JPH071028B2 - Stirling cycle engine and heat pump - Google Patents

Description

Description: TECHNICAL FIELD The present invention is directed to a novel type of hot gas engine and heat pump in which heat to be converted to work or pumped is externally provided to a cylinder containing working gas. . In particular, the present invention is directed to an improved form of Stirling cycle engine and heat pump.
The term "heat pump" is used in the generic sense to describe a device that can be used for either heating or cooling.

BACKGROUND OF THE INVENTION The present invention is directed to a novel machine that uses the modified "Stirling cycle". The first Stirling cycle machine was invented in 1816 by Robert Stirling.
It was operated as an engine that converts heat into mechanical energy. Subsequent developments have shown that the Stirling cycle machine can also be used in reverse, driven by mechanical energy to act as a heat pump for cooling. Due to the practical problems described below, Sterling
Cycle machines have not become widely used in any of the potential applications.

Conventional Stirling cycle machines operate with a working gas such as air, hydrogen or helium. When operating a Stirling cycle machine as an engine, the working gas is compressed during cooling in the cold space of the engine during the "compression" phase of the cycle. The working gas is then expanded in the hot space of the engine so that it is expanded and heated during the power stroke phase of the cycle.
The working gas then moves from the hot space of the engine to the cold space at a constant volume during the "cooling" phase of the cycle. This cycle is then repeated.

The expansion of the working gas in the hot space of the Stirling cycle machine during the power stroke of the cycle produces work when the machine is operating as an engine. When a Stirling machine is operated as an engine, it absorbs work in the compression phase of the cycle but less work than it does during the expansion phase of the cycle.
The extra work is partly due to mechanical and gas friction (conversion /
(Including that of the regeneration stage). The remaining work becomes effective work.

When operating a Stirling cycle machine as a heat pump, the energy required to compress the working gas during the compression phase of the cycle is greater than the energy available during the expansion phase of the cycle. This is because the part of the machine that absorbs heat from the surroundings (ie the expansion space) is cooler than the part of the machine where the working gas is compressed (ie the compression space).

Hereinafter, the compression space will be referred to as a "cold space" and the expansion space will be referred to as a "hot space", and the present invention will be described as an engine. If the machine were operated as a refrigerator (heat pump) instead of an engine, the temperatures of the compression and expansion spaces would be reversed.
Regardless of whether the invention is used as an engine or a heat pump, the gas entering the expansion space is subject to external heating and the gas entering the compression space is subject to external cooling.

A number of machines have been described which embody the variant of the Stirling cycle (Walker, Stirling engine, Claredon Press, 1980; Stirling for automotive applications).
Engine Design and Outlook, Collie Edition, Noyes Data Co
rp, 1979).

The Stirling cycle engine has many theoretical advantages. The theoretical efficiency is high. Also, since the heat source is external to the working gas, some of the air pollution problems associated with internal combustion engines can be avoided. A Stirling cycle engine is relatively quiet because the fuel in the Stirling cycle engine can steadily burn at atmospheric pressure rather than explode at high temperatures and pressures. It can also be powered by any available heat source and can operate on any type of fuel, including solar, geothermal or fission, fusion heat.

However, some practical problems have hampered the commercial use of Stirling cycle machines. These issues include:

(1) Cycle (that is, reducing the volume of the working gas in the low temperature space and increasing the volume of the working gas in the high temperature space, and then simultaneously decreasing the volume of the working gas in the high temperature space to reduce the working gas volume in the low temperature space The mechanical movements required to accomplish this require complicated and expensive arrangements of gears and levers and the use of multiple cylinders with high weight and friction losses.

(2) Energy loss due to friction of working gas has been a major problem in Stirling cycle machines. In modern Stirling machines, working gas is heated and cooled by passing it through hot and cold tubes on either side of the regenerator. 1 if you use multiple tubes
This increases the surface area available for heat transfer over the larger diameter tubes of the book, but at the same time greatly increases the friction of the gas. Stirling engines typically use a "regenerator" of braided wire, wire mesh or similar material placed between a set of hot and cold tubes. The regenerator works by absorbing heat from the gas at some point and returning it to the gas at a later point. The regenerator also creates considerable fluid friction as the working gas travels back and forth, consuming energy.

(3) Thermodynamics in the conventional arrangement is that the working gas is passed through the high temperature heat exchange at the time of the cycle where the working gas is desired to be cooled, and the working gas is passed through the low temperature heat exchanger when the working gas is desired to be heated. Problems also arise.

The present invention achieves improvements in all of these areas, resulting in a more efficient thermodynamic cycle with mechanical devices that use single string motion with low gas friction.

According to one aspect of the invention, using a bipartite volume of gas that is expanded and compressed by a Stirling cycle,
An improvement to the Stirling engine type device is obtained by sequentially sharing the expansion chamber and the compression chamber so that when one volume of gas is expanded, the other volume of gas is compressed.

According to another aspect of the present invention, gas flows in and out of the expansion space of the engine through different hole openings, and the regenerator in the inlet hole retains heat of compression, which causes the action in the regenerator. It can allow overheating of the gas.

It is an object of the present invention to provide an improved high power, high speed modified Stirling cycle engine.

It is another object of the present invention to provide an improved heat pump that operates on a modified Stirling cycle.

It is a further object of the present invention to provide a low pressure, low speed modified Stirling cycle engine that can be operated by a low quality heat source such as solar energy.

Other purposes will be clarified by the following description.

BRIEF DESCRIPTION OF THE DRAWINGS FIGS. 1 (a), 1 (b) and 1 (c) are illustrations of pressure changes of working gas in an engine according to the present invention, and FIG. 2 shows a basic arrangement of the present invention. Illustration, FIG. 3 is an illustration of an embodiment of a single cylinder engine according to the present invention using two regenerators and a bypass, FIG. 4A is a gate valve that may be used in the engine of FIG. FIG. 4B is a cross-sectional view of a sluice valve that can be used in the engine of FIG. 3, and FIG. 4c is a schematic view of a mushroom valve assembly that can be used in the engine of FIG.

BEST MODE FOR CARRYING OUT THE INVENTION The present invention uses at least one cylinder that is sealed at both ends and is equipped with a double-acting piston, and two or more heat exchanger assemblies connected from one end of the cylinder to the other end. Give an engine with. Each heat exchanger assembly includes at least one heater, cooler and valve at each end leading to one or the other end of the cylinder. Each heat exchanger may also have one or more regenerators and / or one or more bypass valves.

When the above valves actuate, each heat exchanger assembly will participate in a thermodynamic cycle, which in turn shares the piston movement with gas movement. As will become apparent below, each cycle performed by all heat exchanger assemblies is identical and is sequentially performed. The theoretical operation of the cycle in each heat exchanger assembly is as follows.

Stroke 1 (compression): The working gas is discharged from the compression space of the cylinder to the heat exchanger assembly where it is compressed from the lowest pressure level during the cycle to a higher pressure level and is cooled as it passes through the cooler during this stroke. Minimize the work required for compression.

Stroke 2 (Isolation): The working gas in the compressed state is enclosed in the heat exchanger assembly with no change in volume and no input or output of mechanical work.

Stroke 3 (expansion): The working gas expands from the heat exchanger assembly into the expansion space of the cylinder and drops from its maximum pressure to the intermediate pressure, during which it is heated to minimize the pressure drop and should be done. Maximize work.

Step 4 (regeneration): The working gas enters the compression space of the cylinder from the expansion space of the cylinder through the heat exchanger assembly without any volume change, and there is no large input or output of mechanical work, so it is compressed again. The process 1 can be repeated. During this "regeneration" stroke, the working gas is cooled so that its pressure reaches the lowest point in the cycle at the beginning of the compression stroke, reducing the work required to compress the working gas during stroke 1.

These pressure changes are shown graphically in Figure 1 (a).
The theoretical illustration of the local pressure of this gas depends on the heat transfer coefficient between the gas and the surface of the heat exchanger. The gas trapped in the heat exchanger assembly during the isolation process will be heated or cooled depending on the temperature of the adjacent surfaces. The gas in the cooler will cool. The gas in the heater will regulate its temperature in both directions. That is, during the previous (compression) stroke, the gas entering the heater will be cooler than the adjacent heat exchange surface, but the gas at the remote closed end of the heater will be compressed and actually hotter than the adjacent heater surface.

In some cases, the rising temperature caused by the compression of the hot gas in the heater at the beginning of the compression stroke is greater than the decreasing temperature of the gas entering the heater from the cooler (or from the optional regenerator) during compression. . This will result in two triangular shapes with abutting vertices as shown in FIG. 1 (b).

It is also possible that the rise and fall of temperature are completely offset.
This case results in the triangular P / V diagram of Figure 1 (c), which also results from theoretically perfect instantaneous heat transfer. Thus, depending on whether the average gas temperature in the heater, and also in the regenerator and cooler, rises, falls or remains constant during the isolation stroke, the P / V of FIG. The diagram is 1
It takes the form of (a), 1 (b) or 1 (c). It is possible to represent each of these three P / V diagrams from time to time even with the same engine operating at different temperature differences and / or different operating speeds.

Referring to FIG. 1, the area under the compression curve (stroke 1) is smaller than the area under the expansion curve (stroke 3), and the difference is the work output of the engine.

A basic embodiment of the invention is shown in the diagram of FIG.
The double acting piston (10) moves in the closed cylinder (9). The piston (10) is connected to the piston rod (11). The piston rod (11) is supported by a crosshead (not shown) so as not to move laterally. Piston rod (11)
Is connected to a crank rod (not shown) via a conventional connecting rod. The piston rod passes through the seal (22).

One end of the cylinder (9) is connected to the other end of the cylinder through a heat exchanger assembly including a heater (12A, 13A) and a cooler (12B, 13B). Heat exchanger assembly has holes (16,1
7) to communicate with the expansion space of the cylinder, and through the other holes (18, 19) to communicate with the compression space of the cylinder. Each hole (16,17) to the expansion space and its associated heater (12A, 13A)
There is a valve (16A, 17A) between and. There are valves (18A, 19A) between each hole to the compression space and its associated cooler (12B, 13B). The regenerator (14) between each heater and cooler is optional.

As the piston (10) moves back and forth between the expansion and compression ends of the cylinder, the valves (16A, 17A, 18A, 19A) open and close in the following sequence.

After that, this cycle is repeated. Valves (16A, 18A), ignoring leaks and small amounts of residual gas not scavenged from the cylinder
It should be noted that the amount of working gas passing through is always isolated from the amount of gas passing through the valves (17A, 19A).

If the pressure / volume relationship of the amount of working gas passing back and forth through each heat exchanger assembly is considered separately, then
Such an amount of working gas is first of each during the course of the cycle.
Consistent with the pressure / volume diagram of the figure, it can be seen that the pressure / volume relationship of the two quantities of gas is 180 ° out of phase with each other throughout the cycle.

A preferred embodiment of the engine is shown in FIG. A double-acting piston (10) moves in a closed cylinder. Piston (10) is connected to piston rod (11) Next, for example, piston rod (11) is connected to a conventional connecting rod (not shown) connected to a crank pin and a crankshaft (not shown), Hopefully a conventional crosshead (not shown)
Therefore, it is conceivable that the vehicle is supported so as not to drive laterally. In this case, as the piston reciprocates in the cylinder, the crosshead acts to store the kinetic energy of the piston and to return this energy to the piston.

Referring to FIG. 3, coolers (12B, 13
There are two heat exchanger assemblies (12, 13) consisting of B), heaters (12A, 13A) and regenerators (14A, 14B). The regenerator end of each heat exchanger assembly has a hole (1) with a valve device (16A, 17A).
6) and 17) respectively connected to the hot end of the cylinder. The other end of each heat exchanger assembly is connected to a compression valve hole (18, 19) of a cylinder including a valve device (18A, 19A). By-pass holes (20,
21) is provided to regenerate the second set of connecting the expansion space of the cylinder between the cooler (12B, 13B) and the heater (12A, 13A) of each heat exchanger assembly (12, 13). Valve (23A, 23B) valve (2
It may be provided between the 0A, 21A) and the cooler (12B, 13B).

In this embodiment, the working gas flows through the heat exchanger assembly and into the expansion space via the valves (16A, 17A), while the valves (20A, 2A
1A) exits the expansion space and flows to the heat exchanger assembly. As a result, the sequence of valve actuation is as follows.

The effect of this sequence is that the working gas passes through the cooler twice (once in each direction), but only once through the heater and regenerator (in one direction) during the course of one cycle. That is. On the contrary, the conventional Stirling cycle
In the engine, working gas passes through the heater, cooler and regenerator in both directions during each cycle. Thus, the present invention eliminates some of the gas friction that occurs in conventional Stirling cycle engines. In addition, as long as there is friction caused by the passage of gas through the regenerator, it turns into heat, which is transferred to the expansion space rather than the cooler.

The heater (12A, 13A) is heated by a heating device (not shown) such as a combustor or solar energy, and the cooler (12B, 13A) is heated.
B) is cooled with a water jacket, air or other suitable heat sink.

The engine cycle according to the invention differs from the conventional Stirling cycle in that a much higher compression ratio is possible. The ratio of the excluded volume of the cylinder to the volume of the heat exchanger assembly determines the compression ratio, because the total volume of working gas is excluded in the heat exchanger assembly and is confined there in compression by the valves at each end. To do. The relatively small volume of the heat exchanger assembly results in a high compression ratio.

The high compression ratios that can be achieved with this engine are desirable in that it produces a large output for its size. However, high compression ratios involve handy caps in the form of extremely high pressures in the machine at the end of the compression stroke. This high pressure raises the temperature of the working gas as the compression stroke progresses, increasing the work consumed to regenerate the working gas.

To mitigate this effect, each heat exchanger assembly is arranged to limit the compression heating of the working gas.

This is because the cold gas from the cold heat exchanger (or the central regenerator if used) is
Equip each heat exchanger so that it is not heated immediately when it enters the heater, such as by using a heater tube with a diameter considerably larger than that used in the cycle machine, or by using only one heater tube It is carried out by
Thus, the heating process can be delayed by reducing the heat exchange area of the heater.

Conversely, the regenerator and cooler tubes can be designed for rapid heat transfer so that the gas entering either will almost immediately reach the regenerator or cooler temperature.

The heater can be provided with heat transfer characteristics such that the gas in the heater (12A, 13A) at the start of the compression stroke approaches the temperature of the heater tube at the start of compression. Referring to FIG. 3, as the compression stroke proceeds, the hot gas is progressively pushed toward the valve device (16A or 17A) and further heated by compression. In order to mitigate this effect, an expansion end regenerator (14A, 14B) is interposed between the heater and the hole to the expansion space, and the heat from the gas extruded from the heater and entering the expansion end regenerator is It is absorbed by the regenerator so that the temperature rise is moderated. If the regenerator has sufficient heat capacity, the temperature rise in the regenerator during any one cycle will be minimal. However, many cycles are repeated, and the working gas bypasses (20,2
When passing 1), it is possible to raise the temperature of the expansion end regenerator above the temperature of the heater, thereby increasing the pressure of the working gas during the expansion stroke and improving engine performance. This effect depends on the volume of the elements of the heat exchanger assembly, the compression ratio of the engine, the temperature of the gas entering the heater during the compression stroke and the heat transfer coefficient within the heater, and the analytical methods known to those skilled in the art. Can be calculated by

By appropriately sizing the regenerator, heater tube and cooler tube to the excluded volume of the cylinder, almost all of the gas in the heater tube at the beginning of the compression stroke is expanded end regenerated until the end of the stroke. It is pushed into the reactor so that during the course of its travel the entire volume of the heater tube is filled with the gas that has just passed through the cooler or central regenerator.

Therefore, at the start of the expansion stroke, the valve device (16A, 17
When A) opens, the gas is heated to the temperature of the expansion end regenerator while expanding to enter the expansion space in the cylinder. The temperature of the gas exceeds the heater temperature, at least initially. Although the temperature of the gas in the heater decreases as the expansion stroke progresses, the gas must pass through the expansion end regenerator on the way into the cylinder, and in the process, close to or above the maximum temperature of the heater tube. Be heated.

A bypass arrangement similar to that shown at the expansion end may be provided at the compression end. In that case, the working gas is cooled by the cooler (12
B, 13B) into the compression space, but the central regenerator (23A, 2A
It should leave the compression space through a bypass that directly communicates with 3B).

During the isolation phase, all valves in the isolated heat exchanger assembly receive a positive pressure within the heat exchanger. However, when the valve device (16A or 17A) is opened and the working gas enters the expansion space of the cylinder, the pressure in the cylinder is higher than the pressure in the heat exchanger assembly which is beginning to compress. Therefore, there is a pressure differential between the expansion end of the cylinder and the heat exchanger assembly, and the working gas is compressed into the heat exchanger assembly while the pressure in the expansion space is higher than the pressure in the compression space. Ultimately, however, the pressure in the expansion space drops and the pressure on the valve arrangement of the heat exchanger, in which the gas is being compressed, is diverted.

To address this problem, the valve that directly communicates with the expansion space of a high pressure engine is pressure tight in both directions. For applications such as heat pumps where the temperature is relatively low and lubricating oil can be used, a simple sluice valve (Figs. 4A and 4B) can be used. In such valves, a partition plate (30) crosses the flow of working gas. In the open position, the holes (31) in the partition plate are aligned with the flow path, allowing gas to flow freely.
When the partition plate is closed, the flat plate blocks the gas flow. Fourth B
As shown in the figure, if both sides of the partition plate are properly smooth and the end of the opening through which the working gas passes can be polished to form a smooth valve seat, the partition plate is first pushed to one side of the hole. If the gas pressure reverses, it will be pushed to the opposite side of the hole. Therefore, a pressure seal is formed in either direction. A suitable sealing device (33) further seals against leaks on the surface of the partition plate (30). Sealed solenoid operated valves can also be used.

For high temperature applications, dual poppet valves (Figure 4C, Figure 35) can be used. Other devices known for pressure sealing of valves will be apparent to those skilled in the art.

In an embodiment of the invention using piston and crankshaft deployment, the timing of valve movement is synchronized with piston movement by conventional mechanical, electrical or electronic devices that sense crankshaft position. .

It is possible to use more than two heat exchanger assemblies. There are at least two practical advantages to using a relatively large number of tubes. This advantage arises because only one tube set actively receives and releases gas during the exchange process. During the power / compression stroke only two tube sets receive and release gas. The rest of the tubes are confined during the "isolation" stage, allowing heat transfer to allow time for temperature regulation. Therefore, it is not necessary to transfer heat from the heater to the gas contained therein very quickly. Theoretically, until compression is complete and the valve has confined the working gas to the heat exchanger assembly, the cold gas entering the heater during compression is too warm due to conduction and convection from the heater wall. I can't.

This design allows the heat transfer between the heater tube and the working gas to be relatively slow, which greatly simplifies the manufacture of the heater. In the extreme case, a single heater tube is used, which makes it very easy to manufacture.

Another advantage of using a single heater tube (or a small number of relatively large heater tubes) is that the frictional drag of the gas can be significantly reduced.

For optimum operation, the machine according to the invention should be balanced, ie the working gas volumes associated with the heat exchanger assembly should be substantially equal. Most practical machines
Since the piston cannot completely scaveng the cylinder and the valve hole, it naturally balances during operation. A small amount of gas remains in the compression space and compression space valve holes at the end of each power / compression stroke. If the just-pressurized heat exchanger assembly contains a disproportionately large amount of gas, the residual gas volume in the compression space and the compression space valve holes will also be disproportionately high. Therefore, when the compression space valve is closed for the gas just compressed at the end of the compression stroke and one compression space valve is opened for the exchange stroke, the extra gas is about to enter the exchange stroke. Transferred to the heat exchanger assembly to slightly increase the amount of gas in the heat exchanger assembly. In this way, a small amount of gas is automatically redistributed from the heat exchanger assembly containing excess gas to the heat exchanger assembly containing less gas as the engine cycle is cycled to balance. Be done.

When the engine is to be started after the working gas has been naturally redistributed, such as leaking through a valve, it can be due to the starting mechanism to balance the machine as an engine. That is, it may be necessary to crank the engine until near equilibrium is reached. If the engine was already in equilibrium when it was to be started, it would only have to be cranked for one cycle before starting.

Claims (24)

[Claims] 1. A cylinder having one end and the other end connected to each other through at least two first and second heat exchanger assemblies that are separated from each other, and each heat exchanger assembly is arranged in series. A heated heat exchanger device and a cooled heat exchanger device, the hot end of the heat exchanger assembly being attached to the hot end of the cylinder, the heat exchanger assembly being at each of the ends. A valve device, the cylinder houses a double-acting reciprocating piston device, the piston device periodically removing or moving a fixed amount of gas from each heat exchanger assembly. And a fixed amount of gas in the pair of heat exchanger assemblies that provides the first and second heat exchanger assemblies is alternately trapped and released from the heat exchanger assembly by the valve device. The hot gas engine as (A) the piston is at substantially the end of a stroke towards the end of the cylinder communicating with the heated heat exchanger device via the valve device, and A valve assembly at both ends of the exchanger assembly is in an open position, a valve assembly at both ends of the second heat exchanger assembly is in a closed position, and a first volume of gas is in the first heat exchange. A second volume of gas is press-fitted into the second heat exchanger assembly and further heat exchanger assemblies, if any, are disposed within the reactor assembly and the cylinder. The valve device at the hot end of the first heat exchanger assembly is closed when the heat exchanger assembly contains a quantity of compressed gas and the second heat is closed at about the same time. The valve device at the hot end of the exchanger assembly is opened to allow the second volume of gas to flow through the piston in the cylinder. Of the gas of the first volume from the cylinder on the second side of the piston through the valve device at the cold end of the first heat exchanger assembly. Compressing and pushing into the first heat exchanger assembly; (b) the stroke of the piston towards the end of the cylinder that communicates with the cold end of the heat exchanger assembly through the valve device. The valve device at the cold end of the first heat exchanger assembly is closed at about the end of, and the valve device at the cold end of the second heat exchanger assembly is opened at about the same time. The second volume of gas is discharged from the cylinder on the first side of the piston through the second heat exchanger assembly into the cylinder on the second side towards the piston and is simultaneously press-fitted. The first volume of gas is The first heat exchanger assembly is temporarily maintained in the heat exchanger assembly, and when the engine device has three or more heat exchanger assemblies, the first heat exchanger assembly is temporarily cycled according to the operating method of the engine. (C) the second heat exchanger when the piston is approximately at the end of the process towards the cylinder end communicating with the hot end of the heat exchanger assembly via the valve device. The valve device at the hot end of the assembly is closed and at about the same time, one of the other heat exchanger assemblies is added as a first heat exchanger assembly to the cycle of operation of the engine. First
Opening the valve device at the hot end of the heat exchanger assembly to direct the first volume of gas to the piston in the cylinder through the valve device at the hot end of the first heat exchanger assembly. The second volume of gas through the valve device at the cold end of the second heat exchanger assembly from the cylinder on the second side of the piston. Compressing and pushing into the second heat exchanger assembly; (d) approximately at the end of the stroke toward the cylinder end where the piston communicates through the valve device to the cold end of the heat exchanger assembly. At one time, the valve device at the cold end of the second heat exchanger assembly is closed and at about the same time the valve device at the cold end of the first heat exchanger assembly is opened towards the piston. Front from the cylinder on the first side Exhausting the first volume of gas through the first heat exchanger assembly into the cylinder on the second side of the piston while simultaneously delivering the compressed second volume of gas to the second volume. The second heat exchanger assembly is temporarily maintained in the heat exchanger assembly, and when the engine system further has three or more heat exchanger assemblies, the second heat exchanger assembly is temporarily operated. Removing one of the other heat exchanger assemblies into the cycle of the operating method of the engine as a second heat exchanger assembly; and (e) from (a) to (d). ) The method including repeating the cycle of the engine operating method shown in the steps up to. 2. A regenerator device in series between each of the heated heat exchanger device and the cooled heat exchanger device in each of the heat exchanger assemblies. The method according to item 1. 3. A regenerator device in series between the heated heat exchanger device and the valve device at each hot end of the heat exchanger assembly. The method described in. 4. The gas stream of step (d), wherein the gas stream of step (b) passes through another conduit bypassing the heated heat exchanger arrangement of the second heat exchanger assembly. 7. The method of claim 1 wherein the fluid is passed through another conduit that bypasses the heated heat exchanger arrangement of the first heat exchanger assembly. 5. A regenerator device is interposed in series between the valve at the hot end of the heat exchanger assembly and the heated heat exchanger device, and the gas flow of step (b) and the step (b). The method of claim 1 wherein said gas stream in d) is passed through a separate conduit that bypasses both said regenerator and said heated heat exchanger arrangement. 6. A cylinder containing a double acting reciprocating piston arrangement and at least two heat exchanger assemblies, each in series with a heated heat exchanger arrangement and a cooled exchanger arrangement. The heat exchanger assembly has one end connected into the cylinder on one side of the piston via a valve device and the other end on the other side of the piston via a valve device. A heat exchanger assembly connected in the cylinder, the hot end of each heat exchanger assembly being connected to the cylinder on the same side of the piston, and the opening and closing of the valve in relation to the movement of the piston A device to adjust the time,
While the piston travels one way, it connects one of the heat exchanger assemblies to the expansion space and another compression space of the heat exchanger assembly, and the piston is A device for connecting one of the heat exchanger assemblies to the expansion space and the compression space during the return stroke, for storing the kinetic energy of the piston during the reciprocating cycle and returning the energy to the piston. And a closed cycle hot gas engine having the device of. 7. A regenerator device in series between each of said heated heat exchanger device and said cooled heat exchanger device in each of said heat exchanger assemblies. Engine described in. 8. The method of claim 6 including a conduit bypassing said heated heat exchanger arrangement in each of said heat exchanger assemblies and incorporating a valve arrangement in each of said conduits. Engine. 9. A regenerator device in series between the valve device and the heated heat exchanger device at the hot end of each of the heat exchanger assemblies. Engine described in. 10. An additional regenerator device in series between the valve device at each hot end of the heat exchanger assembly and the heated heat exchanger device, the heat exchanger assembly comprising: 8. An engine according to claim 7, incorporating conduits bypassing each of said heated heat exchanger arrangements and said additional regenerator arrangements, each incorporating a valve arrangement. 11. A cylinder having one end and the other end connected via at least two first and second heat exchanger assemblies that are separated from each other, and each heat exchanger assembly is arranged in series. A heat absorption heat exchanger device and a heat release heat exchanger device,
Each heat exchanger assembly includes a valve device at each end, the cylinder houses a double-acting reciprocating piston device, and the piston device periodically deviates from each heat exchanger assembly by a fixed amount. A certain amount of gas in the pair of heat exchanger assemblies, which becomes the first and second heat exchanger assemblies, is alternately removed by the valve device by removing the gas or moving the gas by a certain amount of gas. A method of operating a heat pump to be trapped within and released from the heat exchanger assembly, the method comprising: (a) the piston communicating with the heat absorbing heat exchanger device via the valve device; Near the end of the stroke towards the end of the cylinder, the double ended valve arrangement on the first heat exchanger assembly is in the open position and the double ended valve arrangement on the second heat exchanger assembly. Is in the closed position and has the first volume Gas is disposed within the first heat exchanger assembly and the cylinder, and a second volume of gas is press fit into the second heat exchanger assembly, and yet another heat exchanger assembly. Is present, the valve device at the heat absorbing end of the first heat exchanger assembly is included when a compressed amount of gas is contained in each of the other heat exchanger assemblies. Closed and at about the same time the valve device at the heat absorbing end of the second heat exchanger assembly is opened to allow the second volume of gas to expand into the cylinder toward the first side towards the piston. , While simultaneously compressing the first volume of gas from the cylinder on the second side of the piston through the valve device at the heat release end of the first heat exchanger assembly to provide the first heat exchange. Pushing through the valve assembly through the valve device; At about the end of the end-to-end stroke to the cylinder in communication with the heat release end of the exchanger assembly, the valve device at the heat release end of the first heat exchanger assembly is closed at about the same time. The valve device at the heat release end of the second heat exchanger assembly to open the second volume of gas from the cylinder on the first side of the piston and through the second heat exchanger assembly. Discharging into the cylinder on the second side of the piston while maintaining the press-fitted first volume of gas in the first heat exchanger assembly, and further including three or more heat pumps. A heat exchanger assembly, the step of temporarily removing the first heat exchanger assembly from the cycle of the method of operating the heat pump; The sheath that communicates with the heat absorbing end of the exchanger assembly. At about the end of the process towards the Linda end, the valve device at the heat absorbing end of the second heat exchanger assembly is closed, at about the same time,
The valve device at the high temperature end of the first heat exchanger assembly in addition to the cycle of the operating method of the heat pump, wherein one of the other heat exchanger assemblies is a first heat exchanger assembly. Open and expand the first volume of gas through the valve device at the heat absorbing end of the first heat exchanger assembly to a first side in the cylinder toward the piston, while at the same time the piston A second volume of gas from the cylinder on the second side of the cylinder through the valve device at the heat release end of the second heat exchanger assembly into the second heat exchanger assembly. Pushing in; (d) the second heat exchanger when the piston is approximately at the end of its stroke towards the cylinder end communicating with the heat release end of the heat exchanger assembly through the valve device. Closing the valve device at the heat release end of the assembly From the cylinder on the first side, sometimes opening the valve device at the heat release end of the first heat exchanger assembly, toward the piston, through the first heat exchanger assembly to the first of the pistons of the piston. Exhausting the first volume of gas into the cylinder on the second side while simultaneously maintaining the compressed second volume of gas in the second heat exchanger assembly; and When the heat pump has three or more heat exchanger assemblies, the second heat exchanger assembly is temporarily removed from the cycle of the operation method of the heat pump, and the heat exchanger assembly of the other heat exchanger assembly is removed. Adding one of them as a second heat exchanger assembly to the heat pump operating method cycle; (e) the heat pump operating method cycle shown in steps (a) to (d) above. A method that includes repeating steps. 12. A regenerator device in series between each of said heat absorption heat exchange device and said heat release heat exchange device in each of said heat exchanger assemblies. The method described in. 13. A method according to claim 11, wherein a regenerator device is interposed in series between the valve device at the heat absorbing end of the heat exchanger assembly and the heat absorbing heat exchanger device. 14. The gas flow of step (b) is passed through another conduit that bypasses the heat absorbing heat exchanger arrangement of the second heat exchanger assembly, and the gas flow of step (d) is 12. The method of claim 11, wherein the method comprises: passing through another conduit that bypasses the heat absorption heat exchanger arrangement of the first heat exchanger assembly. 15. An additional regenerator device is interposed in series between the valve device at each heat absorption end of the heat exchanger assembly and the heat exchanger device to be heated, the gas of step (b) being included. 13. The method of claim 12 wherein the stream and the gas stream of step (d) pass through another valved conduit that bypasses both the additional regenerator device and the heat absorption heat exchanger device. 16. A cylinder containing a double acting reciprocating piston device and at least two heat exchanger assemblies, comprising:
Each includes a heat-absorption heat-exchanger device and a heat-release heat-exchanger device connected in series, one end of each heat-exchanger assembly being connected to the inside of the cylinder on one side of the piston via a valve device. And the other end is connected via a valve device into the cylinder on the other side of the piston, and the heat absorbing end of each heat exchanger assembly is connected to the cylinder on the same side of the piston. A closed cycle heat pump including a heat exchanger assembly, a device for adjusting the opening and closing timing of the valve in relation to the movement of the piston, and a device for moving the piston in a periodic reciprocating motion. 17. A heat pump according to claim 16, wherein a regenerator device is interposed in series between each heat absorption heat exchange device and heat release heat exchanger device of said heat exchanger assembly. . 18. The heat pump according to claim 16, wherein a regenerator device is interposed in series between the valve device at the heat absorption end of each heat exchanger assembly and the heat absorption heat exchanger device. . 19. A heat pump according to claim 16 including conduits for bypassing the heat absorbing heat exchanger devices of each heat exchanger assembly, and valve devices being installed in each of the conduits. 20. An additional regenerator device is interposed in series between the valve that connects the end of the heat absorption heat exchanger device to the cylinder and the heat absorption heat exchanger device, and each heat exchanger assembly. 18. The heat pump of claim 17 incorporating a valved conduit that bypasses the heat-absorption heat exchanger device and the additional regenerator device. 21. A compression chamber and an expansion chamber, a piston device for reducing the volume of one of the chambers and increasing the volume of the other chamber, and a volume to be heated are connected to the expansion chamber,
It further comprises a heat exchanger device connecting a volume to be cooled to the compression chamber, and a quantity of a compressible gas trapped for circulation through the chamber and the heat exchanger device. Stirling for converting energy between
In a cycle-type device, first and second heat exchangers forming a heat exchanger device, each having a heated volume and a cooled volume, which communicate with each other, and a first heat exchanger of the first heat exchanger. The heated volume of the second heat exchanger is communicated with the expansion chamber and the cooled volume of the second heat exchanger is communicated with the compression chamber of the second heat exchanger. A controller for communicating with the expansion chamber and for communicating the cooled volume of the first heat exchanger with the compression chamber under substantially maximum pressure achieved in each operating cycle. An energy conversion device for confining compressed gas in each heat exchanger periodically and alternately. 22. The control device includes a valve device connecting between the chamber and the heat exchanger, dividing the fixed amount of gas into two separate parts, which parts are alternated. 22. The energy conversion device according to claim 21, which communicates with each of the chambers. 23. Further comprising separate inlet and outlet valve arrangements connecting said expansion chamber to each of said heated volumes of said heat exchanger, said outlet valve of said heated volume and of said cooled volume. 22. The energy conversion device according to claim 21, wherein the energy conversion device communicates with the heat exchanger between them. 24. The energy conversion device according to claim 23, further comprising a regenerator connected between the heated portion of each heat exchanger and the inlet valve.