JP2009236456A - Pulse tube-type heat storage engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pulse tube type heat storage engine which is highly efficient, small in size and convenient in any case operating as an engine or a refrigerator.
A power unit including a power cylinder, a power piston, and a drive unit, a first pulse tube, a first heat exchanger, a regenerative heat exchange. The heat exchanging operation unit 40 that sequentially communicates with the heat exchanger 44 and the second heat exchanger 45, the first operating unit 61 configured on the front side of the displacer piston 63, and the second configured on the back side of the displacer piston 63. A displacer unit 60 having an operating unit 66, the power operating unit 21 and the first moving unit 61 are connected to the first pulse tube 42, and the second operating unit 66 is connected to the second heat exchanger 45. The temperature of the first heat exchanger 43 is higher than the temperature of the second heat exchanger 45.
[Selection] Figure 1

Description

  The present invention relates to a pulse tube type heat storage engine provided with a heat accumulator or a cool accumulator (generally both are regenerative heat exchangers) and a pulse tube.

  As a pulse tube type heat storage engine of the prior art, a vibration generator, a regenerator, a cold head, and a pulse tube are sequentially connected in series, and there is a phase difference between the reciprocation and pressure fluctuation of the working fluid flowing into them. In a pulse tube type heat storage engine that generates low temperature or power by generating a displacer system, there is a displacer system that connects the connection between the vibration generator and the regenerator and the high temperature end of the pulse tube. The system constitutes a displacer working space into which the working fluid flows in and out, a displacer working space that constitutes at least a part of the displacer working space, and is disposed so as to be capable of reciprocating with respect to the displacer working space. A buffer space isolated from the displacer working space in the direction in which the part reciprocates, and a displacer As well as extending in a direction reciprocation of placer unit, one end attached to the displacer part, the displacer bar at least partially disposed in the buffer space, the pulse tube heat storage engine having disclosed.

  When the above pulse tube type heat storage engine is used as an engine, the cold head of the cold head portion is heated with, for example, combustion gas, and the working gas is compressed in the displacer working space on the front side of the displacer. The compressed working gas expands in the working space obtained by adding the compression space of the compressing portion and the displacer working space on the rear side of the displacer to reciprocate the piston. By reciprocating the piston, a linear motor (in the case of a refrigerator) is used as a generator to obtain electric power.

  On the other hand, when used as a refrigerator, the piston of the compression unit is reciprocated by a linear motor to compress the working gas in the compression space and the displacer working space on the front side of the displacer, and the compressed working gas is placed on the front side of the displacer. The piston expands in the displacer working space and reciprocates to generate refrigeration (see, for example, Patent Document 1).

Generally, when a pulse tube type heat storage engine is used as a refrigerator, the efficiency increases when the scavenging volume on the high temperature side of the regenerator is larger than the scavenging volume on the low temperature side of the regenerator, and decreases when the scavenging volume is small. Also when used as an engine, the efficiency increases when the scavenging volume on the high temperature side of the regenerator is larger than the scavenging volume on the low temperature side of the regenerator, and decreases when it is small.
JP 2006-275352 A

  However, according to Patent Document 1, when a pulse tube type heat storage engine is used as a refrigerator, an object to be cooled is cooled by a cold head, and a heat exchanger (hereinafter referred to as a first heat exchanger) on the compression space side is used. Dissipates compression heat. Therefore, the cold head side end of the regenerator is the low temperature end, and the end of the regenerator on the first heat exchanger side is the high temperature end. The scavenging volume on the high temperature side of the regenerator (compressed volume V2 of the compression space and the volume V2 of the displacer operating space on the back side of the displacer, taking into account the phase) Vsum2 is the scavenging volume on the low temperature side of the regenerator ( Efficiency is high because it is larger than the expansion volume V1 of the displacer operating space on the front side of the displacer.

  However, when used as an engine, when the first heat exchanger is heated, the temperature of the working space on the vibration oscillator side and the small-diameter displacer working space becomes high due to conduction heat from the first heat exchanger, and the piston reciprocates. It becomes impossible to move. For this reason, the above-mentioned cold head is heated at high temperature, and the compression heat is radiated by the first heat exchanger. Therefore, the end on the cold head side of the regenerator is the high temperature end, and the end on the first heat exchanger side of the regenerator is the low temperature end. The scavenging volume V1 on the high temperature side of the regenerator is the scavenging volume on the low temperature side of the regenerator (compressed volume obtained by adding the volume V of the compression space and the volume V2 of the displacer operating space on the back side of the displacer in consideration of the phase) Vsum2. Since it is smaller, there is a problem that the efficiency of the pulse tube type heat storage engine is lowered.

  In addition, since the above efficiency is lowered, in order to obtain a required expansion work, the expansion volume and the compression volume must be increased, and there is a problem that the pulse tube heat storage engine becomes large.

  The present invention has been made in view of the above problems, and provides a pulse tube type heat storage engine that is highly efficient, small in size and convenient in any case operating as an engine or a refrigerator. Objective.

In order to solve the above-mentioned problem, the invention described in claim 1 is a pulse tube type heat storage engine that generates power or refrigeration by giving a phase difference between reciprocation of working gas and pressure fluctuation,
A power unit comprising a power cylinder and a power piston housed on the inner peripheral surface of the power cylinder so as to be capable of reciprocating; and a drive unit to which the power piston is coupled; and the working gas absorbs heat. Alternatively, the first heat exchanger that radiates heat, the second heat exchanger that radiates and absorbs the working gas, and one end of the first heat exchanger and one end of the second heat exchanger that are in communication with the working gas, heat absorption, and exhaust heat. A regenerative heat exchanger that repeats alternately, and a first pulse tube that is provided on at least the first heat exchanger side of the first heat exchanger and the second heat exchanger and communicates with the other end of the first heat exchanger. A displacer cylinder, a displacer cylinder, and a displacer cylinder, and a displacer piston back surface. And a displacer portion having a rod connected to the back surface and a second operating portion formed in the displacer cylinder and formed by a partition wall through which the rod passes, the power operating portion being one end of the heat exchange operating portion. Is connected to the end of the first pulse tube, and the second working part is connected to the other end of the heat exchange working part, and the second working part is connected to the other end of the heat exchange working part. When the operating unit communicates with the end of the first pulse tube, the first operating unit is connected to the other end of the heat exchange operating unit, and the temperature of the first heat exchanger is higher than that of the second heat exchanger.

  In the invention according to claim 2, a second pulse tube is arranged at the other end of the second heat exchanger.

  According to a third aspect of the present invention, when the pulse tube type heat storage engine operates as an engine, the working gas is heated via the first heat exchanger, and the compression heat of the working gas is radiated by the second heat exchanger. In the case where the expansion work in which the working gas is expanded in the power working unit is taken out from the driving unit and operated as a refrigerator, the working gas is compressed in the power working unit by the driving unit, and the compression heat of the working gas in the first heat exchanger The compressed working gas expands in the displacer section and generates refrigeration.

Further, in the invention according to claim 4, the drive unit is provided with linear drive means provided with a mover connected to the power piston, and the mover supports the power piston so as to be able to reciprocate with a support spring,
When the pulse tube heat storage engine operates as an engine, the linear drive means operates as a generator,
When the pulse tube heat storage engine operates as a refrigerator, the linear drive means operates as a motor.

  In the invention according to claim 5, the displacer piston is supported by the support spring so as to be reciprocally movable.

  Moreover, the invention described in claim 6 is characterized in that the pulse tube type heat storage engine includes a plurality of heat exchange operation parts.

  According to the first aspect of the present invention, when the first operating part communicates with the end of the first pulse tube that is one end of the heat exchange operating part, the second operating part is connected to the other end of the heat exchange operating part. In the case of (Case 1) and when the second operating part communicates with the end of the first pulse tube that is one end of the heat exchange operating part, the first operating part is connected to the other end of the heat exchange operating part. (Case 2).

  The scavenging volume V1 of the first working chamber of the first working part is larger than the volume of the rod occupied by the rod than the scavenging volume V2 of the second working chamber of the second working part. By making the scavenging volume V of the power operating chamber of the power operating unit sufficiently larger than the volume occupied by the rod, the combined operation is performed by adding the scavenging volume V of the power operating chamber and the scavenging volume V1 of the first operating chamber in consideration of the phase. The combined volume Vsum2 of the part is larger than the scavenging volume V1 of the second working chamber. Further, the combined volume Vsum2 of the combined working unit, which is the sum of the scavenging volume V of the power working chamber and the scavenging volume V2 of the second working chamber, is larger than the scavenging volume V1 of the second working chamber.

  When operating a pulse tube type heat storage engine as an engine, the first heat exchanger is heated to a high temperature (for example, approximately 500 ° C.) with combustion gas or the like, and the compression heat of the working gas compressed by the second heat exchanger is increased. The heat is radiated at a lower temperature (for example, approximately 60 ° C.) than the first heat exchanger. Thereby, the temperature of the 1st heat exchanger is higher than the temperature of the 2nd heat exchanger. Therefore, the end of the regenerative heat exchanger on the first heat exchanger side is a high temperature end, and the end of the regenerative heat exchanger on the second heat exchanger side is a low temperature end. The temperature of the first heat exchanger is higher than the temperature of the second heat exchanger. And, as will be described later, by arranging the first pulse tube on the first heat exchanger side, the first pulse tube acts as a heat insulating material and suppresses the power part and the displacer part from becoming high temperature. The first heat exchanger can be heated with combustion gas and can operate as an engine.

  On the other hand, when the pulse tube type heat storage engine is operated as a refrigerator, the compression heat of the compressed working gas having a high temperature (for example, approximately 60 ° C.) is radiated at, for example, approximately 60 ° C. by the first heat exchanger. And a to-be-cooled body is cooled at the temperature (for example, about -20 degreeC) lower than the temperature of a 1st heat exchanger by interposing a 2nd heat exchanger with the refrigeration which generate | occur | produced by expansion | swelling of working gas. Thereby, the temperature of the 1st heat exchanger is higher than the temperature of the 2nd heat exchanger. Therefore, for the same purpose as the engine, the end of the regenerative heat exchanger on the first heat exchanger side is the high temperature end, and the end of the regenerative heat exchanger on the second heat exchanger side is the low temperature end.

  That is, regardless of whether it operates as an engine or a refrigerator, the end on the first heat exchanger side of the regenerative heat exchanger becomes a high temperature end, and the end on the second heat exchanger side of the regenerative heat exchanger Becomes the cold end.

  As described above, regardless of whether the engine or the refrigerator is operated, the scavenging volume Vsum1 of the combined working space located on the high temperature end side of the regenerative heat exchanger is located on the low temperature end side of the regenerative heat exchanger. 2 It is larger than the scavenging volume V2 of the operating part (case 1). Further, the scavenging volume Vsum2 of the combined working space located on the high temperature end side of the regenerative heat exchanger is larger than the scavenging volume V1 of the first working part located on the low temperature end side of the regenerative heat exchanger (case 2). As a result, the pulse tube type heat storage engine has high efficiency.

  In the prior art, the power operation unit and the second operation unit communicate with the first pulse tube of the heat exchange operation unit, and the first operation unit communicates with the second heat exchanger of the heat exchange operation unit. This corresponds to (Case 2). When operating as a refrigerator, the object to be cooled is cooled by the second heat exchanger, but when operating as an engine, the second heat exchanger is heated.

  When operating as a refrigerator, the first heat exchanger releases heat of compression of the working gas, and the second heat exchanger cools the object to be cooled. The combined working space of the scavenging volume Vsum2, which is the sum of the power working chamber of the scavenging volume V of the power working unit and the second working chamber of the scavenging volume V2 of the second working unit, is located on the high temperature end side of the regenerative heat exchanger. The first working chamber performs expansion work and generates refrigeration. In this case, the high temperature end of the regenerative heat exchanger is located at the end on the first heat exchanger side, and the low temperature end is located at the end on the second heat exchanger side. Therefore, the scavenging volume Vsum2 of the combined working space located on the high temperature end side of the regenerative heat exchange is larger than the scavenging volume V1 of the first working part located on the low temperature end side of the regenerative heat exchanger, so that the conventional pulse The tubular heat accumulator is efficient when operated as a refrigerator.

  When operating as an engine, the second heat exchanger is heated to high temperatures with combustion gases. The combined working space of the scavenging volume Vsum2 obtained by adding the power working chamber of the scavenging volume V of the power working unit and the second working chamber of the scavenging volume V2 of the second working unit is located on the low temperature end side of the regenerative heat exchanger. , Do the expansion work. On the other hand, the first working chamber of the scavenging volume V1 of the first working part to which compression work is applied is located on the high temperature end side of the regenerative heat exchanger. Therefore, since the scavenging volume Vsum2 of the combined working space located on the low temperature end side of the regenerative heat exchange is larger than the scavenging volume V1 of the first working part located on the high temperature end side of the regenerative heat exchanger, the conventional pulse tube type When the regenerator operates as an engine, the efficiency is low.

  However, as described above, the present invention relates to the combined scavenging of the combined operation unit located on the high temperature end side of the regenerative heat exchanger, regardless of whether the pulse tube type heat accumulator operates as an engine or a refrigerator. Since the volume is larger than the scavenging volume of the working chamber (the second working chamber in the case 1 and the first working chamber in the case 2) located on the low temperature end side of the regenerative heat exchanger, the pulse tube When the type heat storage engine operates as an engine, the efficiency is higher than that of the prior art. Further, when the pulse tube type heat storage engine operates as a refrigerator, the efficiency is high as in the prior art.

  Further, when the same electric power or power as in the prior art is obtained due to the increased efficiency, the pulse tube type heat storage engine is smaller than the prior art.

  Further, as described above, since the pulse tube type heat storage engine can be used as a refrigerator even if the engine is used, a highly convenient pulse tube type heat storage engine can be provided.

  Moreover, the 1st pulse tube is arrange | positioned between the union operation part and the 1st heat exchanger. A first gas piston made of working gas is formed in the first pulse tube. Further, a first gas piston working chamber is formed in which the working gas expands and compresses by the first pulse tube, the first gas piston, and the first heat exchanger.

The first gas piston functions as a heat insulator that reciprocates in the first pulse tube,
The heat of the working gas at a high temperature (for example, approximately 500 ° C.) in the first gas piston working chamber is prevented from entering the power section and the displacer section. Thereby, the temperature rise of the power cylinder, power piston, and each member of the drive unit of the power unit is suppressed, and the clearance seal and each member (permanent magnet, support spring) of the drive unit function appropriately. Similarly, the temperature rise of the displacer cylinder, the displacer piston, the rod, the partition wall, and the support spring of the displacer unit is suppressed, and the clearance seal and the support spring function properly. As a result, the durability and reliability of the pulse tube heat storage engine 1 are improved.

  In addition, by suppressing the temperature rise of the power unit and the displacer unit, the loss associated with the temperature rise, for example, the electrical loss of the drive unit (heating of the coil, reduction of the holding power of the permanent magnet) is reduced. The efficiency of the heat storage engine is improved.

  As described above, in any case of operating as an engine or a refrigerator, it is possible to provide a pulse tube type heat storage engine that is highly efficient, compact, and convenient.

  In the invention according to claim 2, the second pulse tube is arranged at the end of the second heat exchanger.

Regardless of whether the second pulse tube is provided or the engine or the refrigerator operates, the end of the regenerative heat exchanger on the first heat exchanger side is the high temperature end, and the second heat exchanger of the regenerative heat exchanger The end on the side becomes the low temperature end. Therefore, as in the first aspect, even when the pulse tube type heat storage engine is operated on the engine or the refrigerator, it is possible to provide a pulse tube type heat storage engine that is highly efficient, small in size, and convenient.

  Further, by disposing the second pulse tube between the second heat exchanger and the displacer unit, when the pulse tube type heat storage engine operates as a refrigerator, the displacer unit on the high temperature side (for example, approximately 40 ° C.) Therefore, conduction heat entering the low temperature side of the second pulse tube at a low temperature (for example, approximately −60 ° C.) can be suppressed. That is, a gas piston (hereinafter referred to as a second gas piston) formed in the second pulse tube serves as a heat insulating material and suppresses conduction heat. As a result, the amount of refrigeration generated in the second gas piston working chamber formed by the second pulse tube, the second gas piston, and the second heat exchanger is increased, and the efficiency of the pulse tube heat storage engine is improved.

  In the invention according to claim 3, the first heat exchanger is heated to a high temperature (for example, approximately 500 ° C.) with, for example, a combustion gas, and the thermal energy of the combustion gas is converted into helium that reciprocates through the first heat exchanger. In addition, the power working unit performs expansion work, and the heat of the helium is radiated (exhaust heat) by the second heat exchanger. The expansion work in the power operating unit is transmitted to the power piston, and is transmitted to the driving unit via the rod. The drive unit supplies the transmitted expansion work to the outside as power or electric power. Further, the expansion work expanded by the first operating part of the displacer part is spent on the compression work of the second operating part. result. A pulse tube type heat storage engine can operate with high efficiency as an engine.

  On the other hand, the power piston is reciprocated in the drive unit, and the power operating unit and the first operating unit are integrated to compress helium, and the compressed helium is expanded by the second operating unit via the heat exchange operating unit. Work and generate refrigeration. With this refrigeration, the object to be cooled is efficiently cooled through the second heat exchanger. As a result, the pulse tube heat storage engine can operate as a refrigerator with high efficiency.

  As described above, the pulse tube heat storage engine can be used with high efficiency both as an engine and as a refrigerator, so that a convenient pulse tube heat storage engine can be provided.

  The above explanation is for the case (case 1) described above, but the case (case 2) also produces the same effect for the same reason.

  According to a fourth aspect of the present invention, the power piston has linear drive means supported by a support spring so as to be reciprocally movable. Therefore, the power piston is supported by the support spring with a minute gap between the power piston and the cylinder. As a result, the working gas is sealed, and the power piston can reciprocate without contacting the power cylinder. As a result, mechanical loss due to sliding friction is reduced, so that a highly efficient pulse tube type heat storage engine can be provided.

  Further, mechanical parts such as piston rings or bearings associated with sliding friction are not required, and the durability of the pulse tube type heat storage engine is improved.

  In the invention according to claim 5, the displacer piston is supported by the support spring so as to be reciprocally movable. Accordingly, the displacer piston is supported with a minute gap between the displacer piston and the displacer cylinder and between the rod and the partition wall. Thereby, helium is sealed, and the displacer piston and the rod can reciprocate without contacting the displacer cylinder and the partition wall, respectively. As a result, mechanical loss due to sliding friction is reduced, so that a highly efficient pulse tube type heat storage engine can be provided.

  Further, mechanical parts such as piston rings or bearings accompanying sliding friction are not required, and the durability of the pulse tube heat storage engine is improved.

  In the invention according to claim 6, the pulse tube type heat storage engine includes a plurality of heat exchange operation parts. Therefore, when using as an engine, the 1st heat exchange part of each heat exchange operation part is heated at different temperature. For example, the first heat exchange of the first is heated with the combustion gas, and the first heat exchange part of the next heat exchange operation part is heated without exhausting the exhausted combustion gas wastefully. Similarly, the first heat exchange unit is sequentially heated without exhausting the combustion gas. Thereby, the heat of combustion gas can be used effectively and the efficiency of a pulse tube type heat storage engine improves.

  Moreover, when using as a refrigerator, the to-be-cooled body is cooled at different temperatures in the second heat exchange section of each heat exchange operation section. For example, the blown air for cooling is cooled by the first second heat exchange, and the cooled blown air is cooled to a lower temperature by the second heat exchange part of the next heat exchange operation part. Similarly, the blown air is sequentially cooled by the second heat exchange unit. Thereby, the quantity of heat by which the blown air is cooled increases, and the efficiency of the pulse tube heat storage engine is improved.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The pulse tube type heat storage engine of the present invention can be used as a refrigerator or an engine. The regenerative heat exchanger is referred to as a regenerator in the case of a refrigerator, and is referred to as a regenerator in an engine. Hereinafter, the regenerator and the regenerator are collectively referred to as a regenerative heat exchanger.

(First embodiment)
FIG. 1 is an explanatory diagram according to the first embodiment of the present invention. In the figure, (A) shows the case where the first working chamber communicates with the first pulse tube, and the second working chamber communicates with the second heat exchanger, and (B) shows the second working chamber, The case where it communicates with one pulse tube and the first working chamber communicates with the second heat exchanger is shown. Since the operation and effect of FIG. 1B are substantially the same as those of FIG. 1A, the following description will be made mainly with reference to FIG.

  As shown in FIG. 1A, the pulse tube heat storage engine 1 includes a power unit 20 that compresses and expands helium (working gas), a displacer unit 60 that expands and compresses helium, and the power unit 20 and the displacer unit. The heat exchange operating unit 40 exchanges heat with helium compressed and expanded by 60 and flowing in and out.

  The power unit 20 includes a power operation unit 21 and a drive unit 25. The power actuating portion 21 includes a small diameter portion of a power cylinder 22 having a small diameter portion and a large diameter portion, and a power piston 23 that reciprocates on the inner peripheral surface of the small diameter portion of the power cylinder 22, and helium repeatedly compresses and expands. It has a power working chamber 21a.

  The drive unit 25 includes a linear drive unit 25 a (linear drive means) that is provided at the large diameter portion of the power cylinder 22 and is connected to the power piston 23, and a balancer 30 that suppresses vibration of the power unit 20.

  The linear drive unit 25 a is provided in the buffer unit 29 on the back side of the power piston 23, and has a stator 27 fixed to the large diameter portion of the power cylinder 22 and a mover having a permanent magnet that reciprocates relative to the stator 27. 26. The stator 27 has a coil around which a copper wire is wound. The mover 26 includes a rod 24, and has a pair of support springs 28 whose outer peripheral side is fixed to the large diameter portion of the power cylinder 22 and whose inner peripheral side is fixed to the rod 24.

  The rod 24 is connected to the center of the back surface of the power piston 23, and the power piston 23 is supported by a pair of support springs 28 with a small gap with respect to the inner peripheral surface of the power cylinder 22. The minute gap allows the warp piston 23 to reciprocate with respect to the inner peripheral surface of the power cylinder 22 and functions as a clearance seal that seals the helium in the power working chamber 21 a and the buffer unit 29.

  The linear drive unit 25a functions as a generator when the pulse tube heat storage engine 1 operates as an engine, and functions as a motor when the pulse tube heat storage engine 1 operates as a refrigerator.

  The balancer 30 includes a mass 31, a rod 32 fixed to the mass 31, a pair of support springs 33 whose outer peripheral side is fixed to the large diameter portion of the power cylinder 22, and whose inner peripheral side is fixed to the rod 32. The balancer 30 suppresses vibrations that occur when the power piston 23 and the mover 26 are reciprocated together.

  The displacer portion 60 includes a displacer cylinder 62 having a small diameter portion and a large diameter portion, a partition wall 65 provided in the displacer cylinder 62, a displacer piston 63, a rod 64 connected to the center of the back surface of the displacer piston 63, and an inner peripheral side being a rod. And a pair of support springs 67 fixed to 64.

  The outer periphery of the support spring 67 is fixed to a displacer cylinder 62 on the buffer unit 68 side provided on the back side of the partition wall 65. The displacer piston 63 is supported by a pair of support springs 67 with a small gap with respect to the inner peripheral surface of the small diameter portion of the displacer cylinder 62. The minute gap allows the displacer piston 63 to reciprocate with respect to the inner peripheral surface of the displacer cylinder 62 and functions as a clearance seal that seals helium. Similarly, the rod 64 is supported with a minute gap with respect to the inner peripheral surface of the through hole provided in the partition wall 65. The minute gap can reciprocate with respect to the inner peripheral surface of the through hole and functions as a clearance seal for sealing helium.

  The first operating part 61 is composed of a displacer cylinder 62 and a displacer piston 63, and has a first operating chamber 61a. The second operating part 66 includes a displacer cylinder 62, a rear surface of the displacer piston 63, a partition wall 65, and a rod 64, and has a second operating chamber 66a.

  In addition, the first working chamber 61 a of the first working unit 61 and the power working chamber 21 a of the power working unit 21 are communicated with each other by a pipe 81, and the power working unit 21 of the power unit 20 and the first of the displacer unit 60 are connected. Together with the operating unit 61, the combined operating unit 35 that repeats expansion and compression of helium.

  The power operating unit 21 and the first operating unit 61 are integrated to form the combined gas operating unit 35, the power operating chamber 21 a of the power operating unit 21, the first operating chamber 61 a of the first operating unit 61, and Are combined to form a combined working chamber.

  When the pulse tube heat storage engine 1 operates as an engine, the combined gas operating unit 35, that is, the power operating unit 21 and the first operating unit 61 function as an expansion unit, and when operating as a refrigerator, as a compression unit Function.

  In the heat exchange operation unit 40, one end of the distributor 41 is sequentially connected to the first pulse tube 42 (pulse tube), the first heat exchanger 43, the regenerative heat exchanger 44, and the second heat exchanger 45. It is configured to communicate with one end.

  The other end of the distributor 41 communicates with the piping 82, the power operating chamber 21 a of the power operating portion 21 through the piping 81, and the first operating chamber 61 a of the first operating portion 61.

  One end of the second heat exchanger 45 communicates with the second working chamber 66a of the second working part 66 through the pipe 83. In the case of an engine, the second heat exchanger 45 functions as a radiator that radiates the compression heat of helium, and in the case of a refrigerator, the second heat exchanger 45 functions as a heat absorber that cools an object to be cooled.

  The first pulse tube 42 is formed with a first gas piston 48 (a dashed line in the drawing) that reciprocates. A first gas piston working chamber 48 a is formed by being surrounded by the first pulse tube 42, the first gas piston 48, and the first heat exchanger 43. The first pulse tube 42 is made of a thin tube having a low thermal conductivity, a thin wall, and a long axial direction.

  The first gas piston 48 is formed of helium having the same cylindrical shape as the inner periphery of the first pulse tube 42, has a constant mass, and changes in volume as the pressure of helium changes. That is, the first gas piston 48 is in the form of an elastic piston whose volume changes with the pressure fluctuation of helium. And the 1st gas piston 48 reciprocates between the edge part 42a and the edge part 42b of the 1st pulse tube 42, changing each volume. The first gas piston working chamber 48a functions as an expansion chamber in the case of an engine and as a compression chamber in the case of a refrigerator.

  The first heat exchanger 43 functions as a heat absorber that absorbs high-temperature thermal energy such as combustion gas in the case of an engine, and functions as a radiator that radiates the heat of compression of helium in the case of a refrigerator.

  In addition, the regenerative heat exchanger 44 is configured by laminating a plurality of wire mesh elements made of a material such as stainless steel having a large heat capacity in a thin stainless steel container having a low thermal conductivity. In the case of an engine, as a heat accumulator, In the case of a refrigerator, it functions as a regenerator. When operating as an engine, the end portion 44a is a high temperature end, the end portion 44b is a low temperature end, and the temperature of the heat storage / cool storage material element gradually increases from the end portion 44b to the end portion 44a. When operating as a refrigerator, the end 44a is a high temperature end, the end 44b is a low temperature end, and the temperature of the element gradually decreases from the end 44a to the end 44b.

  The power piston 23 forms a vibration system having a natural frequency determined from the total mass of the power piston 23 and the movable element 26 including the rod 24 and the spring constant of the pair of support springs 28. Similarly, the displacer piston 63 forms a vibration system having a natural frequency determined by the displacer piston 63, the total mass of the rods 64, and the spring constant of the pair of support springs 67. The natural frequency of the power piston 23 and the natural frequency of the displacer piston 63 are substantially matched, and the pulse tube heat storage engine 1 is operated in the vicinity of this natural frequency.

  Next, the operation and effect of the first embodiment of the present invention shown in FIG.

  A case where the pulse tube heat storage engine 1 operates as an engine will be described. In this case, the power operation unit 21 is an expansion unit, the power operation chamber 21a is an expansion chamber, the first gas piston operation chamber 48a is an expansion chamber, the first heat exchanger 43 is a heat absorber, the regenerative heat exchanger 44 is a heat accumulator, and The second heat exchanger 45 is a radiator, the first working part 61 of the displacer part 60 is an expanding part, the first working chamber 61a is an expanding part, and the second working part 66 of the displacer part 60 is a compressing part, a second working room. 66a functions as a compression chamber.

  The first heat exchanger 43 is heated to a high temperature (for example, approximately 500 ° C.) with, for example, a combustion gas, the thermal energy of the combustion gas is added to helium reciprocatingly flowing through the first heat exchanger 43, The power operating unit 21 and the first operating unit 61 make expansion work, and the heat of the helium is radiated (exhaust heat) by the second heat exchanger 45. The expansion work expanded in the power working chamber 21a is transmitted to the power piston 23 and transmitted to the linear drive unit 25a via the rod. The linear drive unit 25a operates as a generator, converts the expanded work transmitted to electric energy, and supplies the electric power to the outside. The expansion work expanded in the first working chamber 61a is spent on the compression work in the first working part 61 of the displacer part 60. At this time, the generated compression heat is radiated by the second heat exchanger 45 as described above. Is done.

  More specifically, helium reciprocatingly flowing through the first heat exchanger 43 is heated by the combustion gas, and is heated to about 500 ° C., for example. The heated helium gas reciprocates the first gas piston 48, and the movement of the first gas piston 48 is transmitted to the power piston 23 and the displacer piston 63. That is, in the power piston 23, the phase of the combined volume fluctuation obtained by adding the volume fluctuation of the power working chamber 21a and the volume fluctuation of the first working chamber 61 and the volume fluctuation of the first gas piston working chamber 48a are substantially the same phase. Reciprocate so that

  The displacer piston 63 reciprocates so that the volume variation of the first gas piston working chamber 48a advances in phase by approximately 90 ° with respect to the volume variation of the second working chamber 66a.

  When the displacer piston 63 moves in the direction of the partition wall 65, the helium in the second working chamber 66a is compressed and flows into the second heat exchanger 45, where the compression heat is transferred to the temperature of the first heat exchanger (for example, approximately 500 ° C.). ) Radiates heat at a lower temperature (for example, approximately 60 ° C.) and flows into the regenerative heat exchanger 44.

  The helium that has flowed into the regenerative heat exchanger 44 is heated by the heat storage material element, gradually heated in the flow direction, and flows into the first heat exchanger 43.

  The helium that has flowed into the first heat exchanger 43 is heated by the combustion gas at about 500 ° C., absorbs the heat energy, becomes about 500 ° C., and flows into the first gas piston working chamber 48a.

  The helium flowing into the first gas piston working chamber 48a moves the first gas piston 48 in the direction toward the end 42a of the first pulse tube 42 (bottom dead center direction), and the first gas piston 48 performs expansion work. Eggplant. This expansion work is transmitted to the power operating unit 21 and the first operating unit via the first gas piston 48.

  Next, when the first gas piston 48 moves in the direction toward the end 42b of the first pulse tube 42 (top dead center direction), the helium in the first gas piston working chamber 48a passes through the first heat exchanger 43. It flows into the regenerative heat exchanger 44, where it is cooled by the heat storage element, gradually cooled along the flow direction, passes through the second heat exchanger 45, and flows into the second working chamber 66a to complete one cycle. To do. In one cycle as an engine, the temperature of the first heat exchanger 43 (for example, approximately 500 ° C.) is higher than the temperature of the second heat exchanger 45 (for example, approximately 60 ° C.).

  The regenerative heat exchanger 44 gradually cools the helium flowing out from the first heat exchanger 43 and flowing into the second heat exchanger 45 with a heat storage material element filled in the regenerative heat exchanger 44. Further, in the flow in the direction opposite to that described above, helium flowing out from the second heat exchanger 45 and flowing into the first heat exchanger 43 is gradually heated by the heat storage material element. Thereby, the end 44a of the regenerative heat exchanger 44 becomes the high temperature end, and the end 44b becomes the low temperature end.

  In addition, as will be described later, by providing the first pulse tube 42 on the first heat exchanger 43 side, the first pulse tube 42 acts as a heat insulating material, and the power unit 40 and the displacer unit 60 The high temperature is suppressed, the first heat exchanger 43 can be heated with the combustion gas, and the pulse tube type heat storage engine can be operated as an engine.

  Therefore, the variable volume width V (scavenging volume) of the power working chamber 21a and the variable volume width V1 (scavenging volume) of the first working chamber 61 are added in consideration of the phase. That is, the combined scavenging volume Vsum1 is located on the end portion 44a side of the regenerative heat exchanger 44, which is a high temperature end, and performs expansion work. On the other hand, the second working chamber 66a having a variable volume width V2 (scavenging volume) to which compression work is applied is on the end 44b side of the regenerative heat exchanger 44, which is the low temperature end. As a result, the efficiency of the pulse tube heat storage engine 1 is increased.

  The combined scavenging volume Vsum1 is the value of A in the equation Vsin (2πft) + V1sin (2πft + α) = Asin (ωt + β). Here, π is the circumference, f is the operating frequency of the pulse tube type heat storage engine, t is time, α is the phase difference of the variable volume of the first working chamber 61a with respect to the variable volume of the power working chamber 21a, and β is the power This is the phase difference of the variable volume Vsum1 of the combined working space with respect to the variable volume of the working chamber 21a.

  Further, an associated scavenging volume Vsum2 to be described later is a value of A in the equation Vsin (2πft) + V2sin (2πft + γ) = Asin (ωt + δ). Here, γ is the phase difference of the variable volume of the second working chamber 66a with respect to the variable volume of the power working chamber 21a, and δ is the phase difference of the variable volume Vsum of the combined working space with respect to the variable volume of the two power working chamber 21a.

  The prior art will be described with reference to FIG. That is, in the prior art, the power working chamber 21a (scavenging volume V) and the second working chamber 66a (scavenging volume V2) are communicated with each other by pipes to form a combined working space (scavenging volume Vsum2). The end portion 42a of one pulse tube is communicated. The first working chamber (scavenging volume V1) communicates with the second heat exchanger 45. Then, the second heat exchanger 45 is heated with the combustion gas, the end 44b of the regenerative heat exchanger 44 becomes the high temperature end, and the end 44a becomes the low temperature end. The combined working space of the scavenging volume Vsum2 where expansion work is performed is located on the low temperature end side of the regenerative heat exchanger 44, and the first working chamber (scavenging volume V1) where compression work is applied is the high temperature of the regenerative heat exchanger 44. Located on the end side. As a result, the efficiency of the prior art pulse tube heat storage engine is low.

  However, as described above, according to the present invention, the combined scavenging volume Vsum1 of the combined operation unit 35 positioned on the high temperature end 44a side of the regenerative heat exchanger 44 is the second position positioned on the low temperature end 44b side of the regenerative heat exchanger 44. Since it is larger than the scavenging volume V2 of the working chamber 66a, when the pulse tube type heat storage engine 1 operates as an engine, the efficiency becomes higher than that of the prior art.

  Further, when the same electric power or power as in the conventional technology is obtained due to the increased efficiency, the pulse tube type heat storage engine 1 is smaller than the conventional technology.

  The same effect can be obtained even when described from the first gas piston working chamber 48 side. That is, the scavenging volume Vg of the first gas piston working chamber 48a is substantially the same as the combined scavenging volume Vsum1. Therefore, the scavenging volume Vg of the first gas piston working chamber 48a located on the high temperature end 44a side of the regenerative heat exchanger 44 is the scavenging volume V2 of the second working chamber 66a located on the low temperature end 44b side of the regenerative heat exchanger 44. Therefore, when the pulse tube type heat storage engine 1 is operated as an engine, the efficiency is higher than that of the conventional technique.

The first gas piston 48 functions as a heat insulator that reciprocates within the first pulse tube 42.
The heat of high-temperature (for example, approximately 500 ° C.) helium in the first gas piston working chamber 48 a is prevented from entering the power working unit 21 a and the displacer unit 60. Thereby, the temperature rise of the power cylinder 22 of the power part 20, the power piston 23, the support spring 28 of the linear drive part 25a, the permanent magnet (not shown), and the support spring 33 of the balancer 30 is suppressed, and the clearance seal and the permanent magnet The support spring 28 and the support spring 33 function properly. Similarly, the temperature rise of the displacer cylinder 62, the displacer piston 63, the rod 64, the partition wall 65, and the support spring 67 of the displacer unit 60 is suppressed, and the clearance seal and the support spring 67 function appropriately. As a result, the durability and reliability of the pulse tube heat storage engine 1 are improved.

  In addition, since the electric resistance of the coil (not shown) of the stator 27 and the holding force of the permanent magnet of the mover 26 are properly maintained and the efficiency of the linear drive unit 25a is improved, the efficiency of the pulse tube heat storage engine 1 is improved. improves.

  Next, the case where the pulse tube heat storage engine 1 operates as a refrigerator will be described. In this case, the power operation unit 21 is the compression unit, the operation chamber 21a is the compression chamber, the first gas piston operation chamber 48a is the compression chamber, the first heat exchanger 43 is the radiator, the regenerative heat exchanger 44 is the regenerator, the second The heat exchanger 45 is a heat absorber, the first working part 61 of the displacer part 60 is a compression part, the first working chamber 61a is a compression chamber, the second working part 66 of the displacer part 60 is an expanding part, and the second working chamber 66a is expanded. Functions as a chamber.

  The linear drive unit 25a functions as a motor. When a current having substantially the same vibration frequency as the natural frequency of the power piston 23 is supplied to the linear drive unit 25a, the power piston 23 reciprocates due to the magnetic force generated by the linear drive unit 25a. . When the power piston 23 reciprocates, the first gas piston 48 reciprocates due to helium flowing in and out of the power working chamber 21a. By this reciprocation, the displacer piston 63 reciprocates such that the phase of the volume variation of the first gas piston working chamber 48a is delayed by approximately 90 ° with respect to the volume variation of the second working chamber 66a. The volume variation of the first gas piston working chamber 48a is substantially the same as the variation volume of the combined working portion 35 in which the varying volume of the power working chamber 21a and the varying volume of the first working chamber 61a are added. Then, the helium compressed in the first gas piston working chamber 48a and heated (for example, approximately 60 ° C.) releases heat of compression at the first heat exchanger 43 at approximately 60 ° C., and the regenerative heat exchanger 44, 2 Passes through the heat exchanger 45 and flows into the second working chamber 66a. The inflowing helium expands in the second working chamber 66a by the movement of the displacer piston 63 in the direction of the partition wall 65 (bottom dead center direction), and has a lower temperature (for example, approximately −20 ° C.) than the helium in the first heat exchanger 43. ) Freezing. The helium that has generated refrigeration flows into the second radiator 45 from the second working chamber 66a due to the movement of the displacer piston 63 in the top dead center direction, and is cooled by the second radiator 45 at approximately −20 ° C. Cool (not shown).

  Further, a part of the expansion work generated in the second working chamber 66 a is spent on the compression work of helium in the first working chamber 61 a via the displacer piston 63. Then, the helium that has cooled the object to be cooled returns to the first gas pisting working chamber 48a through the regenerative heat exchanger 44 and the first heat exchanger 43, and completes one cycle.

  In one cycle as an engine, the temperature of the first heat exchanger 43 (for example, approximately 60 ° C.) is higher than the temperature of the second heat exchanger 45 (for example, approximately −20 ° C.).

  The regenerative heat exchanger 44 gradually cools with a regenerator element filled in the regenerative heat exchanger 44 with helium flowing out from the first heat exchanger 43 and flowing into the second heat exchanger 45.

  In the reverse flow, the helium that has passed through the second heat exchanger 45 flows into the end portion 44b of the regenerative heat exchanger 44 and is gradually heated by the regenerator element. Therefore, the end 44a of the regenerative heat exchanger 44 is a high temperature end, and the end 44b is a low temperature end.

  Accordingly, the combined variable volume width obtained by adding the variable volume width V1 of the power working chamber 21a and the variable volume width V1 of the first working chamber 61 in consideration of the phase, that is, the combined working space of the combined scavenging volume Vsum1, is: It is located on the end 44a side of the regenerative heat exchanger 44, which is the high temperature end, and compression work is applied. On the other hand, the second working chamber 66a of the scavenging volume V2 where expansion work is performed is on the end 44b side of the regenerative heat exchanger 44, which is a low temperature end. As a result, the pulse tube heat storage engine 1 has high efficiency.

  In the prior art, the power working chamber 21a (scavenging volume V) and the second working chamber 66a (scavenging volume V2) are communicated with each other by pipes to form a combined working space (scavenging volume Vsum2) and the first pulse. It communicates with one end of the tube. The first working chamber (scavenging volume V1) communicates with the second heat exchanger 45. And since the 2nd heat exchanger 45 cools a to-be-cooled body with the refrigeration which generate | occur | produced in the 1st working chamber, the edge part 44b of the regeneration heat exchanger 44 becomes a low temperature end, and the edge part 44a becomes a high temperature end. The combined working space of the scavenging volume Vsum2 to which compression work is applied is located on the high temperature end side of the regeneration heat exchanger 44, and the first working chamber (scavenging volume V1) in which expansion work is performed is the low temperature of the regeneration heat exchanger 44. Located on the end side. As a result, the prior art pulse tube heat storage engine is highly efficient.

  Therefore, when the pulse tube type heat storage engine 1 operates as a refrigerator, the efficiency becomes high as in the prior art.

  The same effect can be obtained even when described from the first gas piston working chamber 48 side, that is, the scavenging volume Vg of the first gas piston working chamber 48a is substantially the same as the associated scavenging volume Vsum1 for the first gas piston working chamber 48a. It is. Therefore, the scavenging volume Vg of the first gas piston working chamber 48a located on the high temperature end 44a side of the regenerative heat exchanger 44 is the scavenging volume V2 of the second working chamber 66a located on the low temperature end 44b side of the regenerative heat exchanger 44. Since it is larger, when the pulse tube type heat storage engine 1 is operated as a refrigerator, the efficiency becomes high as in the prior art.

  The first gas piston 48 functions as a heat insulating material that reciprocates in the first pulse tube 42, and the heat of the helium at, for example, about 60 ° C. in the power operating unit 21 is applied to the power operating unit 21 a and the displacer unit 60. Suppresses intrusions. Thereby, the temperature rise of the power cylinder 22 of the power unit 20, the power piston 23, the support spring 28 of the linear drive unit 25a, the permanent magnet, and the support spring 33 of the balancer 30 is suppressed, and the clearance seal, permanent magnet, support spring 28, The support spring 33 functions properly. Similarly, the temperature rise of the displacer cylinder 62, the displacer piston 63, the rod 64, the partition wall 65, and the support spring 67 of the displacer unit 60 is suppressed, and the clearance seal and the support spring 67 function appropriately. As a result, the durability and reliability of the pulse tube heat storage engine 1 are improved.

  Moreover, since the electric resistance of the coil of the stator 27 and the holding force of the permanent magnet of the mover 26 are appropriately maintained and the efficiency of the linear drive unit 25a is improved, the efficiency of the pulse tube heat storage engine 1 is improved.

  Next, the case of (Case 2) in FIG. As shown in FIG. 1 (B), the pulse tube type heat storage engine 1B has the communication destination of the first working chamber 61a and the communication destination of the second working chamber 61b as shown in FIG. 1 (A). Unlike the above, the other configurations are the same as those of the pulse tube heat storage engine 1. That is, the first working chamber 61 a and the second heat exchanger 45 are communicated with each other through the pipe 83. The second working chamber 66a and the power working chamber 21a are connected via a pipe 81. The middle of the pipe 81 is connected to one end of the pipe 82, and the other end of the pipe 82 is connected to the distributor 41.

  As a result, the combined working portion 35a is formed by adding the power working chamber 21a of the power working portion 21 and the second working chamber 66a of the second working portion 66 together. The variable volume width Vsum2 (federation scavenging volume) of the combined working space of the combined working portion 35a is added in consideration of the phase of the variable volume width V of the power working chamber 21a and the variable volume width V2 of the second working chamber 66a. Value.

  When the pulse tube type heat storage engine 1B operates with the engine, the first heat exchanger 43 is heated to a high temperature in the same manner as the pulse tube type heat storage engine 1 in FIG. 1A, and the second heat exchanger 45 compresses heat. Is dissipated.

  When the pulse tube type heat storage engine 1B operates with a refrigerator, as with the pulse tube type heat storage engine 1 of FIG. 1 (A), the second heat exchanger 45 is interposed to refrigerate generated in the first working chamber. The cooling body is cooled, and the compression heat is radiated by the first heat exchanger 45.

  Therefore, in any case where the pulse tube type heat storage engine operates as an engine or a refrigerator, the end portion 44a of the regenerative heat exchanger 44 is a high temperature end, and the end portion 44b of the regenerative heat exchanger 44 is a low temperature end. As a result, the combined scavenging volume (Vsum2) of the combined working unit located on the high temperature end side of the regenerative heat exchanger is larger than the scavenging volume V1 of the second working chamber located on the low temperature end side of the regenerative heat exchanger. As a result, the effect of the pulse tube type heat storage engine 1B is the same as the effect of the pulse tube type heat storage engine 1 of FIG.

  As described above, the pulse tube type heat storage engine provides the pulse tube type heat storage engine 1B and the pulse tube type heat storage engine 1B that are highly efficient, small in size, and convenient for any operation as an engine or a refrigerator. it can.

(Second Embodiment)
FIG. 2 is an explanatory diagram according to the second embodiment of the present invention. The same reference numerals as those in FIG. 1 denote the same parts and the same parts as those in FIG.

  As shown in FIG. 2, the heat exchange operation part 50 of the pulse tube type heat storage engine 2 is configured by newly adding a second pulse tube 46 and a distributor 47 to the heat exchange operation part 40 shown in FIG. That is, a second pulse tube 46 and a distributor 47 are newly provided between the second heat exchanger 45 shown in FIG. 1 and the second working part 66, and the end of the distributor 47 is interposed with the pipe 83. The second working portion 66 is configured to communicate with the second working chamber 66a.

  The second pulse tube 46 is formed with a second gas piston 49 (indicated by a one-dot chain line in the drawing) that reciprocates similarly to the first pulse tube 42 of FIG. A second gas piston working chamber 49a is formed by being surrounded by the second pulse tube 46, the second gas piston 49, and the second heat exchanger 45. The second pulse tube 46 is made of a thin tube having a low thermal conductivity, a thin wall, and a long axial direction.

  The second gas piston 49 is formed of the same cylindrical helium as the inner periphery of the second pulse tube 46, has a constant mass, and the volume changes with helium pressure fluctuation. In other words, the second gas piston 49 is in the form of an elastic piston whose volume changes with the pressure fluctuation of helium. And the 2nd gas piston 49 reciprocates between the edge part 46a and the edge part 46b of the 2nd pulse tube 46, respectively changing volume.

  When the pulse tube heat storage engine 2 operates as an engine, the second gas piston working chamber 49a functions as a compression chamber and compresses helium. When operating as a refrigerator. The second gas piston working chamber 49a functions as an expansion chamber and generates refrigeration. In any case, the volume variation of the second gas piston working chamber 49a is transmitted to the second working chamber 66a via the second gas piston 49, and the volume variation of the second working chamber 66a is operated by the second gas piston operation. This is substantially the same as the volume fluctuation of the chamber 49a.

  In the pulse tube type heat storage engine 2, the function of the second pulse tube 46 is added by the addition of the second pulse tube 46. Basically, the pulse tube type heat storage engine 1 shown in FIG. Same operation as.

  When the pulse tube heat storage engine 2 operates as an engine, the first heat exchanger 43 is heated by, for example, combustion gas (for example, approximately 500 ° C.), and the compression heat (for example, approximately 500 ° C.) is radiated by the second heat exchanger 45. Is done. Accordingly, as in the pulse tube heat storage engine 1 of FIG. 1A, the end portion 44a of the regenerative heat exchanger 44 is a high temperature end, and the end portion 44b is a low temperature end.

  On the other hand, when the pulse tube type heat storage engine 2 operates as a refrigerator, the first heat exchanger 43 radiates the compression heat of helium compressed in the first gas piston chamber 48a at, for example, about 60 ° C., and the second heat The exchanger 45 cools the object to be cooled by refrigeration (for example, −60 ° C.) having a temperature lower than that of the first heat exchanger 43 generated in the second gas piston working chamber 49a. Thereby, like the pulse tube type heat storage engine 1 of FIG. 1A, the end portion 44a of the regenerative heat exchanger 44 becomes a high temperature end, and the end portion 44b becomes a low temperature end.

  Therefore, in any case where the pulse tube heat storage engine 2 operates as an engine or a refrigerator, the combined scavenging volume Vsum1 of the combined operating portion 35 located on the high temperature end 44a side of the regenerative heat exchanger 44 is the regenerative heat exchanger. 44 is larger than the scavenging volume V2 of the second working chamber 66a located on the low temperature end 44b side. As a result, the same effect as the pulse tube type heat storage engine 1 of FIG. 1A is produced, and in any case of operating as an engine or a refrigerator, the pulse tube type heat storage engine is highly efficient, small and convenient. 2 can be provided.

  When the pulse tube type heat storage engine 2 operates as an engine, the second gas piston 49 becomes a heat insulating material, and the low temperature (for example, about 40 ° C.) from the high temperature (for example, about 60 ° C.) second gas piston working chamber 49a. The conduction heat that enters the second operating portion 66 is suppressed. Thereby, the temperature rise of the displacer cylinder 62 of the displacer part 60, the displacer piston 63, the rod 64, the partition 65, and the support spring 67 is suppressed. As a result, the clearance seal and the support spring 67 function properly, and the durability and reliability of the pulse tube heat storage engine 2 are improved.

  When the pulse tube type heat storage engine 2 operates as a refrigerator, the second gas piston 49 serves as a heat insulating material, and has a low temperature (for example, about −60 ° C.) from the second operation part 66 having a high temperature (for example, about 40 ° C.). The conduction heat entering the second gas piston working chamber 49a is suppressed. As a result, the amount of refrigeration generated in the second gas piston working chamber 49a is increased, and the efficiency of the pulse tube heat storage engine 2 is improved.

(Third embodiment)
FIG. 3 is an explanatory diagram according to the third embodiment of the present invention. The same reference numerals as those in FIG. 1 denote the same parts and the same parts as those in FIG.

  As shown in FIG. 3, the pulse tube heat storage engine 3 includes a linear motor 70 between a pair of support springs 67 of the displacer unit 60, and the linear motor 70 is connected to the displacer piston 63. Other configurations are the same as those of the pulse tube type heat storage engine 1 of FIG. That is, the linear motor 70 includes a stator 72 that is a displacer cylinder 62 and a mover 71 having a permanent magnet. The mover 71 has a rod 64 supported by a support spring 67, and the rod 64 is connected to the back surface of the displacer piston 63.

  By providing the linear motor 70, the phase difference between the displacer piston 63 and the power piston 23 and the stroke of the displacer piston 63 can be adjusted, and the phase difference and stroke can be set to optimum values according to the use situation. The efficiency of the engine 3 is improved. Other operations and effects are the same as those of the pulse tube type heat storage engine 1 of FIG.

(Fourth embodiment)
FIG. 4 is an explanatory diagram according to the fourth embodiment of the present invention. The same reference numerals as those in FIG. 1 denote the same parts and the same parts as those in FIG.

  As shown in FIG. 4, in the pulse tube type heat storage engine 4, a flow path resistance adjusting means 84 is connected between a pipe 82 and a pipe 83 of the pulse tube type heat storage engine 1 of FIG. That is, the flow rate adjusting means 84 such as a needle valve is connected between the middle of the pipe 82 and the middle of the pipe 83. By adjusting the flow path resistance adjusting means 84, the first working chamber 61a, the pipe 81, the pipe 82, the heat exchange operating unit 50, the pipe 83, the second working chamber 66a, the displacer cylinder 62 and the displacer piston 63. And the generation of a circulating flow of helium that circulates in the loop F1 (FIG. 4) with the first working chamber 61a. As a result, the pulse tube type heat storage engine 4 is reduced in loss due to the circulation flow, and the efficiency is improved. Other operations and effects are the same as those of the pulse tube type heat storage engine 2 of FIG.

(Fifth embodiment)
FIG. 5 is an explanatory diagram according to the fifth embodiment of the present invention. The same reference numerals as those in FIG. 1 denote the same parts and the same parts as those in FIG.

  As shown in FIG. 5, the pulse tube type heat storage engine 5 includes a heat exchange operation unit 40, a heat exchange operation unit 40 </ b> A between the pipe 82 and the pipe 83 of the pulse tube type heat storage engine 1 of FIG. Are deployed in parallel with each other. That is, one end of the pipe 82 and one end of the pipe 83 are connected to both ends of the heat exchange operation unit 40, and the other end of the pipe 82 is connected to the middle of the pipe 81. The other end of the pipe 83 communicates with the second working chamber 66a, and a valve 85 is provided in the middle of the pipe 83. Similarly, one end of the pipe 86 and one end of the pipe 87 are connected to both ends of the heat exchange operation unit 40A. The other end of the pipe 86 is connected in the middle of the pipe 82, the other end of the pipe 87 is connected in the middle of the pipe 83, and a valve 85 is provided in the middle of the pipe 87.

  Both the valve 85 on the pipe 83 side and the valve 85 on the pipe 87 side are adjusted to suppress the circulation flow of the loop F2 indicated by the dotted line that circulates through the heat exchange operation unit 40 and the heat exchange operation unit 40A. As a result, the pulse tube type heat storage engine 5 is reduced in loss due to the circulation flow and improved in efficiency.

  The pulse tube type heat storage engine 5 operates the first heat exchanger 43 of the heat exchange operation unit 40 and the first heat exchanger 43 of the heat exchange operation unit 40A at different temperatures, so that the pulse tube type heat storage engine 5 The efficiency is improved. For example, in the case of an engine, the first heat exchanger 43 of the heat exchange operation unit 40A is heated with the combustion gas at about 500 ° C., and the first heat exchanger of the heat exchange operation unit 40 with the combustion gas discharged at about 250 ° C. 43 is heated. As a result, the thermal energy of the combustion gas is effectively utilized in a wide temperature range. As a result, the efficiency of the pulse tube heat storage engine 5 is improved.

  In the case of a refrigerator, for example, cooling air is supplied to the second heat exchanger 45 of the heat exchange operation unit 40 to be cooled to about 20 ° C., and then the second heat exchanger 45 of the heat exchange operation unit 40A. And cool to about 10 ° C. Thereby, since the heat quantity which cools blowing air increases, the efficiency of the pulse tube type heat storage engine 5 improves.

  Other operations and effects are the same as those of the pulse tube type heat storage engine 1 of FIG.

(Sixth embodiment)
FIG. 6 is an explanatory view according to the sixth embodiment of the present invention. The same reference numerals as those in FIG.

  As shown in FIG. 6, as shown in FIG. 6, the pulse tube type heat storage engine 6 includes two heat exchange operation units 40 and two heat exchange operation units 40 </ b> A of the pulse tube type heat storage engine 1 of FIG. It is a two-stage expansion type (in the case of an engine) heat storage engine combined with a stage. That is, one end of the pipe 82 and one end of the pipe 83 are connected to both ends of the heat exchange operation unit 40. The other end of the pipe 82 is connected in the middle of the pipe 81, and a valve 88 is provided in the middle of the pipe 82. The other end of the pipe 83 communicates with the second working chamber 66a. Also, one end of the pipe 86 and one end of the pipe 87 are connected to both ends of the heat exchange operation unit 40A. The other end of the pipe 86 is connected in the middle of the pipe 82, and a valve 88 is provided in the middle of the pipe 87. The other end of the pipe 87 is connected to the first heat exchanger 43 of the heat exchange operation unit 40.

  The pulse tube heat storage engine 6 is preferably operated as an engine. For example, the first heat exchanger 43 of the heat exchange operation unit 40A is heated with the combustion gas of about 500 ° C., and the first heat exchanger 43 of the heat exchange operation unit 40 is heated with the combustion gas discharged at 250 ° C. Thereby, the thermal energy of combustion gas is effectively utilized in a wide temperature range.

  In this case, the loop F3 indicated by the dotted line reciprocates (through the second heat chamber 43a through the first heat exchanger 43 of the heat exchange operation unit 40, the pipe 87, and the second heat exchanger 45 of the heat exchange operation unit 40A). The heat loss ΔQ on the heat exchange operation part 40 side of helium that reciprocates between the first gas piston operation chambers 48a of the heat exchange operation part 40A is the first gas piston operation chamber 48a of the heat exchange operation part 40. It is compensated by the expansion work generated in As a result, the expansion work that can be effectively used in the first gas piston working chamber 48a of the heat exchange operation part 40A is increased by the heat loss ΔQ, and the efficiency of the heat exchange operation part 40A on the higher temperature side is improved. As a result, the pulse tube type heat storage engine 6 has higher efficiency than the pulse tube type heat storage engine 5 of FIG.

  Further, when the pulse tube type heat storage engine 6 is operated as a refrigerator, the temperature of the first gas piston working chamber 48a of the heat exchanging operation unit 40A is near room temperature. On the other hand, the first gas piston working chamber 48a of the heat exchange operating unit 40 becomes a low-temperature compression chamber whose temperature is lower than the temperature of the first gas piston working chamber 48a of the heat exchange operating unit 40A. The scavenging mass of helium in the piston working chamber 48a is greater than when the temperature is near normal temperature. As a result, the amount of refrigeration generated in the second working chamber 66a increases, but the efficiency does not change.

  Further, the valve 88 on the pipe 82 side and the valve 88 on the pipe 86 side are the pipe 82 including the valve 88, the pipe 86 including the valve 88, the heat exchange operation unit 40 </ b> A, the pipe 87, and the heat exchange operation unit 40. Is provided to suppress the circulation flow circulating in the loop F3 (FIG. 6) formed by That is, the two valves 88 are adjusted to suppress heat loss due to the above-described circulation flow. As a result, the pulse tube type heat storage engine 6 is reduced in loss due to the circulation flow, and the efficiency is improved. Other effects are the same as those of the Luz tube type heat storage engine 1 of FIG.

(Seventh embodiment)
FIG. 7 is an explanatory view according to the seventh embodiment of the present invention. The same reference numerals as those in FIGS. 1 and 6 denote the same parts and the same parts as those in FIGS.

  As shown in FIG. 7, the pulse tube heat storage engine 7 is a modified embodiment of the pulse tube heat storage engine 6 of FIG. The operation as the heat storage engine is substantially the same as that of the pulse tube type heat storage engine 6, and the circulation loop of the circulation flow is different. That is, the pipe 81 in FIG. 6 is removed, the power side working chamber 21a and the distributor 41 of the heat exchange operating unit 40 are communicated by the pipe 92, and the first working chamber 61a and the heat exchange operating unit 40A are connected by the pipe 93. The power working chamber 21a and the first working chamber 61a are separated from each other. Then, the middle of the pipe 92 and the middle of the pipe 93 are connected via a flow rate adjusting means 91 such as a needle valve. As a result, the circulation loop F3 (FIG. 6) of the pulse tube type heat storage engine 6 is eliminated, and the first working chamber 61a, the gap between the displacer piston 63 and the displacer cylinder 62, the second working chamber 66a, and the pipe 83 are newly added. A loop F4 that circulates through the heat exchange operating unit 40 and the pipe 93 is formed. The flow rate adjusting means 91 suppresses the circulation flow of helium that circulates in the loop F4. As a result, the pulse tube type heat storage engine 7 is reduced in loss due to the circulation flow, and the efficiency is improved.

  The pulse tube type heat storage engine 7 is preferably operated as an engine in the same manner as the pulse tube type heat storage engine 6 of FIG. The other effects are the same as those of the pulse tube heat storage engine 1 of FIG.

(Eighth embodiment)
FIG. 8 is an explanatory view according to the eighth embodiment of the present invention. The same reference numerals as those in FIGS. 5 and 7 denote the same parts and the same parts as those in FIGS.

  As shown in FIG. 8, the pulse tube heat storage engine 8 is a modified embodiment of the pulse tube heat storage engine 5 of FIG. The operation of the pulse storage heat storage engine 8 as a heat engine is the same as that of the pulse tube heat storage engine 5. As in the case of the pulse storage type heat storage engine in FIG. 7, the power side working chamber 21a and the distributor 41 of the heat exchange operating unit 40 are connected by a pipe 92, and the first working chamber 61a and the heat exchange operating unit 40A are connected by a pipe. 93, the power working chamber 21a and the first working chamber 61a are separated. Then, the middle of the pipe 92 and the middle of the pipe 93 are connected via a flow rate adjusting means 91 such as a needle valve. As a result, the circulation loop F3 of the pulse tube type heat storage engine 6 is eliminated, and the first working chamber 61a, the gap between the displacer piston 63 and the displacer cylinder 62, A loop F4 that circulates through the two working chambers 66a, the pipe 83, the heat exchange operating unit 40, and the pipe 93 is formed. The flow rate adjusting means 91 suppresses the circulation flow of helium that circulates in the loop F4. As a result, the pulse tube type heat storage engine 8 is reduced in loss due to the circulation flow and improved in efficiency.

  The pulse tube type heat storage engine 8 is suitable as an engine in the same manner as the pulse storage type heat storage engine 5 of FIG. The other effects are the same as those of the pulse tube heat storage engine 1 of FIG.

(Ninth embodiment)
FIG. 9 is an explanatory diagram according to the ninth embodiment of the present invention. The same reference numerals as in FIG. 8 denote the same parts and parts as those in FIG.

  As shown in FIG. 9, the pulse tube heat storage engine 9 is a modified embodiment of the pulse tube heat storage engine 8 of FIG. The operation of the heat storage pulse tube heat storage engine 9 as a heat engine is the same as that of the pulse tube heat storage engine 9. Then, the valve 91 of FIG. 8 is removed. The circulation flow in the loop F4 (FIG. 9) on the heat exchange operation unit 40 side is suppressed by adjusting the flow resistance of the heat exchange operation unit 40 and the flow resistance of the heat exchange operation unit 40A in advance. As a result, the pulse tube type heat storage engine 9 is reduced in loss due to the circulation flow, and the efficiency is improved.

  The pulse tube type heat storage engine 9 is suitable as an engine in the same manner as the pulse tube type heat storage engines 5 and 8. The other effects are the same as those of the pulse tube heat storage engine 1 of FIG.

(10th Embodiment)
FIG. 10 is an explanatory diagram according to the tenth embodiment of the present invention, and the same reference numerals as those in FIG.

  As shown in FIG. 10, the pulse tube type heat storage engine 10 is a modified embodiment of the pulse tube type heat storage engine 9 of FIG. The operation of the pulse tube heat storage engine 10 as a heat engine is basically the same as that of the pulse tube heat storage engine 9, and the power operation unit 21A of the power unit 20A and the first operation unit 61A of the displacer unit 60A are: The configuration of the power operating unit 21 in FIG. 9 and the first operating unit 61 of the displacer unit 60 are different.

  That is, the power piston 23a and the power cylinder 22a are both convex, and the power working chambers 21b and 21c are formed. Similarly, the displacer piston 63a and the displacer cylinder 62a are both convex, and a first moving chamber 61b and a first moving chamber 61c are formed. The power working chamber 21 b and the first working chamber 61 b are communicated with each other by a pipe 94, and the middle of the pipe 94 and the distributor 41 of the heat exchange operating unit 40 are connected by a pipe 93. The power working chamber 21c and the first working chamber 61c are communicated with each other by a pipe 95, and the middle of the pipe 95 and the distributor 41 of the heat exchange operating unit 40A are connected by a pipe 92. Accordingly, a circulation flow of the loop F5 (FIG. 10) on the heat exchange operation unit 40 side is generated. The circulation flow of the loop F5 is a flow path resistance of the heat exchange operation unit 40 and a flow path of the heat exchange operation unit 40A. It is suppressed by adjusting the resistance. As a result, the loss due to the circulating flow is reduced in the pulse tube heat storage engine 10 and the efficiency is improved.

  The pulse tube type heat storage engine 10 is suitable as an engine in the same manner as the pulse storage type heat storage engines 5 and 9.

  The other effects are the same as those of the pulse tube heat storage engine 1 of FIG.

(Eleventh embodiment)
FIG. 11 is an explanatory view according to the eleventh embodiment of the present invention, and the same reference numerals as those in FIG.

  As shown in FIG. 10, the pulse tube heat storage engine 10 is a modified embodiment of the pulse tube heat storage engine 5 of FIG. 5 and the pulse tube heat storage engine 9 of FIG. The operation of the heat storage pulse tube type heat storage engine 11 is basically the same as that of the pulse tube type heat storage engine 9, and the second operation unit 66A of the displacer unit 60B is replaced by the second operation unit 66 of FIG. Different from the configuration.

  That is, the back side of the displacer piston 63b and the back side of the displacer cylinder 62b are both convex, and a second working chamber 66b and a second working chamber 66c are formed. The second moving chamber 66b communicates with the second heat exchanger 45 of the heat exchange operating unit 40 via the pipe 83, and the first moving chamber 66c communicates with the second heat exchanger 45 of the heat exchange operating unit 40A via the pipe 87. Communicate with.

  Since the pressures of the second moving chamber 66b and the first moving chamber 66c are the same pressure, the helium flowing through the clearance seal (the seal between the second working chamber 66b and the second working chamber 66c) on the small diameter side of the displacer piston 63b It disappears, and the circulating flow in the loop F2 shown in FIG. 5 and the loop F4 shown in FIG. 9 disappears. As a result, the pulse tube type heat storage engine 10 does not require adjustment of the flow path resistance by a valve or the like or the flow path resistance of the heat exchange operation units 40 and 40A. Therefore, the valve 85 provided in the pipe 83 and the valve 85 provided in the pipe 87 shown in FIG. 5 can be removed. As a result, the pulse tube heat storage engine 11 has no loss due to the circulation flow, and the efficiency is improved.

  Further, the pulse tube type heat storage engine 10 is suitable as an engine in the same manner as the pulse storage type heat storage engines 5 and 9. The effects of the other pulse tube type heat storage engine 10 are the same as those of the pulse tube type heat storage engine 5 of FIG.

It is explanatory drawing concerning 1st Embodiment of this invention. It is explanatory drawing concerning 2nd Embodiment of this invention. It is explanatory drawing concerning 3rd Embodiment of this invention. It is explanatory drawing concerning 5th Embodiment of this invention. It is explanatory drawing concerning 5th Embodiment of this invention. It is explanatory drawing concerning 6th Embodiment of this invention. It is explanatory drawing concerning 7th Embodiment of this invention. It is explanatory drawing concerning 8th Embodiment of this invention. It is explanatory drawing concerning 9th Embodiment of this invention. It is explanatory drawing concerning 10th Embodiment of this invention. It is explanatory drawing concerning 11th Embodiment of this invention.

Explanation of symbols

1, 1B, 2, 3, 5, 6, 7, 8, 9, 10, 11 Pulse tube type heat storage engine 20, 20A Power unit 21, 21A Power operation unit 22, 22a Power cylinder 23, 23a Power piston 25 Drive unit 25a Linear motor (linear drive means)
26 Movable elements 28, 67 Support springs 40, 40A, 50 Heat exchange operation part 42 First pulse tube 42a End part 43 First heat exchanger 44 Regenerative heat exchanger 45 Second heat exchanger 46 Second pulse tube 60, 60A , 60B Displacer portion 61, 61A First operating portion 62, 62a, 62b Displacer cylinder 63, 63a, 63b Displacer piston 64 Rod 65 Septum 66, 66A Second operating portion

Claims (6)

A pulse tube type heat storage engine that generates power or refrigeration by giving a phase difference between the reciprocating motion of the working gas and the pressure fluctuation,
A power unit including a power cylinder and a power operating unit that is housed in an inner peripheral surface of the power cylinder so as to be reciprocally movable; and a driving unit to which the power piston is connected;
The working gas communicates with a first heat exchanger that absorbs or dissipates heat, a second heat exchanger that dissipates and absorbs heat, and one end of the first heat exchanger and one end of the second heat exchanger. The regenerative heat exchanger that alternately repeats the working gas, heat absorption, and exhaust heat, and the first heat exchanger provided on at least the first heat exchanger side of the first heat exchanger and the second heat exchanger. A first pulse tube in communication with the other end of the heat exchange operating part,
A first actuating portion comprising a displacer cylinder and a front surface of a displacer piston housed in a reciprocating manner on an inner peripheral surface of the displacer cylinder; the displacer cylinder; a back surface of the displacer piston; A displacer portion, and a second actuating portion formed by a rod provided in the displacer cylinder and formed by a partition wall through which the rod passes,
Connecting the power operating part to the end of the first pulse tube forming one end of the heat exchange operating part;
When communicating the first operating part to the end of the first pulse tube, connect the second operating part to the other end of the heat exchange operating part,
When communicating the second operating part to the end of the first pulse tube, the first operating part is connected to the other end of the heat exchange operating part,
The first heat exchanger has a higher temperature than the second heat exchanger, and is a pulse tube type heat storage engine. The pulse tube type heat storage engine according to claim 1, wherein a second pulse tube is provided at the other end of the second heat exchanger. When the pulse tube type heat storage engine operates as an engine, the working gas is heated via the first heat exchanger, the compression heat of the working gas is radiated by the second heat exchanger, and the power operating unit Taking out the expansion work in which the working gas has expanded in the drive unit,
When operating as a refrigerator, the driving unit compresses the working gas in the power operating unit, dissipates the compression heat of the working gas in the first heat exchanger, and the compressed working gas flows in the displacer unit. 3. The pulse tube type heat storage engine according to claim 1, wherein the pulse tube type heat storage engine expands and generates refrigeration. The drive unit is provided with a linear drive means provided with a mover connected to the power piston, and the mover supports the power piston so as to be reciprocally movable by a support spring.
When the pulse tube heat storage engine operates as an engine, the linear drive means operates as a generator,
4. The pulse tube type heat storage engine according to claim 1, wherein when the pulse tube type heat storage engine operates as a refrigerator, the linear drive unit operates as a motor. 5. 5. The pulse tube type heat storage engine according to claim 1, wherein the displacer piston is supported by a support spring so as to be able to reciprocate. The pulse tube type heat storage engine according to claim 1, wherein the pulse tube type heat storage engine includes a plurality of the heat exchange operation units.

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