element of the lower end of the connecting rod with an axis for which at least one piston assembly having at least one piston mounted with the possibility of reciprocating motion is provided in orbit around the main axis inside the cylinder along the axis of the piston, while the piston has a cross-sectional area perpendicular to the axis of the piston, at least one tracking element located between the support element and the piston and made the possibility of transmitting movement from the support element to the piston, while the follower element is configured to reciprocate along a rectilinear path having a center line from one end point to another, at least one restrictive means designed to prevent the piston from moving otherwise , rather than movement along its axis, with at least a portion of each of the restrictive means located inside the volume swept by the cross-sectional area of the piston when it is moved SRI along the piston axis, but is not on the center line between the two endpoints. 52. The device according to 51, in which each piston assembly has two surfaces. 53. The device according to paragraph 52, in which there is one servo element for each piston, while the servo element is mounted with the support on both surfaces. 54. The device according to paragraph 52, in which the supporting element is made based on one surface, and the tracking element is made based on another surface. 55. The device according to paragraph 52, which includes two tracking elements, each of which is made based on one corresponding surface. 56. The device according to 51, in which each piston assembly includes one piston. 57. The device according to 51, in which each piston assembly includes two pistons. 58. The device according to 51, in which each piston assembly includes two pistons and one follower element located between the two pistons. 59. The device according to 51, in which the follower is a circular cam, the center of which is offset from the main axis. 60. The device according to 51, which includes two or more piston assemblies for each supporting element of the lower end of the connecting rod. 61. The device according to § 51, which includes two piston assemblies, the axis of one piston of the first piston assembly located at an angle to the axis of one piston of the second piston assembly. 62. The device according to p, in which the angle between the axes of the pistons is 90 °. 63. The device according to item 62, which includes two tracking elements, each of which is made with a clutch with a piston in both piston assemblies. 64. A liquid device comprising the following components: a crank, including a support for the lower end of the connecting rod, containing an axis for which it is possible to move in orbit around the main axis of the crank, a connecting means mounted on the axis of the support of the lower end of the connecting rod, at least one pair of pistons, each piston is installed with the possibility the reciprocating movement inside the corresponding cylinder along the axis of the piston, while the axis of the pistons of each pair are located at an angle of 90 ° to each other, and each piston is made with the possibility of engagement coupling with the connecting means, while the movement of each mass of the pair of pistons is equivalent to the orbital movement of the mass of one material point, the center of mass of the connecting means is located on the support axis of the lower end of the connecting rod or in close proximity to it, while the crank includes a counterweight located almost diametrically opposite the support of the lower end of the connecting rod, the center of mass being at a distance from the axis of the crank, and the counterweight includes the equivalent of the following masses: the first mass for static oh and / or dynamic balancing of the whole mass or part of the mass of the support of the lower end of the connecting rod relative to the axis of the crank, the second mass for static and / or dynamic balancing of the whole mass or part of the mass of the connecting means relative to the axis of the crank and the corresponding third mass for static and / or dynamic balancing of the whole mass or part of the mass of each pair of pistons relative to the axis of the crank. 65. The device according to item 64, in which the trajectory of the orbital movement is a circle, while due to the presence of a third mass, static and / or dynamic balancing of the mass of the pistons is provided. 66. The device according to item 64, in which the trajectory of the orbital motion is not a circle, while due to the presence of the third mass, the mass of the pistons in the first direction is balanced. 67. The device according to p, in which the first direction is parallel or perpendicular to the bisector of the angle between the axes of the pistons of each pair. 68. A liquid device comprising the following components: a crank, including a support for the lower end of the connecting rod, having an axis for which it is possible to move in orbit around the main axis, connecting means mounted on the axis of the support of the lower end of the connecting rod, at least one piston mounted with the possibility of reciprocating movement inside the cylinder along the axis of the piston, an intermediate connecting means made with the possibility of connecting at least one piston with body, and means for adjusting the position of the intermediate connecting means relative to at least one piston, or relative to the connecting means, or relative to both. 69. The device according to p, in which the means for adjusting the position of the intermediate connecting means includes a groove, groove or surface made with the possibility of engagement with the intermediate connecting means. 70. The device according to p, in which the intermediate connecting means is made with the possibility of engagement with a guide means for stabilizing at least one piston inside the corresponding cylinder. 71. The device according to item 70, in which the means for adjusting the position of the intermediate connecting means includes a guide means. 72. The device according to item 70, in which the guiding means is separated from the means for regulating the position of the intermediate connecting means. 73. The device according to p, in which the means for adjusting the position of the intermediate connecting means is arranged to move relative to the axis of the cylinder in the transverse direction, or in the longitudinal direction, or in both directions. 74. The device according to item 70, in which the guiding means is arranged to rotate around an axis. 75. The device according to p, in which the means for adjusting the position of the intermediate connecting means includes a groove or grooves, a groove or grooves, surface or surfaces, or any combination of similar elements that are straight, or curved with one radius of curvature, or curved repeatedly with different radii of curvature. 76. The device according to p, in which the intermediate connecting means includes contact elements by means of which sliding or roller contact is provided with means for regulating the position of the intermediate connecting means. 77. A connecting rod assembly for a fluid device with a triangular connecting rod having pistons located opposite each other, made with the possibility of reciprocating movement inside opposed to each other cylinders, the axes of which are parallel, mounted on two pistons and including an engaging section made with the possibility of placement therein, an engagement element mounted to rotate on a support of the lower end of the connecting rod located on the crank, with the possibility of making the engagement element reciprocating motion during rotation of the crank, while the engagement element is split into two parts. 78. The crank assembly of claim 77, wherein the engagement portion includes two parts that are joined together along a plane substantially parallel to the axes of the cylinders, or along a plane substantially perpendicular to the axes of the cylinders. 79. The crank assembly of claim 78, wherein the two parts of the engagement portion are identical. 80. The connecting rod assembly according to claim 78, wherein for fastening and holding together two parts of the engagement portion, fastening at two points is made. 81. The crank assembly of claim 77, wherein the engaging portion includes two surfaces formed to form a channel in which the engaging means can reciprocate. 82. The connecting rod assembly of claim 81, wherein each channel is limited to only one part of the engagement portion. 83. The connecting rod assembly according to claim 78, in which each part includes legs made with stretching towards the other part and with the possibility of engagement with it. 84. The connecting rod assembly according to claim 78, comprising legs located at the ends of the channel. 85. The connecting rod assembly according to claim 78, comprising a leg located in close proximity to the channel at a midpoint. 86. A piston assembly for a liquid device, comprising the following components: a piston mounted for reciprocating movement inside the cylinder along the axis of the piston, the piston having a cross-sectional area perpendicular to the axis of the piston and a guiding means including a flat surface located transverse to the axis of the piston, while the guiding means is arranged to engage with the means of engagement on a connecting means mounted on the axis of the support of the lower end of the tent una, at least one restrictive means, designed to prevent the piston from moving other than the movement along the axis of the piston, while the piston guide means are arranged so that with it the cross-section of the piston cross-section is divided into two equal parts, and, at least a part of each restrictive means is located inside the volume swept by the cross-sectional area of the piston, but not along the said central line of dissection of the cross-sectional area into two equal parts. 87. The piston assembly of claim 86, wherein two or more rollers are placed on a flat surface. 88. The piston assembly according to any one of claims 86 or 87, wherein the restrictive means are integral with the piston. 89. A fluid device with a triangular connecting rod, containing the following components: a crank, including a support for the lower end of the connecting rod, having an axis for which it is possible to move in orbit around the main axis of the crank and at least one piston assembly including the following components: a piston mounted with the possibility of reciprocating movement inside the cylinder along the axis of the piston, which is located in a plane almost perpendicular to the axis of the support of the lower end of the connecting rod and the main axis, while the piston has a cross-sectional area perpendicular to the axis of the piston, an element of the type "triangular connecting rod" selected from the group comprising a channel, a beam, a channel and a beam, a bored hole and a bored hole and a beam, the element of the type "triangular connecting rod" is configured to specify a longitudinal The bearing of the lower end of the connecting rod is made with the possibility of reciprocating movement along this longitudinal path relative to the piston between the two end points, while the element of the type "triangular connecting rod" is made integrally with the piston, or connected to the latter by means of a connecting rod type, restrictive means configured to move along said predetermined path and to prevent the movement of one or more pistons, an element of the type "triangular connecting rod" and means of the type of connecting rod other than the movement along this predetermined path, with at least a part of the restrictive means being located across the longitudinal path of the triangular connecting rod element and inside the volume swept by the cross-sectional region as it moves along the piston axis. 90. The device according to p, in which the restrictive means includes a pair of elements, one of which is located on the opposite side of the element of the type "triangular connecting rod" with respect to the other. 91. The device according to claim 90, in which the elements are in a straight line perpendicular to the longitudinal path. 92. The device according to p. 89, comprising two pistons, each of which is arranged to reciprocate inside a two-chamber cylinder, closed at both ends, while the combustion chamber is formed between the piston and each end of the cylinder. 93. The device according to p. 89, comprising two pistons for each support of the lower end of the connecting rod, while the axis of one piston is placed in a different plane than the one in which the axis of the other piston is located. 94. The device according to p. 93, comprising at least one lubricating channel for supplying a lubricant to the element of the type "triangular connecting rod". 95. The device according to any one of paragraphs.13 or 14, in which the flat surface and / or means of engagement includes two or more roller bearings, and the guide means is made with the possibility of engagement with means of engagement or with connecting means with the possibility of rolling or with the possibility of rolling so slip. 96. The device according to p. 89, comprising two cylinders, while the main axis is arranged to move towards or away from the cylinders. 97. The device according to p. 89, further comprising an auxiliary crank having an axis parallel to the main axis to stabilize the device. 98. The device according to p. 89, further comprising another crank, while the two cranks are interconnected by means of a connection with the possibility of joint rotation. 99. The device according to p, in which the means of connecting the cranks is a gear. 100. The device according to p. 89, comprising two pistons connected in a pair, while both pistons are located in the same plane perpendicular to the crank. 101. The piston assembly of claim 86, wherein the flat surface is stretched across the diameter of the cross section. 102. The piston assembly of claim 86, comprising lubricant for providing said flat surface with lubricant. 103. The device according to p, in which the restrictive means includes an element having a cross-sectional shape selected from the following group: square, rectangle, ellipse, circle, arc, waves, mushroom, rod, letter F. 104. The device according to p, in which the restrictive means includes a section made with a strike above and below the element of the type "triangular connecting rod". 105. The device according to p. 89, comprising a second restrictive means, which is part of an element of the type "triangular connecting rod", or installed on it, or connected to it and configured to prevent movement of the element of the type "triangular connecting rod" other than the movement along the longitudinal the way. 106. The device according to p, in which the second restrictive means is made with the possibility of rotation. 107. The device according to p, in which the piston or each piston is mounted on an axis that does not coincide with the main axis and is perpendicular to it. 108. The device according to p, in which the movement of each piston is a movement according to a simple harmonic law. 109. The device according to clause 47, in which the control means is mounted on the piston or on the means of engagement using a swivel. 110. The device according to p, in which two pistons are located in the same plane. 111. The device according to p, in which the means for connecting the cranks is a connecting means mounted on a support of the lower end of the connecting rod of each crank using a swivel. 112. The device according to claim 1, in which the restrictive means has a section made with a strike above and below a flat surface. 113. The device according to p, which is part of an internal combustion engine or pump. 114. The device according to p, in which the restrictive means consists of elements located in the volume swept by the area swept by the crank, while moving along the main axis of the crank. 115. The device according to any one of paragraphs 89-91, comprising two bearings of the lower end of the connecting rod, each of which has an axis, while an angle D is formed between the axis of the first support of the lower end of the connecting rod, the main axis and the axis of the second support of the lower end of the connecting rod ° or more, two piston assemblies, wherein the first piston assembly is mounted on the first support of the lower end of the connecting rod, and the second piston assembly is mounted on the second support of the lower end of the connecting rod, the first piston assembly having a first piston axis and the second piston assembly having a second piston axis , while between the first angle A of the piston axis and the second axis of the piston, and when balancing, the angle D is set to 2 · (A-90) °. Priority on points: 04/01/1999 - pp. 9-11; 05/11/1999 - pp. 64-67, 110, 115; 06/04/1999 - p. 68; July 15, 1999 - pp. 69-78; 07/30/1999 - claims 1-8, 13-47, 51-63, 88-109, 111, 113-114; 08/11/1999 - p. 112; 08/13/1999 - item 12; 08.24.1999 - pp. 79-87; 09/14/1999 - pp. 48-50.

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