JP2006275316A - Heat exchanger and stirling engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger and a Stirling engine improved in heat exchanging characteristics. <P>SOLUTION: This heat exchanger 18 for the Stirling engine comprises a circular corrugated fin 421, formed by cylindrically rounding a straight corrugated fin formed by continuously connecting V-shaped cross-sectional shapes, an outer cylindrical member 41 having an inner diameter approximately same as an outer diameter of the circular corrugated fin 421 to insert the circular corrugated fin 421 therein along the axial direction, and an inner cylindrical member 422 having an outer diameter slightly larger than an inner diameter of the circular corrugated fin 421 and inserted in the circular corrugated fin 421 inserted into the outer cylindrical member 41 along the axial direction. A fin material end portion composing an axial end face of the circular corrugated fin 421 is machined to reduce flow resistance. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat exchanger (heat radiator, heat absorber) and a Stirling engine in which the heat exchanger is used.

  First, with reference to FIGS. 12-14, the heat radiator which is a heat exchanger of the high temperature side of a Stirling engine is demonstrated. In addition, since the description of the heat absorber which is a low temperature side heat exchanger is the same as that of a heat radiator, it abbreviate | omits.

  In the Stirling engine, a heat exchanger 18 shown in FIG. 12 is provided as a radiator so as to surround the displacer. In addition, the heat exchanger 18 includes an outer cylindrical member 41 constituting a radiator and an annular corrugated fin 421 fitted into the outer cylindrical member 41. The annular corrugated fins 421 are formed of a corrugated (corrugated: corrugated shape) thin plate in a cylindrical shape.

  When the annular corrugated fin 421 is viewed from the side, a plurality of V-shaped grooves 421a are formed. That is, the annular corrugated fin 421 has a so-called folded plate structure.

Here, a portion protruding to the center side of the outer cylindrical member 41 is a bottom portion 421b of the groove 421a, and a portion protruding to the inner peripheral surface side of the outer cylindrical member 41 is a top portion 421c of the groove 421a. The diameter of the circle formed by smoothly connecting the top portions 421c (the outer diameter of the annular corrugated fin 421) and the inner diameter of the outer cylindrical member 41 are substantially equal, and the outer cylindrical member 41 and the corrugated fin 421 are coaxial with each other. Yes. FIG. 13 is a view showing a state in which the inner peripheral surface of the outer cylindrical member 41 and the top portion 421c of the annular corrugated fin 421 are fixed.
JP 2002-81774 A JP 2002-243291 A

  In the manufacturing process of the conventional corrugated fin 421 of the conventional heat exchanger, first, after a slit process for cutting a single plate into a constant width, a plate material with a constant width cut by pressing is bent, and a folded plate A shape is formed.

  In the above-described manufacturing process, as shown in FIGS. 13 and 14, the burr 500 is formed on the axial end surface of the annular corrugated fin 421 by slit processing. The burr 500 extends in a direction perpendicular to the working gas flow path in the closed circuit in the Stirling refrigerator. Therefore, the fluidity of the working gas is lowered by the axial end surface of the annular corrugated fin 421 and the above-described burr 500. That is, the pressure loss of the working gas is increased by the axial end face and the burr 500. Therefore, the flow rate of the working gas passing through the heat exchanger 42 is reduced. As a result, the amplitude of the piston and displacer of the Stirling engine is reduced, and the heat exchange characteristics between the annular corrugated fin 421 and the outer cylindrical member 41 are deteriorated. Accordingly, the cooling performance of the Stirling refrigerator is reduced.

  The present invention has been made in view of the above-described problems, and an object thereof is to provide a heat exchanger and a Stirling engine having improved heat exchange characteristics.

  The heat exchanger according to the present invention has an annular corrugated fin in which linear corrugated fins having V-shaped cross-sectional shapes connected continuously are rounded into a cylindrical shape, and an inner diameter substantially equal to the outer diameter of the annular corrugated fin, And an outer cylindrical member (a heat radiating part or a heat absorbing part) in which an annular corrugated fin is inserted along the axial direction. Moreover, the flow resistance reduction process is given to the fin material edge part which comprises the axial direction end surface of an annular corrugated fin. According to this configuration, since the flow resistance of the working gas is reduced, the heat exchange performance of the heat exchanger for the Stirling engine is improved.

  Moreover, the flow resistance reduction process is given to the plate-shaped fin material before forming a linear corrugated fin. According to this configuration, the flow resistance reduction process can be easily performed, and the manufacturing cost can be reduced.

  Further, the flow resistance reduction process is a chamfering process including deburring. According to this configuration, the flow resistance reduction processing is facilitated, and the manufacturing cost can be reduced.

  The Stirling engine of the present invention includes a cylinder assembled in a casing enclosing a working medium, a piston that reciprocates in the cylinder, a displacer that reciprocates in a state having a phase difference with respect to the piston in the cylinder, and a piston A compression space formed between the compressor and the displacer, an expansion space provided on the opposite side of the compression space of the displacer, and the heat exchanger described above provided in a communication path that connects the compression space and the expansion space. It has. According to this configuration, a Stirling engine having high heat exchange characteristics can be obtained.

  According to the present invention, the heat exchange performance of the heat exchanger is improved, and the efficiency of the Stirling engine is improved.

  Hereinafter, an embodiment of a heat exchanger and a Stirling engine of the present invention and a Stirling refrigerator in which they are used will be described.

  In the present specification, the “cooling box” is a concept including all of “refrigerator”, “freezer”, and “freezer refrigerator”.

  In the present embodiment, a Stirling refrigerator as a Stirling engine and a Stirling refrigerator as a Stirling engine-equipped device equipped with the Stirling refrigerator will be described. The Stirling engine according to the present invention is a Stirling refrigerator. For example, it is used also as a generator.

  FIG. 1 is a piping system diagram of a Stirling cooler according to an embodiment of the present invention.

  As shown in FIG. 1, the Stirling refrigerator 1 includes a Stirling refrigerator 4 (Stirling engine) having a heat radiating unit 2 and a heat absorbing unit 3, a high temperature side evaporator 5 attached to the heat radiating unit 2, and a high temperature side condenser. 7 and the first high temperature side circulation circuit including the pipes 2A and 2B (first circulation circuit), the high temperature side evaporator 5, the circulation pump 6, the dew prevention pipe 9 and the second high temperature side circulation including the pipes 2C, 2D and 2E. A circuit (second circulation circuit) and a low-temperature side circulation circuit including a low-temperature side condenser 10, a low-temperature side evaporator 11, and pipes 3 </ b> A and 3 </ b> B attached to the heat absorption unit 3 are provided. The first high temperature side circulation circuit cools the heat radiating part 2 of the Stirling refrigerator 4, and the second high temperature side circulation circuit supplies heat to the dew condensation prevention pipe 9. In addition, the low-temperature side circulation circuit performs heat exchange between the air in the refrigerator and the heat absorption unit 3 of the Stirling refrigerator 4.

Water (H ₂ O) or the like is sealed as a refrigerant in the first and second high temperature side circulation circuits. The refrigerant evaporated in the high temperature side evaporator 5 reaches the high temperature side condenser 7 via the pipe 2A (high temperature side conduit) (broken line arrow in FIG. 1). The refrigerant is condensed by heat exchange with the outside air in the high temperature side condenser 7. In order to promote this heat exchange, a fan 8 that generates an air flow in the vicinity of the high-temperature side condenser 7 is provided. The condensed refrigerant returns to the high temperature side evaporator 5 through the pipe 2B (high temperature side return pipe). In the first high temperature side circulation circuit, the heat generated in the heat radiating unit 2 can be transferred to the high temperature side condenser 7 by utilizing the natural circulation caused by the evaporation and condensation of the refrigerant. The side condenser 7 is disposed above the high temperature side evaporator 5. Further, in order to adjust the boiling point of the refrigerant, the pressure in the circulation circuit system is adjusted (depressed from the atmospheric pressure).

  On the other hand, a pipe 2 </ b> C is connected to the lower part of the high temperature side evaporator 5. Liquid phase refrigerant flows from the high temperature side evaporator 5 into the pipe 2C. The refrigerant flowing into the pipe 2 </ b> C reaches the circulation pump 6 provided below the Stirling refrigerator 4. The refrigerant discharged from the circulation pump 6 is sent to the dew prevention pipe 9 via the pipe 2D. Here, the refrigerant flowing in the dew condensation prevention pipe 9 is kept at a relatively high temperature by the heat given from the heat radiating unit 2 of the Stirling refrigerator 4. Therefore, the dew condensation prevention pipe 9 can be arranged in the front opening of the refrigerator to suppress the dew condensation at the door portion or the like. The refrigerant that has flowed through the dew condensation prevention pipe 9 returns to the high temperature side evaporator 5 through the pipe 2E. Thus, forced circulation by the circulation pump 6 is performed in the second high temperature side circulation circuit.

  Carbon dioxide, hydrocarbons, and the like are sealed as refrigerant in the low temperature side circulation circuit. The refrigerant condensed in the low temperature side condenser 10 reaches the low temperature side evaporator 11 through the pipe 3A (low temperature side conduit). Heat exchange is performed by evaporating the refrigerant in the low temperature side evaporator 11. In order to promote this heat exchange, a fan 12 that generates an air flow in the vicinity of the low-temperature evaporator 11 is provided. After the heat exchange, the gasified refrigerant returns to the low temperature side condenser 10 through the pipe 3B (low temperature side return pipe). In the low-temperature side circulation circuit, the low-temperature side evaporator 11 is thus condensed on the low-temperature side so that the cold generated in the heat-absorbing unit 3 can be transmitted using the natural circulation caused by the evaporation and condensation of the refrigerant. It is arranged below the vessel 10. Further, the pressure in the circulation circuit system is adjusted in order to adjust the boiling point of the refrigerant.

When the Stirling refrigerator 4 is operated, heat generated in the heat radiating unit 2 of the refrigerator 4 is heat-exchanged with air via the high temperature side condenser 7. On the other hand, the cold generated in the heat absorption part 3 of the Stirling refrigerator 4 is heat-exchanged with the air in the refrigerator through the low temperature side evaporator 11. The warmed airflow from the inside of the refrigerator is sent again to the vicinity of the low-temperature side evaporator 11 and repeatedly cooled.

  Next, an example of the structure of the Stirling refrigerator 4 and its operation will be described with reference to FIG.

  As shown in FIG. 2, the Stirling refrigerator 4 of the present embodiment is a free piston type Stirling engine, and includes a casing 30, a cylinder 13 assembled to the casing 30, and a reciprocating motion in the cylinder 13. Piston 14 and displacer 15, regenerator 16, working space 17 including compression space 17A and expansion space 17B, heat radiating portion 2, heat absorbing portion 3, linear motor 23 as piston driving means, and piston spring 24, a displacer spring 25, a displacer rod 26, and a back pressure space 27.

  In the example of FIG. 2, the outer shell (outer wall) of the Stirling refrigerator 4 is not constituted by a single container, but is positioned on the back pressure space 27 side and the casing 30 (vessel portion) and on the working space 17 side. The heat dissipating part 2, the tube 18A and the heat absorbing part 3 are mainly configured. The casing 30 defines a back pressure space 27. Various parts including the cylinder 13, the linear motor 23, the piston spring 24, and the displacer spring 25 are assembled to the casing 30. The outer shell is filled with a working medium such as helium gas, hydrogen gas, or nitrogen gas.

  The cylinder 13 has a substantially cylindrical shape, and receives therein a piston 14 and a displacer 15 as a free piston so as to be capable of reciprocating. In the cylinder 13, the piston 14 and the displacer 15 are coaxially spaced apart, and the piston 14 and the displacer 15 divide the working space 17 in the cylinder 13 into a compression space 17 </ b> A and an expansion space 17 </ b> B. More specifically, the working space 17 is a space located closer to the displacer 15 than the end face of the piston 14 on the displacer 15 side, and a compression space 17A is formed between the piston 14 and the displacer 15, and the displacer 15 and the heat absorbing portion. 3, an expansion space 17 </ b> B is formed. The compression space 17 </ b> A is mainly surrounded by the heat radiating part 2, and the expansion space 17 </ b> B is mainly surrounded by the heat absorption part 3.

  Between the compression space 17A and the expansion space 17B, a regenerator 16 in which a film is wound with a predetermined gap on the inner peripheral surface of the tube 18A is disposed. The compression space 17A and the expansion space 17B communicate with each other. Thereby, a closed circuit is formed in the Stirling refrigerator 4. The working medium sealed in the closed circuit flows in accordance with the operations of the piston 14 and the displacer 15, thereby realizing a reverse Stirling cycle described later.

  A linear motor 23 is disposed in the back pressure space 27 located outside the cylinder 13. The linear motor 23 includes an inner yoke 20, a movable magnet portion 21, and an outer yoke 22, and the piston 14 is driven in the axial direction of the cylinder 13 by the linear motor 23.

  One end of the piston 14 is connected to a piston spring 24 constituted by a leaf spring or the like. The piston spring 24 functions as an elastic force applying means for applying an elastic force to the piston 14. By applying an elastic force to the piston spring 24, the piston 14 can be reciprocated in the cylinder 13 more stably and periodically. One end of the displacer 15 is connected to a displacer spring 25 via a displacer rod 26. The displacer rod 26 is disposed through the piston 14, and the displacer spring 25 is constituted by a leaf spring or the like. The peripheral edge of the displacer spring 25 and the peripheral edge of the piston spring 24 are supported by a support member that extends from the linear motor 23 toward the back pressure space 27 of the piston 14 (hereinafter sometimes referred to as the rear).

  A back pressure space 27 surrounded by a casing 30 is disposed on the opposite side of the piston 14 from the displacer 15. The back pressure space 27 includes an outer peripheral region located around the piston 14 in the casing 30 and a rear region located closer to the piston spring 24 (rear side) than the piston 14 in the casing 30. There is also a working medium in the back pressure space 27.

  The heat radiating part 2 is attached to the casing 30 via the base member 30A. The heat radiation part 2 and the heat absorption part 3 are connected via the tube 18A. The heat dissipating part 2 and the heat absorbing part 3 are constituted by an internal heat exchanger 18 and an internal heat exchanger 19, respectively. The internal heat exchangers 18 and 19 perform heat exchange between the compression space 17A and the expansion space 17B, the evaporator attached to the heat radiating unit 2, and the condenser attached to the heat absorbing unit 3, respectively.

  A balance mass 29 is attached to the rear side of the casing 30 via a leaf spring 28. The balance mass 29 is a mass member that absorbs vibration of the casing 30 that is generated when the piston 14 and the displacer 15 vibrate. Specifically, when the vibration is generated in the casing 30 due to the vibration of the piston 14 or the displacer 15, the balance mass 29 is vibrated so as to follow the vibration of the casing 30, whereby the Stirling refrigerator 4. Vibration is reduced.

  For example, a first distance sensor is provided on the end surface of the piston 14 on the displacer 15 side, and a second distance sensor is provided on the end surface of the displacer 15 on the heat absorbing unit 3 side. The first distance sensor can measure a change with time of the interval between the piston 14 and the displacer 15 during the operation of the Stirling refrigerator 4. Further, the second distance sensor can measure a change with time of the interval between the displacer 15 and the heat absorbing unit 3 when the Stirling refrigerator 4 is operated.

  Next, the operation of the Stirling refrigerator 4 will be described.

  First, the linear motor 23 is actuated to drive the piston 14. The piston 14 driven by the linear motor 23 approaches the displacer 15 and compresses the working medium (working gas) in the compression space 17A.

  When the piston 14 approaches the displacer 15, the temperature of the working medium in the compression space 17 </ b> A rises, but heat generated in the compression space 17 </ b> A is released to the outside by the heat radiating unit 2. Therefore, the temperature of the working medium in the compression space 17A is maintained almost isothermal. That is, this process corresponds to an isothermal compression process in a reverse Stirling cycle.

  After the piston 14 approaches the displacer 15, the displacer 15 moves to the heat absorption unit 3 side. On the other hand, the working medium compressed in the compression space 17A by the piston 14 flows into the regenerator 16, and further flows into the expansion space 17B. At that time, the heat of the working medium is stored in the regenerator 16. That is, this process corresponds to an isovolumetric cooling process in a reverse Stirling cycle.

  The high-pressure working medium that has flowed into the expansion space 17B expands when the displacer 15 moves to the piston 14 side (rear side). As the displacer 15 moves rearward in this way, the center portion of the displacer spring 25 is also deformed so as to protrude rearward.

  As described above, when the working medium expands in the expansion space 17B, the temperature of the working medium in the expansion space 17B decreases, but external heat is transferred into the expansion space 17B by the heat absorbing portion 3, The inside of the expansion space 17B is kept almost isothermal. That is, this process corresponds to an isothermal expansion process of a reverse Stirling cycle.

  Thereafter, the displacer 15 starts to move away from the piston 14. Thereby, the working medium in the expansion space 17B passes through the regenerator 16 and returns to the compression space 17A side again. At this time, since the heat stored in the regenerator 16 is applied to the working medium, the working medium is heated. That is, this process corresponds to a constant volume heating process of a reverse Stirling cycle.

  By repeating this series of processes (isothermal compression process-isovolume cooling process-isothermal expansion process-isovolume heating process), an inverse Stirling cycle is configured. As a result, the endothermic part 3 gradually becomes low temperature and has an extremely low temperature (for example, about −50 ° C.). On the other hand, the heat radiating part 2 gradually becomes high temperature (for example, about 60 ° C.). As described above, the cold heat in the heat absorption unit 3 is supplied into the refrigerator through the low temperature side circulation circuit, and the heat in the heat dissipation unit 2 is released to the outside of the refrigerator through the first and second high temperature side circulation circuits. Is done.

  Hereinafter, with reference to FIG. 3 and FIG. 4, the heat exchanger of embodiment of this invention is demonstrated. In addition, in each figure explaining the heat exchanger of this Embodiment, the code | symbol same as the code | symbol attached | subjected in FIGS. 12-14 is attached | subjected to the site | part which has the same structure and the same function as a prior art. ing. Moreover, in this Embodiment, although the structure of the heat exchanger 18 as a heat radiator is demonstrated, the structure and the material of a member are applicable to the heat exchanger 19 as a heat absorber. Therefore, unless otherwise specified, the configuration of the radiator is also applied to the configuration of the heat absorber.

  As shown in FIG. 3, the heat exchanger 18 of the present embodiment includes an outer cylindrical member 41 (the heat radiating portion 2 in FIG. 2), an annular corrugated fin 421 fitted into the outer cylindrical member 41, and an annular corrugated And an inner cylindrical member 422 fitted into the fin 421.

  The annular corrugated fin 421 has the same configuration as the conventional annular corrugated fin 421 shown in FIGS. More specifically, the annular corrugated fins 421 are made of a 0.2 mm Cu alloy thin plate that has been annular corrugated. Therefore, the groove 421a formed by the annular corrugated fin 421 extends in parallel with the axial direction of the piston of the Stirling refrigerator. The annular corrugated fin 421 is formed in a cylindrical shape and is provided along the inner peripheral surface of the outer cylindrical member 41. The inner cylindrical member 422 is a cylinder made of a material having good thermal conductivity, and is provided inside the annular corrugated fin 421.

  As shown in FIG. 4, the corrugated fin 421 and the inner cylindrical member 422 are in contact with each other so as to be coaxial with each other. Here, the diameter of the circle formed by smoothly connecting the bottom portions 421b of the annular corrugated fins 421 (the inner diameter of the annular corrugated fins 421) is slightly smaller than the outer diameter of the inner cylindrical member 422.

  Therefore, when the inner cylindrical member 422 is pushed into the annular corrugated fin 421, the annular corrugated fin 421 is strongly pressed against the outer cylindrical member 41, and the annular corrugated fin 421 and the outer cylindrical member 41 have good heat transfer. It is crimped to become. In the present embodiment, the annular corrugated fin 421 and the outer cylindrical member 41 are pressure-bonded, but brazing or soldering may be used instead.

  Moreover, in this Embodiment, the flow resistance reduction process is given to the axial direction end surface of the cyclic | annular corrugated fin 421 as shown in either of FIGS. That is, the burr 500 described with reference to FIG. 13 in the prior art is removed, and the corner portion of the end face in the axial direction of the annular corrugated fin 421 is removed, that is, chamfered. The cross-sectional shape of the axial end face includes an isosceles triangle as shown in FIG. 5, a trapezoid as shown in FIG. 6, a right triangle as shown in FIG. 7, a semicircular arc shape as shown in FIG. A quarter arc shape as shown in FIG.

  In the processing method of the axial end face, after the plate material 420 having a constant width shown in FIG. 10 is formed, the plate material 420 is slid in the length direction, and the burrs 500 at the side end portions of the plate material 420 are scraped off with a blade. Cutting is used. Further, if the contact angle between the blade and the plate material 420 is changed when the burr 500 of the plate material 420 is scraped off, the side end portion of the plate material 420 can be processed into an arc shape (R shape). Thereafter, as shown in FIG. 11, linear corrugated fins 420a in which V-shaped cross-sectional shapes are continuously connected are formed. The linear corrugated fin 420a is rounded as indicated by an arrow to form the annular corrugated fin 421 shown in FIG.

  The heat exchanger 42 for the Stirling engine according to the above-described embodiment includes an annular corrugated fin 421 in which linear corrugated fins 420a having continuous V-shaped cross-sectional shapes are continuously connected, and an annular corrugated fin 421. An outer cylindrical member 41 having an inner diameter substantially equal to the outer diameter and having an annular corrugated fin 421 inserted along the axial direction, and an outer cylindrical member having an outer diameter slightly larger than the inner diameter of the annular corrugated fin 421 And an inner cylindrical member 422 inserted along the axial direction into an annular corrugated fin 421 inserted into the terminal 41. Moreover, the flow resistance reduction process as shown to FIGS. 5-9 is given to the fin material edge part which comprises the axial direction end surface of the annular corrugated fin 421. FIG. According to this configuration, since the flow resistance of the working gas is reduced, the heat exchange performance of the heat exchanger 42 for the Stirling engine is improved.

  In addition, since the flow resistance reduction processing is performed on the plate material 420 before forming the linear corrugated fins 420a, the operation of performing the flow resistance reduction processing is easy, and the manufacturing cost can be reduced.

  Moreover, since the flow resistance reduction process is a chamfering process including deburring as shown in FIGS. 5 to 9, the flow resistance reduction process is easy and the manufacturing cost can be reduced.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a figure which shows schematic structure of the refrigerator where the Stirling refrigerator of embodiment was used. It is a section schematic diagram of a free piston type Stirling refrigerator of an embodiment. It is an external appearance perspective view of the heat exchanger of an embodiment. It is a disassembled perspective view of the components of the heat exchanger of embodiment. It is a 1st figure which shows the shape of the cross section of the cyclic | annular corrugated fin of embodiment. It is a 2nd figure which shows the shape of the cross section of the annular corrugated fin of embodiment. It is a 3rd figure which shows the shape of the cross section of the cyclic | annular corrugated fin of embodiment. It is a 4th figure which shows the shape of the cross section of the annular corrugated fin of embodiment. It is a 5th figure which shows the cross-sectional shape of the annular corrugated fin of embodiment. It is a figure for demonstrating the board | plate material before forming a linear corrugated fin. It is a figure for demonstrating a linear corrugated fin. It is an external appearance perspective view of the conventional heat exchanger. It is a principal part enlarged view which shows an example of the conventional heat exchanger. It is a figure which shows the state by which the burr | flash was formed in the end surface of the conventional annular corrugated fin.

Explanation of symbols

  41 outer cylindrical member (heat radiating part or heat absorbing part), 18, 19 heat exchanger, 420 plate material, 420a linear corrugated fin, 421 annular corrugated fin, 421a groove, 422 inner cylindrical member.

Claims (4)

An annular corrugated fin in which linear corrugated fins having continuous V-shaped cross-sections are rounded into a cylindrical shape;
An outer cylindrical member having an inner diameter substantially equal to the outer diameter of the annular corrugated fin and having the annular corrugated fin inserted along the axial direction, and a heat exchanger for a Stirling engine,
The heat exchanger by which flow resistance reduction processing was given to the fin material end which constitutes the axial direction end face of the annular corrugated fin.   The heat exchanger according to claim 1, wherein the flow resistance reduction processing is performed on a plate-like fin material before forming the linear corrugated fin.   The heat exchanger according to claim 1, wherein the flow resistance reduction process is a chamfering process including a deburring process. A cylinder assembled in a casing enclosing the working medium;
A piston that reciprocates within the cylinder;
A displacer that reciprocates in the cylinder with a phase difference with respect to the piston;
A compression space formed between the piston and the displacer;
An expansion space provided on the opposite side to the compression space of the displacer;
A Stirling engine comprising: the heat exchanger according to claim 1 provided in a communication path communicating the compression space and the expansion space.

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