MX2010008098A

MX2010008098A - Fluid pump for heat engine, heat engine, thermal system and method.

Info

Publication number: MX2010008098A
Application number: MX2010008098A
Authority: MX
Inventors: Barry Woods Johnston
Original assignee: Barry Woods Johnston
Priority date: 2008-01-23
Filing date: 2009-01-23
Publication date: 2010-12-21
Also published as: CN101978134A; AU2009206314A1; BRPI0907401A2; WO2009094559A1; JP2011510226A; EP2252767A1; CA2712734A1

Abstract

In a thermal system, low pressure fluid is returned to a source of high pressure fluid through a balance of internal pressures or forces that balances out the resistance to the flow of the working fluid being pumped from the low pressure to the high pressure.

Description

FIGURE 6 is a simplified cross-sectional view of a valve / port mechanism according to a further embodiment.

FIGURE 7 is a simplified cross-sectional view of a | thermal system according to an additional modality. j I ' FIGS. 8A-8B are simplified cross-sectional views of fluid Ibómbas according to additional embodiments; FIGURE 8C is a schematic perspective view of the structure of a pump piston / diverter member shown in FIGURE 8B; and FIGURE 8D includes schematic side views j and top of a modality in which two Wankel motors are combined. j FIGURE 9A is a simplified cross-sectional view of a | system I 'thermal according to an additional embodiment, FIGURE 9B includes; Simplified views of a fastener mechanism in FIGURE 9A through numerous steps during a system cycle.

FIGURE 10 includes simplified cross-sectional views of a regulator of varying conditions according to one embodiment.

FIGURES 1 1 -12 are seen in cross-section, simplified by variable regulator stabilizers according to one or more modalities.

FIGS. 13A-3B are simplified cross section views (several Kockum motors adapted according to one or more embodiments.

FIGURE 14 discloses a rotary divider valve for coriurial use for more modalities.

FIGURE 15 describes a particular application of a highly efficient combined power (CHP) motor in accordance with one or more embodiments DETAILED DESCRIPTION In the following detailed description, for purposes of explanation, numerous specific details are set forth to provide a complete understanding of the modalities specifically described. However, it will be evident that one or more modalities can be practiced without these specific details. In other cases, well-known structures and devices are shown schematically in order to simplify the drawing. I; 'I ! | I FIGURE 1 is a schematic diagram of a thermal system 1000 which will be referred to hereinafter as the Soony 1000 engine.

The Soony 1000 engine in one embodiment comprises a heat engine 400, a heat exchanger 500, a cooling exchanger 600, and an I b 1 fluid pump 700.

The heat exchanger 500 in one embodiment includes a boiler which is a closed vessel in which a working fluid was heated. The working fluid, in one embodiment, is heated under pressure. The steam or water vapor of the heated working fluid, which is now in a high pressure state, is then circulated outside the heat exchanger 500 for use in the motor cylinder 400. The heat source (not shown) for the heat exchanger 500 in a modality may be the combustion of any type of fossil fuels such as wood, coal, oil, natural gas. In a further embodiment, the heat source may also be solar, electric, nuclear (e.g., lower grade nuclear waste) or the like.

| The source of heat can also be heat rejected from other processes such as car exhaust or factory chimneys, etcetera. . { i: The working fluid can be any type of working fluid that can be used 101 to transfer the work generated by the thermal engine 400 towards the extériór | during the down stroke and to drive the power piston 103 to discharge the working fluid processed in the upward stroke, and the negative work d before the compression as will be described hereinafter in certain embodiments.

Examples of motor cylinder 400 include, but are not limited to, multi-cylinder unidirectional flow engines described in the patents and applications listed at the beginning of this specification, especially US Patents.

Nos. 5,806,403 and 6,505,538. i i The fluid pump 700 is provided to move the processed working fluid in a low pressure state back to the heat exchanger 500 which is in the high pressure state. In certain embodiments, the fluid pump 700 allows the expanded working fluid to be returned to the heat exchanger) 500 without a vapor-liquid phase change. The fluid pump 700 includes a leaving chamber 701 divided into two pump sub-chambers 1 14 and 1 12 by means of a displaceable pump piston 1 13. The pump piston 1 13 is operatively and controllably driven by the piston power 103 of the heat engine 400 through the connector 800 that allows the pump piston 1 13 to follow the power piston 103 for a certain period (for example, the up stroke) and to be independent of the power piston 103 during another period (for example, the downward stroke) of a Mótor 'oony 1000 cycle. The pump piston 1 13 is further deflected by means of a diverter element 709. In certain embodiments, the diverter element 709 comprises a spring. which pulls the pump piston 1 13 in a direction that minimizes the v † lumerj) of the second pump sub-chamber 112. Other diverter element configurations 709, such as air cylinders or any kind of activators which can point to the fluid pump at closing at the appropriate time as described below in the present, they are used in one or more modalities.

The first sub-ca.ara de bo.ba, 14 is comuni cab, e con, a piston camaja 104 of the heat engine 400 through the connection 123 and define an I i i l l expansion chamber in the down stroke of the power piston 103 as well as a chamber I pump displacement in the upward stroke of the power piston 103. i: the exhaust port 122 in a mode is provided in the first sub-chamber of pump 1 14 for fluid communication between the cooling exchanger 600 and the (rimera) pump sub-chamber 1 14. However, other provisions are not excluded, for example, one or more escape ports 122 are provided in additional modalities and in l 'ap ir! imera I | pump sub-chamber 1 14 and / or piston chamber 104 and / or connection 123. Likewise, one or more input ports 121 are provided in certain embodiments in the first pump sub-chamber 14 and / or chamber of piston 104 and / or connection 123. The first sub-chamber has dual functions of an expansion chamber and a pump displacement chamber, as will be described later in the present ß? There are several modalities, and can be referred to in the description herein as "expansion chamber" (collectively with the piston chamber) or as "piston displacement chamber".

The second pump sub-chamber 12 is communicable with the thermal intercalator 500 through a pump output port 124 and the cooling interchanger 600 through a pump inlet port 125. One is provided. or more control elements, such as check valves, in one or more doors 121, 122, 124, 125 to controllably open and close the respective ports during the operation of the Soony 1000 engine. It is also provided, in additional embodiments, a valve / port control mechanism (not shown) to control the | opening and / or closing of one or more ports 121, 122, 124, 125. The second sub-chamber of | pump I it can be referred to in the description herein as a "bomb". The "pump is closed or switched off" when the second pump sub-chamber is at or near its minimum volume (zero in certain embodiments) after a pumping action as will be described hereinafter in one or more embodiments . The 'pump is full' when the second pump sub-chamber is at or near its maximum volume (the full volume of the pump chamber in certain embodiments) just after a pumping action as will be described below in the present in one or more modalities.

An operating cycle of the Soony 1000 engine will now be described with referejicija to FIGURE 2 which includes multiple views similar to FIGURE 1 illustrating numerous steps during the operation of the Soony 1000 engine. The only reference numbers that are necessary for the description of A particular stage is shown in IGUFjA 2.

To understand the operation of the engine, three aspects of the engine will be mentioned: 1) the nature of the positive work output that occurs in an expansion chamber 107 (illustrated in Step 1 of FIGURE 2) comprising the piston chamber 104 and the first pump sub-chamber 14 which are Lendo expanded together during the down stroke of the power piston 103; 2) the nature of the anti-work that is caused by the recap occurring in an expanded cooling chamber 100 (illustrated in Step 7 of FIGURE 2) comprising the piston chamber 104 (which now functions as a chamber compression), first pump sub-chamber 1 14 (which now functions as a pump displacement chamber) 1 14, cooling chamber 0 of cooling exchanger 600, and second pump sub-chamber 1 12 what are being cooled and compressed simultaneously during the down stroke of the power piston 103; Y 3) the effective work output balance due to the pressure differential between expansion 1) and understanding 2). j I The positive work 1) of the motor 1000 is created by expanding the working fluid heated at high pressure to a low pressure exhaust manifold (e.g., the cooling exchanger 600).

Negative work 2) in the expanded cooling chamber 100 is the work imposed on the working fluid during compression and cooling. The shrinkage of the working fluid is caused both by the compression and by the alteration of the heat while passing through the cooling chamber 110 of the cooling interchanger 600.

Work 3) in particular is created by the work or pressure differential occurring between the expansion volume in the expansion chamber 107 and the contraction volume of the expanded cooling chamber 100 as the power piston 103 moves between Top Dead Center (TDC) and Lower Point (BDC).

Stage 1 Stage 1 shows the Soony 1000 engine just before the bombing action. At or near the TDC, for example, at or at the end of the upward stroke of the power piston 103, the high pressure heated working fluid from the heat exchanger | 500 is injected into the minimum volume of the expansion chamber 107 through the inlet port 121 that is briefly opened (for Steps 1 and 2). Specifically, the working fluid in the heat exchanger 500 is accessed both for the piston chamber 104 and for the first pump sub-chamber 14 through the port certain embodiments, the connector 800 is disabled at or slightly before the opening of the inlet port 121. After the connector 800 has been released, the pump piston 1 13 is subject only to the deviation action of the diverter member 709 on the which forces the pump piston 1 13 towards a closed pump position as shown in Step 2 in FIGURE 2. The working fluid cooled and compressed in the second pump sub-chamber 12 is pumped by the pump piston l jl3, through the pump outlet port 124 which is now open, returned inside the heat exchanger 500. Since the pressures are equalized by the presence of the heated working fluid on both sides of the pump piston 1 13, Only a small amount of energy is required for the diverter element 709 to pump the! fall from the return pump into the heat exchanger 500. The pump piston 1113 is stopped in the closed pump position as shown in Step 2 in FIGURE 2.

The presence of the pump piston 1 13 at or near the closed pump position closes the pump outlet port 124, either by means of the pump piston body 13 or through the aforementioned valve / port control mechanism. . The volume of the second pump sub-chamber 12 in the closed pump position in about six modes will be as close to zero as possible. In the expansion chamber 107, the heated working fluid begins to expand and move the power piston 103 towards the BDC.

Stage 3 Stage 3 shows the Soony 1000 engine in an initial stage in the expansion (descending) race. The inlet port 121 has been closed so that the expansion occurs in isolation within the expansion chamber 107! M In the! Stage 3, expansion chamber 107, which includes the piston chamber 104 and the first pump sub-chamber 14, is closed from both the heat exchanger 500 and from the cooling exchanger 600. The power piston 103 initiates downward stroke allowing the working fluid to expand adiabatically. The downward stroke of the pump piston 1 13 generates work that is emitted to the output mechanism 101 through a power piston shaft 141. The piston of The pump 1 13 is held by the diverter element 709 in the closed pump position.

Stage 4 Stage 4 shows the Soony 1000 Motor near the termination of the expansion (descending) stroke. The working fluid in the expansion chamber 107 continues to expand towards the BDC, in isolation from the heat exchanger 500 and the cooling exchanger 600.! Stage 5 Stage 5 shows the Soony 1000 Engine at the end of the expansion (descending) career and, therefore, the beginning of the understanding (ascending) race. The piston chamber 104 and the first pump sub-chamber 14 are being converted from an expansion chamber to a compression chamber. The power piston shaft 141 is being converted from (a) transferring positive work from the expansion and the workflow to the outside to (b) transferring negative work from the outside to drive the subsequent compression of the fluid from the outside. work processed. The power piston 103 has completed its downward stroke and has reached the BDC. The escape port 122 is open for the cooling exchanger 600. The piston chamber 104 and the first pump sub-chamber 1 14 are now converted to a compression chamber and a pump displacement chamber, respectively, so that the working fluid can be forced into the cooling exchanger 600. The descending energy output stroke moves toward the compression upward stroke in preparation for the compression of Step 6.

Stage 6 Stage 6 shows the Soony 1000 Engine in an initial stage of the compression stroke (ascending). The connector 800 is reactivated to connect the power piston 103 and the pump piston 1 13. Therefore, the pump piston 1 lj3 moves from the closed pump position with the power piston 103 during the previous up stroke. It will be noted that, during each cycle, in the BDC, the expansion chamber 107 changes to become the expanded cooling chamber 100 (best illustrated in Step 7 of FIGURE 2) with the consumed working fluid that is compressed Now and cooled simultaneously. The upward stroke of compression input, which causes anti-work (by means of a piston shaft of power 141) from the motor output (which now functions as a compression unit), takes the working fluid consumed in the piston chamber 104 (now functional as a compression chamber) 104 and first pump sub-chamber 14 (which now functions as a pump displacement chamber) and initiate compression. The exhaust port 122 and the pump inlet port 125 open, giving access to the recompressed consumed working fluid from the displacement chamber of | pump 1 14 inside the cooling exchanger 600. Afterwards, the working fluid cooled and pump input 125, is reduced slightly, for example, to about 306 psi as in the example described hereinafter, due j to the added increased volume of the second pump sub-chamber 1 12. The pressure in the second pump sub-chamber 1 12 during the initial stage of the compression stroke is greater than that in the first pump sub-chamber 14, and aids in the opening of the pump, i.e. facilitates the upward movement of the piston pump 1 Í13 to its TDC. For this reason, in certain modalities, it is not necessary to immediately enable connector 800 at the start of the compression stroke, allowing the piston! ' 1 j d! e pump 1 13"float" to its TDC under the pressure differential between the second pump sub-chamber 1 12 and the first pump sub-chamber 1 14 until the pressures in | The two sub-chambers of the pump are equalized.

Once the pressure equalization occurs between the first pump sub-chamber 14 and the second pump sub-chamber 12, the pump piston 1 13 is forcedly moved by the power piston 103, through the connector now enabled 800, towards the TDC thus further compressing the working fluid processed in the piston chamber 104 and the first pump sub-chamber 1 14. When the working fluid pressure is processed and compressed in the first sub-chamber pump chamber 1 1 ¡4 and the piston chamber 104 reaches the opening pressure of the check valve in the exhaust port 122, the exhaust port 122 is opened and the compressed work fluidOj is pushed into the chamber Cooling 1 10, coming back! to thereby raise the pressure in the cooling chamber 1 10 and the second su?! c: a! m, pump 1 12 to the desired level, for example, from 306 to 373 psi as in the Example described hereinafter. The compressed working fluid pushed by the power piston 103 and the pump piston 1 13 within the | cooling chamber 1 10 is cooled by the coolant of the cooling exchanger 600 up to a lower entropy. The cooled and compressed working fluid is moved in a manner i, subsequent within the second pump sub-chamber 1 12. | The embodiments which provide both a cooling chamber of the large volume 1 10 and maintain the pressure in that grating or verifying cooling chamber will prevent both (a) turbulence between the cooling chamber 10 and the expansion chamber 107, and (b) the working fluid in the second pump sub-chamber 112 is compressed without the removal of its heat. The retention of the cooling chamber 1 10 and the second pump sub-chamber 1 12 in the pressure c! .erc 'to ina I to the average in certain modes will stabilize the pressure in the second sub-chamber of bjomba 1 12 which will improve the heat absorption capacity during the compression phase of the working fluid in the general compression chamber during the upward stroke.

Note that the lower pressure equalization in the fluid pump 700i in the initial stage of the up stroke will assist in the opening of the fluid pump 700 | just like the top pressure equalization in the 700 fluid pump will help! rapid closing of the fluid pump 700 in the TDC.

In one or more embodiments, the pumping action described in Steps 1 and 2 exchanges a volume of the cooled and compressed working fluid in the second pump sub-chamber 12 (Stage 1) for the same volume of the heated working fluid in the first pump sub-chamber 14 (Stage 2). In such modalities, the Soony Engine 1000 exchanges volumes at a much higher speed than it can; h! a icler a common Stirling engine to exchange heat. For a common Stirling engine, the inevitable delay in this heat exchange process is the reason that the St 1irli engine does not suffer a loss of thermal efficiency of approximately 30%. Specifically, the common Stirling engine loses the work output because the working fluid is absorbing heat during the work stroke so that part of the output of the Work occurs before the working fluid is completely heated. Therefore, the volume exchange in one or more modalities of the Soony 100O Engine can be more deliberate and faster than the thermal exchange in the common Stirling engine.

In one aspect, unlike the common Stirling engine, the Soony Motor 1000 according to one or more embodiments cycles its working fluid volume (from the second pump sub-chamber 1 12) so that it can be completely heated before to be injected back into the working cylinder of the 400 engine.

This allows the working fluid to achieve its full potential output potential. Likewise, the working fluid is completely cooled in one or more conditions during the compression phase of the cycle. Therefore, the Soony 1000 Motor e † unap plus modalities proportion the entire scope of the Carnot class, which uses part 6 most of the 30% loss of efficiency suffered discarded by the common Stirling engine.

In one or more embodiments, 30% loss of efficiency of the common Stirling engine can be regained by (a) rapid closing action of the fluid pump 700 and / or (b) negligible loss due to the preparation of the item. diverter 709. The first, that is, the fast-closing action of the fluid pump 700, is to be achieved because the equalization of the pressures on opposite sides of the pump piston 1 13 allows the diverting force so that the action pumping act with little loss of power. The Soony 1000 engine in one or more modes does not force! al, fluid work to circulate, although it is allowed. In a balanced pressure environment, the diverter element 709 causes the closure (Stage 2, FIGURE 2) with the fluid pump 700. The force of the diverter element 709 loaded and stored (Etápa 1, FIGURE 2) until the moment of opportunity in TDC when the equalization occurs, allowing the quick closing action of the pump. The fluid pump 700 opens,! In a Í | or more modalities, also under conditions of balanced pressure (Stages 6-8, FIGURE 2) by means of the connector 800 which prepares the diverter element 709 in preparation for the moment of opportunity in TDC. The latter, that is, the loss due to the preparation of diverter element 709, is negligible in certain embodiments, for example, 4.5-5%, compared to 30% loss of efficiency of the common Stirling engine, and still the force of the diverter element 709 is sufficiently intense to move the pump piston 1 13, and fast enough to overcome the loss of mass of the pumping mechanism in the period.

In a further aspect, the balance of the internal pressures dentijo djeljjMotor Soony 1000 according to one or more modes during the pump opening (Stages 5-8) and the pump closing (Stages 1 -2) of the fluid pump 700 Permit the working fluid to circulate completely and be fully heated before entering the heat engine 400 and / or to be completely cooled during compression. The configuration of the Soony 1000 engine in one or more modes is capitalized in a momentary window of opportunity during the cycle when there is a momentary equilibrium of internal forces within the engine that allows the rapid transfer of the working fluid from the low temperature / pressure to the high temperature / pressure without a considerable expenditure of energy and without suffering the common losses that occur in other engines including the common Stirling engine. In this regard, the Soony 1000 Motor is a new class of thermal engine that is not a Brayton engine, a Rankin, a lErjcsson or a standard Stirling. ! Example A particular example of a Soony 1000 Motor mode will now be described.

A. Expansion The work output (W = ????) of the Soony 1 000 Motor is the differential d † lower the expansion and compression as the working fluid advances through its ^ expansion "WCOmpreson / cooled- ^ pAVexpans¡on - APAVcompresion / en (riado Using helium as the working fluid, within the parameters of the temperature ango from 212 F to 62 ° F and the pressure range from 480 psi hast 'to 2! 5 l 5 I psi, expansion chamber 1 07 is expanded by ?? / expansion = VBDC expansion "VTDC expansion = 1 Unit of volume to 480 pS¡ where VBDC expansion is the total volume (for example, = 3.1 877 volume units) of the l I volume i 1 I expansion chamber 107 in BDC and is defined by the total of the maximums of the piston chamber 104 and the first pump sub-chamber 1 4 (Stage 5), j and VTDC expansion is the total volume (eg, = 2.1 877 volume units) of the expansion chamber 107 in TDC and is defined as the maximum volume of the first pump sub-chamber 1 1 4 (Stage 2), with the Assumption that the volume of the piston chamber 104 at TDC is zero.

VBDC expansion / VTDc expansion is the expansion ratio example, 3.1 877 / 2.1 877 = 1 .4571 times) Therefore, the first pump sub-chamber 14 which is injected from the heat exchanger 500 with 2.1877 units of working fluid volume, high pressure / temperature, expands by 1 volume unit as the piston from the working fluid passes back into the heat exchanger 500 j in a partially high pressure condition.

The heat removed by the refrigerant, for example water, during compression is determined as follows: Qi = 4673.6 Btu - 4485.4 Btu = 188.2 Btu. The same ones are required! to raise the same 1 unit from 255 psi to 480 psi.

Q2 = 4674.6 Btu - 4486.5 Btu = 187.1 Btu / lbm.

The heat per Ibm that must be added to the cycling fluid in the thermal buffer 500 is the same as the heat removed during recompression. Since the expansion phase is adiabatic, there is no real heat removal during the downward career of work. The heat removal occurs during re-compression while the fluid is maintained at a constant low temperature of 62 ° F. That heat removal is a factor of the change in density of the expanded working fluid as it is recompressed and cooled. Since the compressed fluid (maintained at 62 ° F) is raised to 373 ¡DSÍ (the midpoint between 255 psi and 480 psi), Q2 (the heat per Ibm removed during compression is equal to the heat that is added to the Tank) ) is a factor of the increase in density caused by the change in pressure from 255 psi to 373 psi at a constant of 62 ° F temperature.

The thermal replenishment from 62 ° F in the fluid pump 700 to 2 ° 2 ° F in the heat exchanger 500 is ? = d2 / di x (Q2) = d2 / d! x 187.1 Btu loss due to heat removal ddirainte compression from 255 psi to 373 psi.

This is the same heat that must be replenished to raise the working fluid temperature from 62 ° F to 212 ° F or from 373 psi to 480 psi. Because the aggregate heat is measured in Btu / lbm, the heat to be replenished in the Tank is the same I based on Wankel. The Wankel configurations include but are not limited to those of Ramelli, Otto von Guericke, Pappenheim, Watt, Elijah Gallpway, Jones, Alotham / Franchot, Cooley, Umpleby, the Wallinder / Skoog, the Sensaud / Lavaud, the Bernard Maillard, and the recent George Yarr.

The Soony 3000 engine comprises the heat exchanger 500, by Ib minus a Wankel engine 403 corresponding to the heat engine 400 of FIGURE 1 and having a Wankel 3103 piston which corresponds to the power piston 103, a fluid pump 700R / L for each working chamber of the Wankel 403 engine, and a cooling exchanger (not numbered) comprising a cooling chamber 1 10 for each ! ,! Fluid pump 700. Each Wankel 403 engine comprises three working chambers 3107R / L M corresponding sequentially to the piston chamber 104 of the FIGURE 1 . The Wankel 403 engine also comprises two 700R / L fluid pumps each with a cooling chamber 1 10R / L in the cooling exchanger. A cam mechanism 144 (FIGURE 3) comprises cams 144UR (FIGURES 5A-5H) which respectively connect pump pistons 1 13L / R of the fluid pumps 700L7 j to the main power piston shaft 141 (similar to the FIGURE 1) through left / right pump ejections 141 L / R. In certain embodiments, auxiliary cooling elements (not shown in all drawings) are provided within the fluid pumps 700L / R to further cool the cooled and compressed working fluid in addition to the cooling effect of the cooling exchanger. In one or more modes, the auxiliary cooling elements comprise piping assemblies with part of the refrigerant that is diverted from the cooling exchanger.

The Wankel configuration shown greatly simplifies the arrangement of '! I ! I I valve and the general design, thus significantly reducing the production cost. Specifically, in certain modalities, the rotating configuration it eliminates the need for the piston stroke valve arrangement. In certain embodiments, the rotating action also automatically displaces an expansion chamber 107 toward the expanded cooling chamber 100 and / or vice versa without an internal piston-operated valve arrangement. . The cam mechanism 144 in certain modes eliminates the need for any other complex synchronization mechanism.

In certain embodiments, a check valve 970R / L is placed in the exhaust ports 122R / L between the Wankel engine 403 and the cooling chambers 1 10R / L (A check valve similar in certain embodiments is also provided for the configuration in piston base of FIGURE 4). The 970R / L check valve is used to maintain the level of retention pressure in the cooling chamber! 1 1 (R / L and the second pump sub-chamber 1 12R / L, for example, at -373 psi as in the example described above If variable condition regulators are provided 1 J0I R / L (described hereinafter) in certain embodiments, the holding pressure will vary. Regulators of variable conditions 1001 R / L are omitted in other modalities. When the high pressure working fluid is released into the expansion chamber 107R / L, the high pressure working fluid in the expansion chamber 107R / L then expands and the pressure drops to its low level, the chamber 107R / L expansion will automatically move to the expanded 100R / L cooling chamber and its consumed working fluid will begin to be richly compressed up to, for example, approximately half (eg, Example) between the original heat / maximum pressure (per example, 480 psi in the Example) of the heat exchanger 500 and the minimum pressure (for example, 255 psi in the tjennp o) of the expanded working fluid. The check valve 970R / L in the cooling chamber 1 10R / L keeps the fluid compressed therein at its almost average high pressure The right spool valve 1 15R is open and the first right pump sub-chamber 14R (which now operates as an expansion chamber - is best seen in FIGURE 5B) is empty but accessed with the locking fluid or at high pressure hot from the heat exchanger 500 ready to be filled quickly. The second right pump sub-chamber 1 12R of the right-hand fluid pump 700R is completely filled with cooled compressed working fluid ready to be pumped into the heat exchanger 500. The right working chamber 3107R i '' is pressurized. The right diverting element 709R is fully prepared and ready to pump the cooled load from the second sub-chamber of bbmba 1 12R i within the high pressure of the 500 heat exchanger. A balance of the internal forces / pressures will allow the right fluid pump 700R to empty: 5u load inside the high pressure / temperature heat exchanger 500. The right 700R fluid pump is located in a state similar to Stage 1 shown in FIG. 2.

The left working chamber 3107L in the rotary motor has been completely expanded and that ready to convert its expanded volume to an expanded cooling chamber, compression on the right side. The left fluid pump 700L (ie, its second pump sub-chamber) is completely empty but ready to begin to open as the left working chamber 3107L of the rotary motor begins to compress the working fluid consumed as it passes through the cooling chamber 1 10L and, subsequently, the second pump sub-chamber 1 12L (better seen in FIGURE 5C) of the left fluid pump 700L.

The left fluid pump 700L is in a state similar to! Stage 5 shown in FIGURE 2.

Stage 2 - FIGURE 5B As stated, during expansion, the expansion chamber, for example, the right expansion chamber 107R, includes the first right pump sub-chamber. 1 14R and the right working camera 3107R. During compression, the expanded cooling chamber, for example, the expanded cooling chamber left or; OL (best seen in FIGURE 5C) includes not only the first left pump sub-chamber 1 14L, and the working chamber left 3107L, but also the left cooling chamber 1 10L and the second left pump sub-chamber 1 12Ü in the opening of the left fluid pump 700L. In one or more modalities, for optimum efficiency, all expanded working fluid is forced out of the corresponding I piston compartment during compression and / or closes the volume of the piston chamber.

On the right side, the hot / high pressure working fluid from the heat exchanger 500 has been injected through the right carriage valve 1 15R (which functions similarly to the inlet port 121 of FIGURE) within the volume two compartments of the right expansion chamber 107R, namely the first right pump sub-chamber 1 14R and the right working chamber | 31¡07R through the input port 121 R corresponding to the connection 123 of the FIGURE 1. The rapid pumping action in the right fluid pump 700R has occurred to pump the load of the right fluid pump 700R through the right pump outlet port 124R back into the heat exchanger 500. The fluid pump 1 right 700R is completely empty and ready for the next opening of the pumping stroke. Specifically, due to the balanced pressure condition on sides i | I : I Opposite of the right pump piston 1 13R, the right deflecting element 709 R, for example, a compression spring, was able to force the right fluid pump 700R to close. The cam mechanism 144 has released its fastener in the pump ejé i i I Once the left fluid pump 700L has emptied its charge inside the heat exchanger 500. The working fluid in the left expansion chamber 107L I continues to expand, moving the Wankel 3103 piston. The right-hand check valve 970R in the right exhaust port 122R remains open, determing the new expanded working fluid in the intermediate working chamber 3107M and the first pump sub-chamber right 114R (which now functions as a pump displacement compartment) through the right cooling chamber j1 10R into the second right pump sub-chamber 112R. The cameras / sub-chambers 3107M, 1 14R, 1 10R and 1 12R together define the expanded right cooling chamber 101pR.

The right fluid pump 700R is in a state similar to Stage 6 I shown in FIGURE 2, or the status of the left fluid pump 700L in FIGURE 5B. The left fluid pump 700L is in a state similar to Stage 2 shown in FIGURE 2, or the status of the right fluid pump 700R in the FIGURE 5B.

Stage 7 - FIGURE 5G The second right pump sub-chamber 1 12R of the right-cooled right-hand chamber 100R continues to open in tandem with the thrust of the cam 144R acting on the right pump shaft 141 R of the right fluid pump 700R. The left inlet port 121 L continues to open, as the flow c, work during the adiabatic expansion in the left working chamber 3107L c iontinu? A to exert work output.

The right fluid pump700R is in a state similar to Stage 7 shown in FIGURE 2, or the state of the left fluid pump 700L in. { the figure The left fluid pump 700L is in a state similar to Stage 3 shown in FIGURE 2, or the status of the right fluid pump 700R ß? FIGURE 5C.

Stage 8 - FIGURE 5H The Wankel 3103 piston is near the termination of its downward power stroke in the left working chamber 3107L The second sub-chamber d < 3 right-hand pump 1 12R of the right-hand fluid pump 700R is almost full and ready to empty its load inside the heat exchanger 500. The jsoin 3000 engine is preparing to return to Stage 1. | The right-hand fluid pump700R is in a similar state as Stage 8 shown in FIGURE 2, or the state of the left-hand fluid pump 700L in the pljGURA I ' 5 D. The left fluid pump 700L is in a state similar to Stage 4 shown in FIGURE 2, or the status of the right fluid pump 700Ri in FIGURE 5D. i In summary, the high pressure / temperature working fluid fed from the ! ! heat exchanger 500 inside the right side of the Soony 3000 engine in FIGURE 3 expands into the upper side of the Wankel 403 engine, compressed / cooled then inside the left side and finally pumped from the side (left side of The return inside the heat exchanger 500. Likewise, the high pressure / temperature working fluid fed from the heat exchanger 500 into the left side of the Soony 3000 engine in FIGURE 3 is expanded within the lac or lower side of the Wankel engine. 403, compressed / cooled then on the right side, and ^ finally pumped from the right side back into the heat exchanger 5/00.

I The Soony 4000 engine shown in FIGURE 4 operates from a manjeraj if Imilar to the Soony 3000. The Soony 4000 engine comprises four thermal engines 400 of FIGURA specifically, at or near TDC, the power piston 103 couples the port valve bracket 133 from below and moves the port valve bracket 133 together with the ring valve sleeve 132 upwards, thereby opening the door. input 121 and closing exhaust port 122. As soon as the power piston 103 leaves the vicinity of the TDC, the port valve bracket 133 returns to its neutral position, allowing the ring valve sleeve 132 to close both the inlet port 121 as the exhaust port 122. Thus, the inlet port 121 is opened only briefly at or near the TDC and both ports are closed, d (during the downward stroke or expansion of the working fluid .

The two lower drawings in FIGURE 6 (Stage 4 and Stage 5) show the closing of the inlet port 121 and the opening of the exhaust port 122. Specifically, at or near the BDC, the power piston 103 engages the bracket of the poppet valve 133 from above and moves the port valve bracket 133 together with the ring valve jange 132 downward, thereby opening the exhaust port jl 22 while maintaining the inlet port 121 in the state closed. As the power piston 103 leaves the BDC and moves upward, the port valve bracket 133 remains in the down position, allowing the sleeve † e ring valve 132 to continue to open the exhaust port 122 and close the port shown 121. Therefore, the entrance port 121 is closed most of the i, downward stroke and upward stroke, while the exhaust port 122 is open for most of the upward stroke.

Various modalities can be derived from the configurations described above and / or described below. For example, one or more of one of the cams 144R / L are provided on each power piston shaft 141 of agreement with one or more embodiments. Other forms of connectors 800 and / or mechanism are not excluded It has a cylinder with two chambers and two power pistons 103LJR. Instead of having a rotating drive shaft to ensure the continuous movement of the piston action, a pendulum 9001 causes an accumulation of inertia that oscillates back and forth in tandem with the movement of the power pistons 103R / L which in one or more modes can be combined in a single power piston; o3. This backward and forward action drives the oscillating linear electric generator 9¡001. The two-cylinder, four-chamber engine described above and / or hereinafter has an overlapping chamber action which ensured that the engine is continuous. The configuration of FIGURE 9A with a one-cylinder, two-chamber engine exceeds this lack of overlap by maintaining the continuous oscillating action of the engine. In general, the average pressure differential between the work output in the expansion chamber [similar to 107 in FIGURE 1) and the working input of the compression chamber (similar to 100 in FIGURE 1) is sufficient to boost the engine. However, both the expansion force and the compression force are acting on both ends of the individual piston. As the expansion side opens, the end of the expansion cowl weakens as, as the compression end closes, the end of the compression stroke becomes greater.

FIGURE 10 describes a regulator of variable conditions for the use of one or o mptetim mizoadra lalid caadpeasc'id, aaldes d ceo emxopa anqsu The co-channel of flsucidriotas de cotrnab reasjope bcatj0o co lansdic FiIoGnUeRsí ysa: ri Vá (it is the thermal exchanger pa 500, especially when the 500 exchanger témjiicp is powered by solar energy, the Soony engine in certain modalities is able to self-adjust with the variable conditions imposed of temperature / pressure.! For example, as the temperature / pressure of the working fluid heated in the heat exchanger 500 rises, since the volume of the piston chamber (1) use the existing Kockums cooling system to maintain a low temperature / low pressure cooling receiver, (2) seal the upstream valve access to the rest of the circulation system of the existing Kockums compression chamber and transform the existing Kockums compression chamber to the back pressure receiver; (3) interconnect the transformed back pressure receiver chambers to maintain a constant volume in the receiver in order to avoid the compression of the back pressure, (4) minimize the purge or spill through the power piston between the transformed expansion / compression chambers and the converted cooling receiver, (5) provide a fluid pump that returns the fluid spilled to the circulation system, and (6) convert the expansion chamber to the dual function of an expanding and compressing chamber (the expansion / compression chamber) so that the piston performs its positive work during the down stroke and negative work (or pumping within another motor) Soony as described with respect to, for example, FIGURE 3) during the upward run. i The walls of the adapted engine expansion / compression chamber are constructed in certain modalities of a material that does not retain or absorb, heat. The ceramic that can handle the abrasion of a motor piston is a po! Sibi Ilid? Ad. The spill between the expansion / compression chamber and the cooling receiver remains at zero. (1) Use the existing Kockums motor cooling system to create a low temperature, low pressure cooling receiver Cooling receiver, the adapted motor would provide the ideal ideal temperature / pressure constant condition. However, in reality, unless a physical barrier (such as a bellows as described in relation to one or more embodiments) is provided for each working piston, the working fluid will be poured into the low pressure cooling receiver. . (5) Provide a fluid pump that returns the spilled fluid to the circulation system.

The spilled fluid is passed back into the circulation system using a rotary pump or the device shown in FIGURE 13B which uses a piston to empty that fluid back into the circulation in BDC when the pressures in BDC are essentially equal to the receiver . As shown in FIGURE 13B, this receiver pump 1307 operates at the lower end of the pressure cycle. Instead of pumping during the high pressure equilibrium in TDC, the receiver pump 1307 pumps the spilled fluid back into the circulation during the low pressure jequiliblio in BDC. Because the spill is expected to be minimal, a gear system is provided that allows the pumping action to occur only after several engine cycle rotations. The spring 1309 is prepared as in the case of the fluid pump 700 of the circulation system and released in the equilibrium pressure condition just as in the circulation system. However, the 1307 receiver pump will achieve pumping at the low pressure point. (6) Convert the expansion chamber to the dual function of the | expansion / compression chamber so that the piston performs its positive work during the downstroke and negative work (or pumping into another Soony engine as described with respect, for example, FIGURE 3) during the four | ascending races. This small internal pump configuration is consistent | with the

Claims

CLAIMS 1 . A temic motor of adiabatic expansion, comprising: a piston chamber; a power piston capable of moving within the piston chamber to operate on the working fluid in a high pressure state receivable from a thermal barrier and to discharge the working fluid in a low pressure state; Y a fluid pump for transferring the working fluid in a low pressure state j back to the high pressure state of the heat exchanger, characterized in the fluid pump comprising: a pump piston; Y an expansion chamber and a pump chamber which are disposed on opposite sides of the pump piston, and which have variable volumes as the pump piston is able to move between the expansion chamber and the pump chamber; characterized because the expansion chamber and the piston chamber are connected | fluidly to jointly define a working chamber for the adiabatic expansion of the working fluid therein during the down stroke of the power piston; the working chamber is able to communicate fluidly and contously with the pump chamber during an upward stroke of the power piston to compress ! ! the working fluid in the low pressure state in the pump chamber; and 1 When the power piston is in or bristle from an upper dead center (TDC) thereof, both the working chamber and the pump chamber are capable of communicating in a flexible and fluid manner with the heat exchanger so that the pressures in the opposite sides of the pump ram are equalized by the trapajo fluid in the high pressure state dosing from the heat exchanger, stabilizing this I I j The resistance of the working fluid to be pumped, by means of a pumping action of the pump piston, from the low pressure state of the pump chamber back to the high pressure state of the heat exchanger. 2. The heat engine according to claim 1, further characterized in that the working fluid in the low pressure state is adapted to be compressed in the pump chamber under partially adiabatic conditions which are between isothermal conditions on the one hand and conditions completely adiabatics on the other hand. 3. The heat engine according to claim 1, further characterized in that (a) the dosing of the working fluid in the high-pressure state from the heat exchanger to the working chamber and (b) the action of the batch is configured to occur from Simultaneously. 4. The heat engine according to claim 1, characterized I in addition because the pump piston is configured to progressively open the pump chamber during the upward stroke of the power piston. 5. The heat engine according to claim 1, characterized in that it also comprises: a cooling chamber capable of communicating in a controlled manner and | fluid between the working chamber and the pump chamber during the upward stroke of the piston l working fluid in the low pressure state before the power i, to cool that I the working fluid cooled in the low pressure state be compressed in the pump chamber. 6. The heat engine according to claim 1, characterized in addition because the pump piston is adapted to be driven operatively, at least indirectly, by the power piston to advance, together with the power piston, into the working range during the upward stroke of the piston of the piston. power. 7. The heat engine according to claim 6, characterized : I because it also includes: I i a connector for operatively connecting the pump piston to a movement into the power piston during the up stroke, and to operatively disconnect the pump piston from the movement of the power piston during the down stroke. 8. The heat engine according to claim 7, further characterized in that the connector comprises a cam mechanism. 9. The heat engine according to claim 1, characterized in that it also comprises: a diverting element that deflects the pump piston towards a closing of the pump chamber to cause the pumping action when the pressures on the opposite sides of the pump piston are equalized by the working fluid in the state} of high pressure that doses from the heat exchanger. 10. The heat engine according to claim 1, characterized ! 1 1 also because the fluid pump is a steam pump adapted to forcefully move the working fluid vapor in the low pressure state to $ \ state ! · High-pressure heat exchanger without a vapor-liquid phase change. eleven . The heat engine according to claim 1, characterized in that it also comprises: a rotating divider valve for operatively opening and / or closing the inlet opening j and the outlet openings of the expansion chamber at different synchronizations. 12. The heat engine according to claim 1, is also made because it is a motor based on Kockum. 13. The heat engine according to claim 1, also characterized because it is a motor based on Wankel. 14. A method for operating a thermal expansion thermal engine which has a piston chamber, a power piston capable of moving inside the piston chamber, a pump piston, an expansion chamber and a pump chamber disposed on the sides opposite of the pump piston and having variable volumes as the pump piston is able to move between the expansion chamber and the pump chamber, wherein the expansion chamber and the piston chamber are fluidly communicated to jointly define a work chamber, characterized by the method because it comprises: expanding adiabatically a working fluid in a state of high pressure in the working chamber during a down stroke of the power piston; fluidly communicate the working chamber with the boijnba camera during an upward stroke of the power piston to compress the fluid! of expanded work in a state of low pressure in the pump chamber; Y when the power piston is in or sow a top dead center (TDC) . i thereof, fluidly communicate both the working chamber and the pump chamber with a heat exchanger so that the pressures on the opposite sides of the pump ram are equalized by the working fluid in the high pressure state by dosing from the heat exchanger, thus stabilizing the resistance of the working fluid being pumped, by means of a pumping action of the pump piston, from the low pressure state of the pump chamber of the pump. return to the high-pressure state of the heat exchanger. 15. A fluid pump for moving a fluid from a first fluid source of said fluid in a low pressure state to a second source of fluid fluid in a high pressure state, the fluid pump comprising: a camera; a displaceable partitioning member in the chamber and dividing the chamber into first and second sub-chambers of variable volumes; the first sub-chamber that has inlet and outlet openings consolably I communicable with the second and first sources of fluid, respectively; the second sub-chamber having inlet and outlet openings that are conslatablely communicable with the first and second fluid sources, respectively; Y characterized in that the partitioning member is positioned to move within the second sub-chamber to pump the fluid in the low pressure state from the second sub-chamber into the second fluid source when; equalize pressures on opposite sides of the partitioning member.