JP2009198084A - Pulse pipe type heat storage engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a highly convenient pulse pipe type heat storage engine having high reliability and efficiency, and capable of switching a radiator to a heat absorber and the heat absorber to the radiator by suppressing the heat of a working gas intruding into a compressor and an expansion displacer. <P>SOLUTION: This pulse pipe type heat storage engine 1 is provided for generating refrigeration or motive power by imparting a phase difference between the reciprocating motion of the working gas and a pressure variation. One end 17a of a first pulse pipe 17, the heat absorber 16, a regenerative heat exchanger 15, the radiator 14 and one end 13a of a second pulse pipe 13 successively communicate with one another. An expansion chamber 51 communicates with one of the other end 17b side of the first pulse pipe 17 or the other end 13b side of a second pulse pipe 13, and a compression chamber 31 communicates with the other end 13b side of the second pulse pipe 13 when the expansion chamber 51 communicates with the other end 17b side of the first pulse pipe 17, and communicates with the other end 17b side of the first pulse pipe 17 when the expansion chamber 51 communicates with the other end 13b side of the second pulse pipe 13. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a pulse tube type heat storage engine including a regenerator or a heat 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.

  The vibration generator includes a cylinder that defines a compression space, a piston disposed in the cylinder, a drive source that includes a linear motor for reciprocating the piston, and a support spring that supports the piston so as to reciprocate. And have. The support spring holds a minute gap of a clearance seal that seals the working fluid between the piston outer peripheral surface and the cylinder inner peripheral surface. The same support means and the same sealing means are adopted for the displacer system.

The compression space and the displacer working space on the back side of the displacer are sequentially communicated with the high temperature ends of the pipe, the radiator, and the regenerator, and the heat of the compression is radiated by the radiator. (For example, refer to Patent Document 1).
Japanese Patent Laid-Open No. 2806-275352

  However, according to Patent Document 1, the pulse tube type heat storage engine is operated as a refrigerator, and is used, for example, in a hot water / cold water device that converts normal temperature water to hot water using a radiator and cools normal temperature water using a heat absorber. . In this case, in order to change the water at room temperature (approximately 20 ° C.) to, for example, approximately 65 ° C. hot water, the temperature of the radiator is approximately 120 ° C. The compression space and the displacer working space on the back side of the displacer are equal to or higher than the temperature of the radiator (for example, 140 ° C.). Also, each part of the vibration generator (compressor part) and displacer system (displacer part), eg, piston and cylinder, displacer and displacer cylinder, rod and partition clearance seal part on the back of the displacer, support spring for supporting the piston and displacer Each temperature of the permanent magnet of the linear motor that drives the piston becomes a temperature close to or higher than the temperature of the compressed fluid (for example, approximately 140 ° C.). As a result, it becomes difficult to secure an appropriate gap between the clearance seals, and the strength of the support springs and the holding power of the permanent magnets of the linear motor are reduced, resulting in a problem that the reliability of the pulse tube heat storage engine is lowered.

  In addition, there is a problem that the efficiency of the linear motor decreases and the efficiency of the pulse tube type heat storage engine decreases due to a decrease in the holding power of the permanent magnet of the linear motor and an increase in electrical resistance accompanying the temperature increase of the coil.

  In addition, a pulse tube type heat storage engine is operated as an engine and used as, for example, cogeneration. In this case, a cold head (heat absorber) disposed between the regenerator and the pulse tube is heated to about 500 ° C. with combustion gas, and a linear motor as a driving source is operated as a generator to obtain electric energy, and a hot water supply device To use. The hot water supply device dissipates the compression heat of the working gas with a radiator to convert normal temperature water into, for example, approximately 65 ° C. hot water, and further to exhaust water from the combustion gas of the heat absorber to a high temperature (for example, approximately 90 ° C.). To do. A generator generates electrical energy by generating electricity. As described above, the radiator has a high temperature (for example, about 120 ° C.), and the compression chamber has a higher temperature (for example, about 140 ° C.), so that there is a problem that the reliability of the pulse tube type heat storage engine is lowered. .

  In addition, the heat radiator of the pulse tube type heat storage engine cannot radiate heat only by radiating heat, and the heat absorber cannot radiate heat only by absorbing heat.

  The present invention has been made in view of the above problems, and by suppressing the heat of the working gas entering the compressor section and the displacer section, the reliability and efficiency are high, and the radiator is used as the heat absorber. An object of the present invention is to provide a highly convenient pulse tube type heat storage engine that can be switched to a radiator.

In order to solve the above-mentioned problem, the invention described in claim 1 is a pulse tube type heat storage engine that generates refrigeration or power by giving a phase difference between reciprocation of working gas and pressure fluctuation,
A displacer piston, a displacer cylinder that forms an expansion side compression chamber with a rear surface of the displacer piston that forms an expansion chamber with the front surface of the displacer piston and is connected to a rod, and expansion side drive means that enables the displacer piston to reciprocate A compressor part provided with a displacer part provided with, a power piston, a power cylinder that forms a compression side compression chamber with the power piston, and a compression side driving means that enables the power piston to reciprocate, One end of the first pulse tube, a first heat exchanger that absorbs or dissipates the working gas, a regenerative heat exchanger that alternately repeats the working gas, heat absorption, and exhaust heat, and a second heat exchange that dissipates or absorbs heat. And a heat exchange operation part that sequentially communicates one end of the second pulse tube, and the expansion chamber is connected to the other end side of the first pulse tube or the second pulse tube. When the expansion chamber is communicated with the other end side of the first pulse tube, the compression side compression chamber and the expansion side compression chamber communicate with either one of the other end sides of the pulse tube. When the expansion chamber communicates with the other end side of the second pulse tube, it communicates with the other end side of the first pulse tube.

  In the invention according to claim 2, the regenerative heat exchanger includes a heat exchanger between a high temperature side end of the regenerative heat exchanger and a low temperature side end lower in temperature than the end. .

  In the invention according to claim 3, flow path switching means for opening and closing the flow path is provided in the compression chamber and the expansion chamber, and the flow path switching means is such that the compression chamber is communicated with the other end side of the second pulse tube. The expansion chamber communicates with the other end of the first pulse tube, and when the compression chamber communicates with the other end of the first pulse tube, the expansion chamber communicates with the other end of the second pulse tube. Is done.

  In the first aspect of the present invention, when the pulse tube type heat storage engine is operated as a refrigerator, for example, as a hot / cold water device for converting normal temperature water (approximately 20 ° C.) into hot water or cold water, the compression side drive means The power piston is reciprocated. When the power piston reciprocates, the displacer piston reciprocates by the expansion side driving means. When the compression chamber communicates with the end side of the second pulse tube, the second heat exchanger acts as a radiator and the first heat exchanger acts as a heat absorber. Since the second pulse tube is arranged between the compression chamber and the second heat exchanger (hereinafter referred to as a radiator), the movement of the power piston is transmitted to the second gas piston formed in the second pulse tube. The And a gas piston side compression chamber is formed by the 2nd pulse tube, the 2nd gas piston, and the 2nd heat exchanger (henceforth heat radiator). The working gas in the gas piston side compression chamber is compressed by the reciprocating motion of the second gas piston, generates heat of compression, and is heated to a temperature higher than room temperature (approximately 20 ° C.) (for example, approximately 140 ° C. or more). The compression heat is radiated there. Using this heat radiation, room temperature water is converted to, for example, approximately 65 ° C. hot water.

  Since the second gas piston reciprocates between both ends of the second pulse tube, the working gas forming the second gas piston does not flow into the compression chamber. Therefore, conduction heat from the gas piston side compression chamber, that is, conduction heat transmitted through the tube wall of the second pulse tube, and conduction heat transmitted through the second gas piston enter the compression chamber. By making the second pulse tube thin, long in the axial direction, and made of a material with low heat conduction (for example, stainless steel), heat conduction is suppressed and conduction heat from the tube wall becomes small. The second gas piston is formed of the same columnar working gas as the inner periphery of the second pulse tube. Since the thermal conductivity of the working gas (substantially 1/100 of the thermal conductivity of stainless steel) is very small, the conduction heat transmitted through the second gas piston is even smaller. That is, the tube wall of the second pulse tube and the second gas piston act as a heat insulating material with respect to heat conduction.

  As described above, the conduction heat entering the compression chamber from the gas piston side compression chamber is small, and the temperature of the gas piston side compression chamber and the expansion side compression chamber (for example, approximately 140 ° C. or higher) is higher than the room temperature. That is, the temperatures of the compression-side compression chamber and the expansion-side compression chamber are close to substantially room temperature, and the temperatures of the compression-side drive means and the expansion-side drive means are also predetermined appropriate temperatures close to substantially room temperature. For example, if each drive unit is a linear drive, the temperature of each clearance seal between the power piston and the power cylinder, the displacer piston and the displacer cylinder, the support spring that supports the power piston and the displacer piston, and the temperature of the permanent magnet of the linear motor Each has a proper temperature close to about room temperature, and each part functions properly.

  A first pulse tube is disposed between the expansion chamber and the first heat exchanger (hereinafter referred to as a heat absorber), and a first gas piston is formed in the first pulse tube. A gas piston side expansion chamber is formed by the first pulse tube, the first gas piston, and the first heat exchanger (hereinafter referred to as a heat absorber). Then, the working gas cooled by the regenerative heat exchanger (cold accumulator) and flowing in and out of the heat absorber performs expansion work in the gas piston-side expansion chamber, reciprocates the second gas piston, and is at a temperature lower than room temperature (for example, approximately -10 ° C) freezing. The reciprocating motion of the second gas piston is transmitted to the displacer piston, and the expansion work of the gas piston side expansion chamber is transmitted to the expansion chamber. The refrigeration generated in the expansion chamber on the gas piston side cools normal temperature water to, for example, 5 ° C. cold water with a heat absorber.

  Since the first gas piston reciprocates between both ends of the first pulse tube, the working gas forming the first gas piston does not flow into the expansion chamber. Therefore, the conduction heat transmitted from the expansion chamber through the tube wall of the first pulse tube and the conduction heat transmitted through the first gas piston enter the gas piston side expansion chamber that has reached a low temperature. As described above, as in the case of the second pulse tube, the first pulse tube serves as a heat insulating material, and the temperature of the expansion chamber and the expansion side drive means does not become the low temperature of the gas piston side expansion chamber, and is substantially the same. It becomes a predetermined appropriate temperature close to room temperature. As a result, the displacer part functions well.

  As described above, since the temperatures of the compressor unit and the displacer unit can be maintained at a predetermined appropriate temperature close to substantially room temperature, the compressor unit and the displacer unit function properly and a highly reliable pulse tube type heat storage engine can be provided.

  In addition, a pulse tube type heat storage engine is operated as an engine, for example, used as a co-generation, and used for a hot water supply device. In this case, the heat absorber is heated with combustion gas, and the linear motor of the compressor unit (when operated with the refrigerator) is operated as a generator to obtain electrical energy via the power piston. In the radiator, normal temperature water is converted to, for example, approximately 65 ° C. hot water with compressed heat radiated, and further, approximately 65 ° C. hot water is converted to approximately 90 ° C. hot water with exhaust heat of the combustion exhaust gas of the heat absorber.

  In the radiator, when normal temperature water is changed to hot water of approximately 65 ° C., the temperature of the radiator becomes higher than room temperature (for example, approximately 120 ° C.), and the gas piston side compression chamber has a higher temperature (for example, approximately 140 ° C.). ° C).

  Since the second pulse tube is arranged between the gas piston side compression chamber and the compression chamber, the second pulse tube becomes a heat insulating material as in the case of operating as a refrigerator, and from the gas piston side compression chamber, Heat conduction to the compression chamber is suppressed. As a result, although the temperature of the compression chamber on the gas piston side is high, the conduction heat entering the compression chamber is small, the temperature of the compression chamber is close to about room temperature, and the temperature of the compression side drive means is also close to about room temperature. The compressor will function properly at the proper temperature.

  Further, the temperature of the heat absorber becomes a high temperature (for example, approximately 500 ° C.) due to fuel combustion, but since the first pulse tube is disposed between the heat absorber and the expansion chamber, the first pulse tube is insulated. Become a material. Thereby, the heat conduction from the gas piston side expansion chamber to the expansion chamber is suppressed, and the conduction heat entering the expansion chamber is small despite the high temperature of the heat absorber. As a result, the temperature of the expansion chamber is close to about room temperature, the temperature of the expansion side drive means is also a predetermined appropriate temperature close to about room temperature, and the displacer section functions properly.

  As a result, even when used as an engine, the temperature of the compressor section and the displacer section becomes a predetermined appropriate value that is close to about room temperature, and the compressor section and the displacer section function properly, providing a highly reliable pulse tube heat storage engine. it can.

  In the above description, the compression chamber communicates with the end of the second pulse tube. However, when the compression chamber communicates with the end of the first pulse tube, the second pulse tube described above is used. Is replaced with the first pulse tube and the second heat exchanger is replaced with the first heat exchanger, and the operation and effect are the same as described above.

  Further, since the temperature of the compression side driving means becomes a predetermined appropriate temperature close to substantially room temperature, the electric resistance of the coil of the motor (linear motor, rotary electric motor) and the holding force of the permanent magnet are properly maintained, and the efficiency is high. A pulse tube type heat storage engine can be provided.

  Further, by providing flow path switching means between the compression chamber and the first pulse tube and the second pulse tube, and between the expansion chamber and the first pulse tube and the second pulse tube, the compression chamber becomes the second pulse tube. The second heat exchanger becomes a heat radiator. At this time, since the expansion chamber communicates with the first pulse tube, the first heat exchanger becomes a heat absorber. When the flow path switching means is switched and the compression chamber communicates with the first pulse tube, the first heat exchanger becomes a radiator. At this time, since the expansion chamber communicates with the second pulse tube, the second heat exchanger becomes a heat absorber. Therefore, by switching the flow path by the flow path switching means, the first heat exchanger is switched from the heat absorber to the radiator, and the second heat exchanger is switched from the radiator to the heat absorber. A tubular heat storage engine can be provided.

  In the invention according to claim 2, the regenerative heat exchanger (the regenerator or the regenerator) is heated between the high temperature side end of the regenerative heat exchanger and the low temperature side end of the regenerative heat exchanger. An exchanger is provided. Accordingly, when the pulse tube type heat storage engine is used as a refrigerator, the heat exchanger is provided at a position where the temperature of the working gas flowing through the heat exchanger is higher than the temperature of the surrounding air. Air is blown to the heat exchanger, the heat exchanger acts as a radiator, and the working gas flowing in the heat exchanger is cooled, so that the working gas gas is cooled and generated in the expansion chamber on the gas piston side. The amount of refrigeration increases.

  When a pulse tube type heat storage engine is used as an engine, the heat exchanger is provided at a position where the temperature of the working gas flowing through the heat exchanger is lower than the temperature of the combustion exhaust gas of the heat absorber. Then, the exhaust gas was blown into the heat exchanger, the heat exchanger acted as a heat absorber, and the working gas flowing from the gas piston side compression chamber toward the gas piston side expansion chamber was heated, whereby the working gas gas was heated. The power that can be extracted from the power piston increases by approximately the amount of heat. As described above, the efficiency of the pulse tube type heat storage engine is improved in both the refrigerator and the engine.

  In the invention according to claim 3, the compression chamber and the expansion chamber are connected to the flow path switching means, and the flow path switching means is connected when the compression chamber communicates with the end portion side of the second pulse tube. The expansion chamber communicates with the end portion side of the first pulse tube. In this case, the second heat exchanger functions as a heat radiator, and the first heat exchanger functions as a heat absorber. Next, when the flow path switching means switches the flow path and the compression chamber communicates with the end portion side of the first pulse tube, the expansion chamber communicates with the end portion side of the second pulse tube. In this case, the first heat exchange functions as a radiator, and the second heat exchanger functions as a heat absorber. Therefore, by switching the flow path switching means, it is possible to switch either the first heat exchanger or the second heat exchanger to the radiator and the heat absorber. For example, at any one of the first heat exchanger and the second heat exchanger, normal temperature water can be made into hot water and cold water, and a highly convenient pulse tube heat storage engine can be provided.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The pulse tube heat storage engine 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. As shown in FIG. 1, the pulse tube heat storage engine 1 includes a compressor unit 30 that compresses helium (working gas), a displacer unit 50 that expands helium, and refrigeration (in the case of a refrigerator) that exchanges heat with helium. It is comprised from the heat exchange action | operation part 10 which generates work (in the case of an engine).

  The compressor unit 30 includes a power cylinder 33, a power piston 34 provided with a rod 35, and compression-side drive means 40 that reciprocates the power piston 34 with the rod 35 interposed therebetween, and is located at a room temperature (approximately 20 ° C.) atmosphere. Placed in. The compression side compression chamber 32 for compressing helium is formed by being surrounded by a power cylinder 33 and a power piston 34. The compression chamber 31 is formed by a compression side compression chamber 32, an expansion side compression chamber 55 described later, pipes 6 and 7, and a flow path 8.

  The power piston 34 is supported by a pair of support springs 42 with an outer periphery fixed to the housing 41 with a rod 35 interposed therebetween, and a minute gap is held with respect to the inner peripheral surface of the power cylinder 33. This minute gap has a function of a clearance seal for sealing helium.

  The compression side drive means 40 includes a housing 41, a pair of support springs 42, and a linear motor 43 provided in the housing 41. The linear motor 43 includes a stator 44 that is fixed to the inner peripheral surface of the housing 41 and includes a coil wound with a copper wire, and a movable element 45 that includes a permanent magnet 46 and reciprocates relative to the stator 44. . The permanent magnet 46 is fixed to the rod 35. When the mover 45 reciprocates, the power piston 34 reciprocates via the rod 35. The power piston 34 forms a vibration system having a natural frequency determined by the total mass of the power piston 34, the rod 35, and the mover 45 and the spring constant of the pair of support springs 42.

  When the pulse tube heat storage engine 1 is used as an engine, the linear motor 43 operates as a linear generator.

  The displacer unit 50 includes a displacer cylinder 52 having a partition wall 56, a displacer piston 53 (piston) having a rod 54, and expansion side driving means 60 that allows the displacer piston 53 to reciprocate through the rod 54. Placed in a room temperature atmosphere. The expansion chamber 51 in which helium expands is formed by being surrounded by a displacer cylinder 52 and a front surface 53a of the displacer piston 53, and the front surface 53a side of the displacer piston 53 functions as a piston for expanding helium.

  The expansion side compression chamber 55 is formed by being surrounded by the displacer cylinder 52, the back surface 53b of the displacer 53 including the rod 54, and the rod 54, and the back surface 53b side of the displacer piston 53 functions as a piston for compressing helium. To do.

  The displacer piston 53 is supported by a pair of support springs 61 having an outer periphery fixed to the inner peripheral surface of the housing 57 with a small gap with respect to the inner peripheral surface of the displacer cylinder 52 through a rod 54. The This minute gap has a function of a clearance seal for sealing helium. Further, the minute gap provided between the rod 54 and the through hole of the partition wall 56 also has a function of a clearance seal that seals helium.

  The expansion side driving means 60 includes a housing 57 and a pair of support springs 61. The displacer piston 53 forms a vibration system having a natural frequency determined from the displacer piston 53, the total mass of the rods 54, and the spring constant of the pair of support springs 61. The natural frequency of the displacer piston 53 and the natural frequency of the power piston 34 are combined, and the pulse tube heat storage engine 1 is operated in the vicinity of this natural frequency.

  The heat exchange operating unit 10 includes a collector 11, a distributor 12, a second pulse tube 13, a radiator 14 (second heat exchanger), a regenerative heat exchanger 15, and a heat absorber 16 (first heat exchanger). An exchanger), a first pulse tube 17, a distributor 18, and a collector 19. The first pulse tube 17 and the second pulse tube 13 are made of a thin tube having a low thermal conductivity, a thin wall and a long axial direction.

  In the second pulse tube 13, a second gas piston 20 (indicated by a one-dot chain line in the figure) that reciprocates is formed. A gas piston side compression chamber 21 is formed surrounded by the second pulse tube 13, the second gas piston 20, and the radiator 14.

  Similarly, in the first pulse tube 17, a first gas piston 22 (a dashed line in the figure) that reciprocates is formed. A gas piston side expansion chamber 23 is formed by being surrounded by the first pulse tube 17, the first gas piston 22 and the heat absorber 16.

  The first gas piston 22 and the second gas piston 20 are made of the same cylindrical helium as the inner periphery of the first pulse tube 17 and the inner periphery of the second pulse tube 13, respectively, and each has a constant mass and a helium pressure. The volume changes with each change. That is, the first gas piston 22 and the second gas piston 20 are in the form of an elastic piston whose volume changes with the pressure fluctuation of helium. The first gas piston 22 and the second gas piston 20 change the volume, respectively, between the end portion 17a and the end portion 17b of the first pulse tube 17, and the end portion 13a and the end portion 13b of the second pulse tube 13. Reciprocates between.

  The regenerative heat exchanger 15 is configured by laminating a number of wire mesh elements made of a material such as stainless steel having a large heat storage capacity in a thin stainless steel container having a low thermal conductivity. The portion 15a is a high temperature end, the end 15b is a low temperature end, and the temperature of the element gradually decreases from the end 15a along the end 15b. In the case of an engine, the end 15a is a low temperature end, the end 15b is a high temperature end, and the temperature of the element gradually increases along 15a to 15b.

  The radiator 14 includes an inflow port 14a into which normal temperature (approximately 20 ° C.) water that is heated with hot compression heat of helium flows in and an outflow port 14b into which the water flows out. Similarly, the heat absorber 16 includes an inflow port 16a into which normal temperature water to be chilled by refrigeration generated in the gas piston side expansion chamber 23 flows in and an outflow port 16b into which it flows out.

  The compression side compression chamber 32 communicates with the collector 11 through the pipe 6, and the expansion side compression chamber 55 communicates with the middle of the pipe 6 through the flow path 8 and the pipe 7. The expansion chamber 51 communicates with the collector 19 via the pipe 9.

  The compression side driving means 40 and the expansion side driving means 60 are each provided with a linear drive mechanism that enables the power piston 34 and the displacer piston 53 to reciprocate, but may be a crank mechanism. Further, the gas seal of the power piston 34, the displacer piston 53 and the rod 54 is a clearance seal, but a non-lubricated piston ring such as a tetrafluoride resin containing filler and a non-lubricated rod seal may be used.

  Further, although the compressor unit 30 and the displacer unit 50 are separate bodies, the displacer unit 30 and the displacer unit 50 may be integrated, and the power piston 34 and the displacer piston 53 may be arranged coaxially. In this case, the front surface 34a of the power piston 34 and the back surface 53b of the displacer piston 53 are opposed to each other, and the rod 54 provided on the back surface 53b of the displacer piston 53 penetrates the power piston 34 and the rod 35 and is fixed to the housing. Supported by a spring. In this case, the compression chamber is formed between the front surface 34 b of the power piston 34 and the rear surface 53 b of the displacer piston 53. Therefore, the partition wall 56 shown in FIG. 1 becomes unnecessary.

  The compression chamber 31 includes a compression side compression chamber 32 formed by the power piston 34 and the power cylinder 33, and an expansion side compression chamber 55 formed by the back surface 53 b side of the displacer piston 53 and the displacer cylinder 52. However, the compression chamber 31 may be only the compression side compression chamber 32 formed by the power piston 34 and the power cylinder 33. In this case, the displacer piston is in the form of an expander piston, and no compression chamber is provided on the back side of the expander piston.

  Next, the operation and effect of the first embodiment of the present invention shown in FIG. 1 will be described. A case will be described in which the pulse tube heat storage engine 1 is operated as a refrigerator and used in a hot / cold water device that converts normal temperature water into hot and cold water. When a current having a sinusoidal waveform with a vibration frequency corresponding to the natural frequency of the power piston 34 is supplied to the linear motor 43, the power piston 34 reciprocates due to the magnetic force generated by the linear motor 43. When the power piston 34 reciprocates, pressure acts on the front surface 53a and the back surface 53b of the displacer piston 53, and the displacer piston 53 reciprocates. The phase of the volume fluctuation of the compression chamber 31 obtained by adding the volume fluctuations of the compression side compression chamber 32 and the expansion side compression chamber 55 is delayed by approximately 90 ° from the phase of the volume fluctuation of the expansion chamber 51.

  When the volume of the compression chamber 31 is decreasing, the helium in the compression chamber 31, that is, the helium in the compression side compression chamber 32 and the expansion side compression chamber 55 merges in the pipe 6 and sequentially passes through the collector 11 and the distributor 12. It flows into the second pulse tube 13.

  The helium flowing into the second pulse tube 13 pushes the back surface 20b of the second gas piston 20, moves the second gas piston 20 upward in FIG. 1, and compresses the helium in the gas piston-side compression chamber 21. In the gas piston side compression chamber 21, helium generates compression heat and flows into the radiator 14 at a temperature higher than room temperature, for example, 140 ° C.

  The helium that has flowed into the heat exchanger 14 dissipates the compression heat to the outside, and the temperature decreases, for example, reaches approximately 120 ° C. and flows into the regenerative heat exchanger 15. The room-temperature water that has flowed into the inlet 14a of the radiator 14 with this radiated compression heat is heated, for example, becomes hot water of approximately 65 ° C., flows out from the outlet 14b, and is stored in a tank (not shown). Used as hot water.

  In the regenerative heat exchanger 15, the helium that has flowed in is gradually cooled along the flow by the regenerator element, reaches a lower temperature, for example, approximately 0 ° C., passes through the heat absorber 16, and enters the gas piston side expansion chamber 23. Inflow.

  In the gas piston-side expansion chamber 23, helium flowing out of the heat absorber 16 performs expansion work, reciprocates the first gas piston 22, and generates refrigeration at a lower temperature, for example, approximately −10 ° C.

  The expansion work generated in the gas piston side expansion chamber 23 causes the displacer piston 53 to reciprocate via the first gas piston 22. The expansion work generated in the gas piston side expansion chamber 51 is transmitted to the expansion chamber 23. The expansion work transmitted to the expansion chamber 23 is caused to flow in and out of the helium in the expansion side compression chamber 55 by the reciprocating movement of the displacer piston 53 and is compressed in the gas piston side compression chamber 21 via the second gas piston 20. Is spent.

  The refrigeration generated in the gas piston-side expansion chamber 23 is used by the heat absorber 16 to cool the object to be cooled. That is, for example, room-temperature water that is an object to be cooled flows in through the inlet 16a of the heat absorber 16 and is reciprocated through the heat absorber 16 and is cooled with, for example, approximately 0 ° C. to approximately −10 ° C. helium. It becomes cold water and flows out from the outlet 16b, is stored in a tank (not shown), and is used as cold water. The helium that has received heat absorption from the water at normal temperature becomes approximately 0 ° C. and flows into the regenerative heat exchanger 15.

  In the regenerative heat exchanger 15, the helium that has flowed in is warmed along the flow by the regenerator element, gradually becomes a high temperature, passes through the radiator 14, and the lower side of the power piston 34 and the displacer piston 53 in FIG. 1. It flows into the compression side compression chamber 32 and the expansion side compression chamber 55 by the movement in the direction. In this way, one cycle of the pulse tube type heat storage engine is formed.

  Since the second gas piston 20 reciprocates between the end portions 13 a and 13 b of the second pulse tube 13, the working gas that forms the second gas piston 20 is compressed with the compression side compression chamber 32 that forms the compression chamber 31. It does not flow into the expansion side compression chamber 55. Therefore, in the compression side compression chamber 32 and the expansion side compression chamber 55, the conduction heat from the gas piston side compression chamber 21, that is, the conduction heat transmitted through the tube wall of the second pulse tube 13, and the second gas piston 20 are transferred. Conducted heat invades. By making the second pulse tube 13 thin, long in the axial direction, and made of a material with low heat conduction (for example, stainless steel), heat conduction is suppressed and conduction heat from the tube wall becomes small.

  Further, since the thermal conductivity of the working gas (approximately 1/100 of the thermal conductivity of stainless steel) is extremely small, the conduction heat from the second gas piston 20 is further reduced. That is, the tube wall of the second pulse tube 13 and the second gas piston 20 act as a heat conductive heat insulating material. Therefore, the conduction heat entering the compression chamber 31, that is, the compression side compression chamber 32 and the expansion side compression chamber 55 from the gas piston side compression chamber 21 is small. As a result, although the temperature of the gas piston side compression chamber 21 is high, the temperatures of the compression side compression chamber 32 and the expansion side compression chamber 55 are close to room temperature, and the temperatures of the compression side drive means 40 and the expansion side drive means 60 are high. Also, it becomes a predetermined appropriate temperature close to substantially room temperature. As a result, the temperatures of the clearance seal portion between the power piston 34 and the power cylinder 33, the support spring 42 of the compression side drive means 40, and the permanent magnet 46 of the linear motor 43 are each set to a predetermined appropriate value close to substantially room temperature. As the temperature increases, the clearance seal clearance, the holding force of the permanent magnet 46, and the strength of the support spring 42 are maintained at appropriate values, and each function properly. Similarly, each temperature of the clearance seal portion between the displacer piston 53, the displacer cylinder 52, the rod 54, and the partition wall 56 and the support spring 61 of the expansion side drive means 60 is set to a predetermined appropriate temperature close to substantially room temperature. Each function properly.

  Further, since the first pulse tube 17 is disposed between the expansion chamber 51 and the heat absorber 16, the first pulse tube 17 serves as a heat insulating material, and conduction heat that enters the gas piston-side expansion chamber 23 from the expansion chamber 51. Is small for the same reason as described above. As a result, although the temperature (for example, approximately −10 ° C.) of the gas piston-side expansion chamber 23 is low, the temperatures of the expansion chamber 51 and the expansion driving side means 60 become predetermined appropriate temperatures close to substantially room temperature.

  As described above, the permanent magnet 46, the support springs 42 and 61, and the clearance seals of each function properly, and the pulse tube heat storage engine 1 with high reliability can be provided.

  Next, the case where the pulse tube heat storage engine 1 is operated as an engine will be described. When the heat absorber 16 is heated to a high temperature (for example, approximately 500 ° C.) with combustion gas and the heat of the helium is radiated (exhaust heat) with the radiator 14, the helium reciprocating through the heat absorber 16 is heated with the combustion gas, For example, the temperature is raised to about 500 ° C. The heated helium gas causes the first gas piston 22 and the second gas piston 20 to reciprocate so that the phase of the volume fluctuation of the piston-side expansion chamber 23 advances by approximately 90 ° with respect to the volume fluctuation of the gas piston-side compression chamber 21. The reciprocating motion of the second gas piston 20 causes helium to flow into and out of the compression chamber 31, that is, the compression side compression chamber 32 and the expansion side compression chamber 55. The helium flowing into and out of the compression side compression chamber 32 causes the power piston 34 to reciprocate, and the linear motor 43 serves as a generator to generate electric power to obtain electric energy.

  For example, the present invention is adapted to a co-generation hot water supply device that obtains hot water of about 90 ° C. by using heat radiation of helium compression heat in the radiator 14 and exhaust heat of combustion gas in the heat absorber 16. In this case, water at room temperature is raised to, for example, approximately 65 ° C. by the radiator 14, and the warm water heated to approximately 65 ° C. is further heated to approximately 90 ° C. by the combustion exhaust gas of the heat absorber 16. The radiator 14 becomes, for example, approximately 120 ° C., and the gas piston side compression chamber 21 becomes a temperature higher than that of the radiator 14, for example, approximately 140 ° C.

  Since the second pulse tube 13 is disposed between the compression side compression chamber 32 and the expansion side compression chamber 55 and the gas piston side compression chamber 21, the second pulse tube 13 is provided in the same manner as when operating as a refrigerator. The pulse tube 13 acts as a heat insulating material. Thereby, the heat conduction from the gas piston side compression chamber 21 is suppressed, and the conduction heat entering the compression side compression chamber 32 and the expansion side compression chamber 55 is small despite the high temperature of the gas piston side compression chamber 21. . As a result, the temperatures of the compression side compression chamber 32 and the expansion side compression chamber 55 are close to substantially room temperature, and the temperatures of the compression side drive means 40 and the expansion side drive means 60 are also predetermined appropriate temperatures close to substantially room temperature.

  The temperature of the heat absorber 14 becomes a high temperature (for example, approximately 500 ° C.) due to the combustion of fuel. However, since the first pulse tube 17 is disposed between the heat absorber 16 and the expansion chamber 51, the first pulse tube 17 becomes a heat insulating material. As a result, heat conduction from the heat absorber 16 to the expansion chamber 51 is suppressed, and although the temperature of the heat absorber 16 is high, the conduction heat entering the expansion chamber 51 is small, and the temperature of the expansion chamber 51 and the expansion side drive means The temperature of 60 is a predetermined appropriate temperature close to substantially room temperature.

  As described above, even when the pulse tube heat storage engine 1 is operated as an engine, the permanent magnet 46, the support springs 42 and 61, and the clearance seals of each function properly, and the pulse tube heat storage engine 1 with high reliability can be provided. .

  Further, since the temperature of the compression side drive means 40 becomes a predetermined appropriate temperature close to substantially room temperature, the electric resistance of the coil of the stator 44 and the holding force of the permanent magnet 46 of the mover 45 are properly maintained, and the linear motor The efficiency of 43 can be improved and the highly efficient pulse tube type heat storage engine 1 can be provided.

(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, a heat exchanger is provided between the end 15a and the end 15b of the regenerative heat exchanger 15 shown in FIG. That is, the heat exchanger 73 is provided between the regenerative heat exchanger 71 and the regenerative heat exchanger 72 of the heat exchange operation unit 70. When the pulse tube type heat storage engine 2 is used as a refrigerator, the heat exchanger 73 is disposed at a position where the temperature of helium reciprocatingly flowing through the heat exchanger 73 is higher than the temperature of the surrounding air, and the heat exchanger 73 is used as a radiator. To act as. Air is blown to the heat exchanger 73 by the fan 74 and the helium flowing through the radiator 73 is cooled. As a result, the amount of refrigeration generated in the gas piston-side expansion chamber 23 increases by the amount of heat that substantially cools the helium.

  When the pulse tube heat storage engine 2 is used as an engine, the heat exchanger 73 is disposed at a position where the temperature of helium reciprocatingly flowing through the heat exchanger 73 is lower than the temperature of the combustion exhaust gas, and the heat exchanger 73 is used as a heat absorber. Make it work. Combustion exhaust gas is blown to the heat exchanger 73 to heat helium that reciprocates through the heat exchanger 73. As a result, the power extracted from the power piston 34 is increased by the amount of heat that heats the helium.

  As described above, by arranging the heat exchanger 73 at an appropriate position in the middle of the regenerative heat exchanger 15 in FIG. 1, the efficiency of the pulse tube heat storage engine 2 is improved in either case of the refrigerator or the engine.

(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, a flow path switching valve 80 that switches the flow path between the compression chamber 31 (the compression side compression chamber 32 and the expansion side compression chamber 55) and the expansion chamber 51, and the collector 11 and the collector 19. (Channel switching means) is provided. That is, the first flow path port 81 of the flow path switching valve 80 communicates with the compression side compression chamber 32 via the pipe 91 and the expansion side compression chamber 55 via the pipe 92. That is, the first flow path port 81 communicates with the compression chamber 31. The second flow path port 82 communicates with the collector 11 via the pipe 94. The third flow path port 83 communicates with the expansion chamber 51 through a pipe 95, and the fourth flow path port 84 communicates with the collector 19 through a pipe 96.

  FIG. 4 is an explanatory diagram of the flow path switching valve 80 of FIG. As shown in FIGS. 4A and 4B, the flow path switching valve 80 includes a spool 87 having a large-diameter column at both ends and a valve box 85 having a hole 86, and the spool 87 has a hole 86. In contrast, it is slidably inserted with a minute gap. The valve box 85 is provided with channels 81a, 82a, 83a, and 84a. The first channel port 81, the second channel port 82, and the third channel through which helium flows in and out of the channels 81a, 82a, 83a, and 84a, respectively. A channel port 83 and a fourth channel port 84 are provided.

  In FIG. 4A, the first channel port 81 and the second channel port 82, and the third channel port 83 and the fourth channel port 84 communicate with each other. Therefore, the compression chamber 31 communicates with the pipe 93, the flow path switching valve 80, the pipe 94, and the collector 11. The expansion chamber 51 communicates with the collector 19 via a pipe 95, a flow path switching valve 80, and a pipe 96. The collectors 11 and 19 communicate with the end portion 13b of the second pulse tube 13 and the end portion 17b of the first pulse tube 17 through the distributors 12 and 18, respectively.

  When the flow path switching valve 80 is in the state shown in FIG. 4A, the pulse tube heat storage engine 3 is the same as the pulse tube heat storage engine 1 shown in FIG. Therefore, when the flow path switching valve 80 is in the state shown in FIG. 4A, the radiator 14 radiates the compression heat generated in the gas piston side compression chamber 21 and acts as a radiator. Further, the heat absorber 16 cools the object to be cooled by refrigeration generated in the gas piston expansion chamber 23 and acts as a heat absorber.

  In FIG. 4B, the first flow path port 81 and the fourth flow path port 84, and the second flow path port 82 and the third flow path port 83 communicate with each other. Therefore, the compression chamber 31 communicates with the collector 19 via the pipe 93, the flow path switching valve 80, and the pipe 96. The expansion chamber 51 communicates with the collector 11 via a pipe 95, a flow path switching valve 80, and a pipe 94.

  When the flow path switching valve 80 is in the state shown in FIG. 4B, the pulse tube heat storage engine 3 is different from the pulse tube heat storage engine 1 shown in FIG. That is, the gas piston side compression chamber 21 operates as a gas piston side expansion chamber that generates refrigeration, and the radiator 14 functions as a heat absorber that cools the object to be cooled by refrigeration generated in the gas piston side compression chamber 21. On the other hand, the gas piston side expansion chamber 23 operates as a gas piston side compression chamber that compresses helium, and the heat absorber 16 functions as a radiator that radiates the compression heat generated in the gas piston side expansion chamber 23.

  By switching the flow path switching valve 80 from the state of FIG. 4A to the state of FIG. 4B, the radiator 14 is switched from the radiator to the heat absorber, and the heat absorber 16 is switched from the heat absorber to the radiator. Is switched to. Therefore, by switching the flow path switching valve 80, it becomes possible to switch between heat dissipation and heat absorption in either the heat radiator 14 or the heat absorber 16, and one heat exchanger (the heat radiator 14 or the heat absorber) can be switched. 16), normal temperature water can be made into hot water and cold water. As a result, the highly convenient pulse tube type heat storage engine 3 can be provided.

(Fourth embodiment)
FIG. 5 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. 5, the pulse tube type heat storage engine 100 removes the second pulse tube 13 of the pulse tube type heat storage engine 1 of FIG. 1, and instead replaces the power cylinder 113 and the power piston 114 of the compressor unit 110 in the axial direction. Lengthen. The heat exchange operation unit 10A is formed by removing the second pulse tube 13 of the heat exchange operation unit 10 of FIG.

  Further, a pulse tube unit 120 is provided between the compression side compression chamber 112 and the expansion side compression chamber 55, and the pulse tube unit 120 is connected to the compression side compression chamber 112 with a pipe 117, a pipe 116, and a flow path 8 interposed therebetween. It communicates with the expansion side compression chamber 55. The pulse tube unit 120 is configured by sequentially connecting distributors 122 and 124 and collectors 121 and 125 to both ends of the pulse tube 123.

  The power cylinder 113 and the power piston 114 are made of a material that is elongated in the axial direction and has low thermal conductivity. As a result, the conduction heat transmitted from the compression side compression chamber 112 to the compression side drive means 40 at a high temperature (for example, approximately 140 ° C.) can be suppressed. The temperature of the clearance seal portion in the vicinity of the side becomes a predetermined appropriate temperature close to substantially room temperature.

Further, the expansion side compression chamber 55 has a temperature close to substantially room temperature due to the heat insulating action of the pulse tube 123, and therefore the temperature of the expansion side driving means 60 also becomes a predetermined appropriate temperature close to substantially room temperature.

  As described above, the pulse tube heat storage engine 100 with high reliability can be provided for the same reason as the pulse tube heat storage engine 1 of FIG.

  Further, since the second pulse tube 13 of FIG. 1 is removed and the volume of the pulse tube 123 is smaller than the volume of the second pulse tube 13, the pressure amplitude of the pulse tube type heat storage engine 1 is the same at the same sealed pressure. The amount of refrigeration and power generation of the pulse tube heat storage engine 100 is larger than that of the pulse tube heat storage engine 1.

(Fifth embodiment)
FIG. 6 is an explanatory diagram according to the fifth embodiment of the present invention, which is a modification of the fourth embodiment of FIG. The same reference numerals as in FIG. 5 denote the same parts and parts as in FIG.

  As shown in FIG. 6, the pulse tube type heat storage engine 101 includes a heat exchange operation unit 10 </ b> A, a compressor unit 110, and a displacer unit 130 by replacing the pulse tube unit 120 of FIG. 5 with a pipe 137.

  Instead of removing the pulse tube section 120 of FIG. 5, the displacer cylinder 132 and the displacer piston 133, the rod 134 and the partition wall 136 through which the rod 134 penetrates are elongated in the axial direction, and are made of a material having low thermal conductivity. Suppresses conduction. Thereby, heat conduction from the expansion side compression chamber 135 having a high temperature (for example, about 140 ° C.) to the expansion side driving means 60 and the expansion chamber 131 is suppressed, and the expansion side driving means 60 and the expansion chamber 131 are close to about room temperature. It reaches a predetermined appropriate temperature. As a result, a highly reliable pulse tube type heat storage engine 101 can be provided for the same reason as the pulse tube type heat storage engine 1 of FIG.

  5 is removed, the pressure amplitude of the pulse tube type heat storage engine 101 becomes larger than that of the pulse tube type heat storage engine 100 at the same sealed pressure, and the pulse tube type heat storage engine 101 is refrigerated. The amount or power generation amount increases from the pulse tube type heat storage engine 100.

(Sixth embodiment)
FIG. 7 is an explanatory diagram according to the sixth embodiment of the present invention, which is a modification of the first embodiment of FIG. 1 and the fifth embodiment of FIG. The same reference numerals as in FIGS. 1 and 6 denote the same parts and the same parts as those in FIGS. 1 and 6.

  As shown in FIG. 7, the pulse tube type heat storage engine 102 includes a heat exchange operation unit 10B from which the first pulse tube 17 of FIG. 1 is removed, the compressor unit 30 of FIG. 1, and a displacer unit 140. The

  In the displacer section 140, the displacer cylinder 132 and the displacer piston 133 are long as in FIG. 6, and the rod 54 and the partition wall 56 are short as in FIG.

  The pulse tube 13 is disposed between the compression side compression chamber 32 and the expansion side compression chamber 135 and the radiator 14, and the displacer cylinder 132 and the displacer piston 133 are long in the axial direction. Therefore, for the same reason as in the case of the pulse tube type heat storage engines 1 and 101 of FIGS. 1 and 6, the compression side compression chamber 32 and the expansion side compression chamber 135 are at a temperature close to substantially room temperature. As a result, the temperature of the compression side drive unit 40 and the temperature of the expansion side drive unit 60 are respectively predetermined appropriate temperatures close to substantially room temperature, and the pulse tube heat storage engine 102 with high reliability can be provided.

  Since the first pulse tube 17 of FIG. 1 is removed and the pulse tube unit 120 is not provided, the pressure amplitude of the pulse tube type heat storage engine 102 is the same as that of the pulse tube type heat storage engine of FIG. The refrigeration amount and power generation amount of the pulse tube type heat storage engine 102 are larger than those of the pulse tube type heat storage engine 100.

  Further, when used as a refrigerator, the volume on the low temperature side is small, so the efficiency of the pulse tube type heat storage engine 102 is higher than that of the pulse tube type heat storage engine 1.

(Seventh embodiment)
FIG. 8 is an explanatory diagram according to the seventh embodiment of the present invention, which is a modification of the fourth embodiment of FIG. 5 and the sixth embodiment of FIG. 5 and FIG. 7 are denoted by the same reference numerals as those in FIG. 5 and FIG.

  As shown in FIG. 8, the pulse tube type heat storage engine 103 includes a heat exchange operation unit 10B in FIG. 7, a compressor unit 110 in FIG. 5, a pulse tube unit 120 in FIG. 5, and a displacer unit 140 in FIG. Composed.

  Since the power cylinder 113 and the power piston 114 have a heat insulating structure that is long in the axial direction, heat conduction from the compression side compression chamber 112 having a high temperature (for example, approximately 140 ° C.) to the compression side drive means 40 is suppressed, and the compression side drive is performed. The temperature of the means 40 becomes a predetermined appropriate temperature close to substantially room temperature.

  A pulse tube 120 is disposed between the compression side compression chamber 112 and the expansion side compression chamber 135 having a high temperature, and the displacer cylinder 132 and the displacer piston 133 are long in the axial direction. The chamber 135 and the expansion side driving means 60 have a predetermined appropriate temperature close to substantially room temperature. As a result, a highly reliable pulse tube type heat storage engine 103 can be provided.

  Further, since the first pulse tube 13 and the second pulse tube 17 are removed and the volume of the pulse tube 123 is smaller than that of the first pulse tube 13 and the second pulse tube 17, the pulse tube type heat storage engine 103 is used at the same sealed pressure. Is larger than that of the pulse tube type heat storage engines 101 and 102 in FIGS. 6 and 7, and the refrigeration amount and power generation amount of the pulse tube type heat storage engine 103 are larger than those of the pulse tube type heat storage engines 101 and 102.

(Eighth embodiment)
FIG. 9 is an explanatory diagram according to the eighth embodiment of the present invention, which is a modification of the fifth embodiment of FIG. The same reference numerals as those in FIG. 6 denote the same parts and the same parts as those in FIG.

  As shown in FIG. 9, the pulse tube type heat storage engine 104 includes a power cylinder 113 and a power piston instead of the first pulse tube 17 and the second pulse tube 13 of the pulse tube type heat storage engine 1 of FIG. 114, the displacer cylinder 132, the displacer piston 133, the rod 134, and the partition wall 136 have a long heat insulating structure in the axial direction. Therefore, even if the temperature of the compression side compression chamber 112 and the expansion side compression unit 135 is high, and the temperature of the expansion chamber 131 is high or low, the temperatures of the compression side drive means 40 and the expansion side drive means 60 are substantially equal. It becomes a predetermined appropriate temperature close to room temperature. As a result, a highly reliable pulse tube type heat storage engine 104 can be provided.

  Further, since the first pulse tube 17 and the second pulse tube 13 are removed and the pulse tube unit 120 is not provided, the pressure amplitude of the pulse tube type heat storage engine 104 is the same as that of FIG. It becomes larger than the pulse tube type heat storage engine 103, and the amount of refrigeration and power generation of the pulse tube type heat storage engine 104 is larger than that of the pulse tube type heat storage engine 103.

(Ninth embodiment)
FIG. 15 is an explanatory diagram according to the ninth embodiment of the present invention. As shown in FIG. 15, the pulse tube type heat storage engine 4 includes a heat exchange operating unit 10, a compressor unit 30, and a displacer unit 50.

  The compression side compression chamber 32 of the compressor unit 30 is connected to the first pulse tube 17 through the pipe 97, the collector 19, and the distributor 18 in order. The expansion chamber 51 of the displacer unit 50 is also connected to the first pulse tube 17 through the pipe 98, the pipe 97, the collector 19, and the distributor 18. The expansion side compression chamber 55 is connected to the second pulse tube 13 via the pipe 99, the collector 11 and the distributor 12 in this order.

  The heat absorber 16 is heated to a high temperature (for example, 500 ° C.) with combustion gas, the radiator 14 is cooled to a temperature close to room temperature with cooling water, and the pulse tube heat storage engine 4 is operated as an engine. In this case, the compression side compression chamber 32 of the compressor unit 30 operates as an expansion chamber. On the other hand, the expansion chamber 51 of the displacer unit 50 operates as an expansion chamber, and the expansion side compression chamber 55 on the back surface 53b side of the displacer piston 53 operates as a compression chamber. The compression-side compression chamber 32, the expansion chamber 51, the pipe 97, and the pipe 98 form one expansion chamber 58.

  The work generated in the gas piston side expansion chamber 23 by the heat absorbed by the heat absorber 16 is transmitted to the power piston 34 and the displacer piston 53 via the first gas piston 22. The work transmitted to the war piston 34 generates AC power by the linear generator 43a (the linear motor 43 functions as the linear generator 43a) via the rod 35, and is used as AC electrical energy. On the other hand, the work transmitted to the displacer piston 53 is spent on the compression work of helium in the expansion side compression chamber 55.

  The heat absorber 16 has a high temperature of about 500 ° C., for example. However, since the first gas piston 17 is interposed, the temperatures of the compression side compression chamber 32 and the expansion chamber 51 are set to predetermined appropriate temperatures close to about room temperature. Become. As a result, the highly reliable pulse tube type heat storage engine 4 can be provided.

  When the pulse tube type heat storage engine 4 is operated as an engine, the scavenging volume of the high temperature side gas piston side expansion chamber 23 is larger than the scavenging volume of the gas piston side compression chamber 21 whose temperature is lower than that of the gas piston side expansion chamber 23. It is preferable. Since the scavenging volume on the normal temperature side corresponding to the high temperature side gas piston side expansion chamber 23 is the volume obtained by adding the compression side compression chamber 32 and the expansion chamber 51, the pulse tube type heat storage engine 4 is operated as an engine. Is preferred. In the first embodiment of FIG. 1, when the heat absorber 16 is heated to a high temperature with combustion gas and operated as an engine, the normal temperature side corresponding to the gas piston side compression chamber 21 whose temperature is lower than that of the gas piston side expansion chamber 23. Since the scavenging volume is a volume obtained by adding the compression side compression chamber 32 and the expansion side compression chamber 55, it is preferable to operate as a refrigerator rather than an engine. When operating as an engine, the pulse tube heat storage engine 4 is more efficient than the pulse tube heat storage engine 1 of FIG. However, when operating as a refrigerator, the efficiency of the pulse tube heat storage engine 1 is higher than that of the pulse tube heat storage engine 4.

  Moreover, the pulse tube type heat storage engine 4 can also function as a refrigerator. In this case, the expansion chamber 51 functions as a compression chamber, and the expansion side compression chamber 55 functions as an expansion chamber.

(First adaptive form)
FIG. 10 is an explanatory diagram according to the first adaptive embodiment of the present invention, and shows an adaptive form in which the pulse tube type heat storage engine 1 of FIG. 1 is applied to a hot water supply apparatus. The same parts and the same parts as those of the pulse tube type heat storage engine 1 shown in FIG.

  The hot water supply device 200 includes a pulse tube heat storage engine 1 and a hot water supply unit 210. In the hot water supply unit 210, a valve 215 that controls normal temperature water supplied from the pipe 221 is connected to the bottom of the tank 211 via the pipe 222. A valve 216 that controls the supply of hot water (for example, approximately 65 ° C.) stored in the tank 211 to the outside is connected to the upper portion of the tank 211 via a pipe 223.

  The pipe 224 branched from the middle of the pipe 222 is connected to the suction port of the pump 212, and the discharge port is connected to the inlet 14 a of the radiator 14 of the pulse tube type heat storage engine 1 through the pipe 225. The outlet 14b is sequentially connected to the middle of the pipe 223 through the pipe 226, the valve 217, and the pipe 227.

  A valve 218 is provided in the middle of the pipe 226 and the pipe 224 via the pipes 228 and 229. One end of the heat exchanger 213 is connected in the middle of the pipe 224, and the other end is connected in the middle of the pipe 226 through the valve 219. The heat exchanger 213 is provided with a fan 214 and is cooled by blown air. A temperature sensor 220 is provided in the vicinity of the upstream side of the valve 217 of the pipe 226.

  Next, the operation of the hot water supply apparatus 200 will be described.

  Valve 216, valve 217, valve 219 and valve 215 are all closed, valve 218 is opened, pulse tube type heat storage engine 1 and pump 212 are operating, fan 214 is stopped, and pump 212 The part of the pipe 224 and the residual water in the pipes 225, 226, 228, and 229 form a circulating flow through the valve 218, the pump 212 and the radiator 14, and the radiator 14 compresses helium. It is circulated until heated to a predetermined temperature (for example, approximately 65 ° C.). The temperature of the hot water is detected by the temperature sensor 220. Next, when the circulating hot water reaches a predetermined temperature, the valve 217 is opened, the valve 218 is closed, and hot water having the predetermined temperature is sent to the upper side of the tank 211. The pump 212 sucks normal temperature water on the bottom side of the tank 211 and sends it to the radiator 14. In the radiator 14, the supplied water is heated by the compression heat of helium to make hot water of a predetermined temperature (approximately 65 ° C.) and sent to the upper side of the tank 211. When the hot water is lower than a predetermined temperature (for example, approximately 55 ° C.), the valve 218 is opened, the valve 217 is closed, a circulating flow is formed again via the valve 218, and the heat radiator 14 circulates until the predetermined temperature is reached. And warm up.

  When the hot water in the tank 211 is filled with hot water of a predetermined temperature, the valve 219 is opened, and the valve 217 and the valve 218 are closed. The hot water heated by the radiator 14 sequentially passes through the valve 219, the heat exchanger 213, and the pump 212 to form a circulating flow returning to the radiator 14, and heats the compression heat of helium radiated from the radiator 14. It is transferred to the exchanger 213 where it is exhausted.

  Note that the valve 218 and the pipes 228 and 229 do not have to be provided if the capacity of the radiator 14 to receive hot water is large. In this case, the pump 212 is stopped at the time of heating, the hot water is heated by the radiator 14, and when the hot water reaches a predetermined temperature, the pump 212 is operated to send the hot water to the tank 211.

  As described above, since the second pulse tube 17 and the first pulse tube 13 are provided in the pulse tube type heat storage engine 1 even if the temperature of the radiator 14 is high, the temperatures of the compressor unit 30 and the displacer unit 50 are arranged. Becomes a predetermined appropriate temperature close to about room temperature. As a result, the reliability of the pulse tube heat storage engine 1 is improved, and a highly reliable hot water supply apparatus 200 can be provided.

(Second adaptive form)
FIG. 11 is an explanatory view according to the second adaptive embodiment of the present invention, and shows an adaptive form in which the pump 212 of the hot water supply apparatus 200 of FIG. The same parts and the same parts as those of the pulse tube type heat storage engine 1 shown in FIG.

The hot water supply apparatus 201 includes a pulse tube heat storage engine 1 and a hot water supply unit 240. The hot water supply unit 240 includes a tank 242, a heat pipe 241, a fan 243, valves 245 and 246,
It consists of pipes 246, 247, 248, 249.

  Water at room temperature is supplied to the tank 242 at an appropriate time through the pipe 246, the valve 244, and the pipe 247. Hot water is supplied to the outside through a pipe 248, a valve 245, and a pipe 249.

  The heat pipe 241 has a heat absorption part 241 a mounted in the radiator 14, a heating part 241 b is provided in the tank 242, and the exhaust heat part 241 c is cooled by air blown by a fan 243. Water or the like is used as the refrigerant of the heat pipe 241.

  With the fan 243 stopped, the refrigerant of the heat pipe 241 circulates between the heat absorption part 241a and the heating part 241b, absorbs the compression heat of the working gas flowing through the radiator 14 by the heat absorption part 241a, and heats the heating part. In 241b, the heat of compression is radiated to warm water at room temperature in the tank 242 to a predetermined temperature. When the hot water in the tank 242 reaches a predetermined temperature, the fan 243 is rotated to blow air to the exhaust heat unit 241 to exhaust the heat of compression of helium from the exhaust heat unit 241c.

  Since the first pulse tube 17 and the second pulse tube 13 are provided in the pulse tube type heat storage engine 1 even when the temperature of the radiator 14 is high, the pulse tube type heat storage engine 1 is the same as in the first adaptive mode. 1 reliability is improved. As a result, a highly reliable hot water supply apparatus 201 can be provided. In addition, the hot water supply apparatus 201 does not require a pump, the number of valves used is reduced, the configuration is simplified, and the cost is lower than the hot water supply apparatus 200.

(Third adaptive form)
FIG. 12 is an explanatory diagram according to the third adaptive embodiment of the present invention, and shows an adaptive form in which the pulse tube type heat storage engine 1 of FIG. 1 is applied to a hot water / cold water device. The same parts and the same parts as those of the pulse tube heat storage engine 1 shown in FIG.

  The hot water / cold water device 300 includes a pulse tube type heat storage engine 301, a tank 302, a tank 303, a fan 304, a heat exchange operation unit 10C, and a heat exchange operation unit 10D that are the same as the heat exchange operation unit 10 in FIG. And a fan 305.

  The collector 19 of the heat exchange operation unit 10C and the collector 19 of the heat exchange operation unit 10D are communicated with the expansion chamber 51 of the displacer unit 50 through the valve 306 and the valve 307, respectively. The collector 11 of the heat exchange operation unit 10C and the collector 11 of the heat exchange operation unit 10D are communicated with the compression side compression chamber 32 and the expansion side compression chamber 55 of the compressor 30 via the valve 308 and the valve 309, respectively.

  The heat absorber 16 of the heat exchange operation unit 10C is in thermal contact with a tank 302 to which water at normal temperature is supplied at appropriate times, and a fan 304 is provided in the radiator 14.

  In the heat exchanger 14D of the heat exchange operation unit 10D, a tank 303 to which water at room temperature is supplied is in thermal contact with the heat exchanger 16D, and a fan 305 is provided in the heat absorber 16.

  When cold water (for example, approximately 5 ° C.) is obtained from room temperature water, the valve 306 and the valve 308 are opened, the valve 307 and the valve 309 are closed, the heat exchange operation unit 10C is operated, and the room temperature water in the tank 302 is obtained. Is cooled by the heat absorber 16 by refrigeration generated in the gas piston-side expansion chamber 23 and is made cold water (approximately 5 ° C.). At this time, air is blown to the radiator 14 by the fan 304 to radiate the compression heat of helium. Note that the fan 305 on the heat exchange operation unit 10D side is stopped.

  When hot water (for example, approximately 65 ° C.) is obtained from room temperature water, the valve 307 and the valve 309 are opened, the valve 306 and the valve 308 are closed, the heat exchange operation unit 10D is activated, and the room temperature water in the tank 303 is obtained. Is heated by the heat of compression of helium by the radiator 14 to convert the water at room temperature into hot water of approximately 65 ° C. At this time, the temperature of the radiator is high (approximately 120 ° C.), and the temperature of the gas piston side compression chamber is even higher (approximately 140 ° C.). Further, air is blown to the heat absorber 16 by the fan 305 and a heat load is applied to the heat absorber 16. Note that the fan 304 on the heat exchange operating unit 10C side is stopped.

  Since the first pulse tube 17 and the second pulse tube 13 are arranged in the pulse tube type heat storage engine 301 even when the temperature of the 10D radiator 14 is high, the temperatures of the compressor unit 30 and the displacer unit 50 are It becomes a predetermined appropriate temperature close to about room temperature. As a result, the reliability of the pulse tube heat storage engine 301 is improved, and a highly reliable hot water / cold water apparatus 300 can be provided.

  Moreover, the efficiency of the pulse tube type heat storage engine 301 is improved by using the two heat exchange operation units 10C and 10D, the heat exchange operation unit 10C for cold water, and the heat exchange operation unit 10D for hot water.

(4th adaptive form)
FIG. 13 is an explanatory diagram according to the fourth adaptive embodiment of the present invention, and shows an adaptive form in which the pulse tube type heat storage engine 1 of FIG. 1 is applied to a hot water / cold water device. The same parts and the same parts as those of the pulse tube type heat storage engine 1 shown in FIG.

The hot water / cold water device 310 includes a heat pulse tube type heat storage engine 1, a tank 311, a tank 312, a fan 313, and a fan 314.

  The tank 311 and the tank 312 are brought into thermal contact with the heat absorber 16 and the heat radiator 14, respectively, and water at normal temperature is supplied to each of them at appropriate times. The heat absorber 16 and the heat radiator 14 are provided with a fan 313 and a fan 314, respectively.

  When cold water (for example, approximately 5 ° C.) is obtained from room temperature water, the fan 313 is stopped and the fan 314 is operated, and the normal temperature water in the tank 311 is cooled by the heat absorber 16 to be approximately 5 ° C. cold water.

  When hot water (for example, approximately 90 ° C.) is obtained from room temperature water, the fan 313 and the fan 314 are operated, and the room temperature water in the tank 312 is heated by the radiator 14 to be approximately 90 ° C. hot water.

  Further, both the fan 313 and the fan 314 can be stopped, and at the same time, the normal temperature water in the tank 311 can be changed to cold water by the heat absorber 16 and the normal temperature water in the tank 312 can be changed to hot water by the radiator 14.

  The hot water / cold water device 310 is less efficient than the hot water / cold water device 300, but has a simple configuration, a small size and light weight, and a low cost.

  As described above, the pulse tube type heat storage engine 1 is provided with the first pulse tube 17 and the first pulse tube 13 even when the temperature of the radiator 14 becomes high. The hot water / cold water device 310 with improved reliability and high reliability can be provided.

(5th adaptive form)
FIG. 14 is an explanatory diagram according to a fifth adaptive embodiment of the present invention, which is an adaptive mode in which the pulse tube type heat storage engine 1 of FIG. 1 is operated as an engine and applied to a cogeneration system. The same parts and the same parts as those of the pulse tube heat storage engine 1 shown in FIG. 1 and the hot water supply unit 210 shown in FIG.

  As shown in FIG. 14, the cogeneration system 400 includes a pulse tube heat storage engine 1 and a hot water supply unit 410. The linear motor 43 of FIG. 1 provided in the drive unit 40 of the pulse tube type heat storage engine 1 operates as a linear generator 43a. The heat absorber 16 includes a fuel inlet 16c and an air inlet 16d through which fuel and air flow. Further, the heat absorber 16 is provided with a heat exchanger 411 that performs hot water using the burned exhaust gas, and the heat exchanger 411 includes an exhaust gas outlet 411a for exhaust gas. The radiator 14 is provided with a temperature sensor 412 that detects the temperature of the hot water.

  The configuration of the hot water supply unit 410 around the tank 211 is the same as that in FIG. The difference is that the pipe 222 is branched from the middle of the pipe 222 connected to the bottom of the tank 211, and the pipe 224 is sequentially connected to the inlet 14 a of the radiator 14 through the pump 212 and the pipe 225. The outlet 14b of the radiator 14 is sequentially connected to the upper portion of the tank 211 via a pipe 226, a heat exchanger 411, and pipes 227 and 223. The heat exchanger 411 is heated by the exhaust heat of the exhaust gas combusted by the heat absorber 16.

  In the heat absorber 14, the fuel and air flowing in from the inlet 16c and the inlet 16d are mixed and burned, the helium is heated, the pulse tube heat storage engine 1 operates as an engine, and the power piston 34 reciprocates. As the power piston 34 reciprocates, AC power is extracted from the linear generator 43a and supplied to the outside.

  The compression heat generated by the reciprocating motion of the power piston 34 and the displacer piston 53 is used for heating normal temperature water pumped from the pump 212 by the radiator 14. Hot water heated by the radiator 14 and heated (for example, approximately 65 ° C.) flows into the heat exchanger 411, is heated by exhaust heat of the combustion exhaust gas from the heat absorber 16, and is heated to a higher predetermined temperature (for example, It becomes hot water at about 90 ° C. The hot water that has reached the predetermined temperature flows into the upper portion of the tank 211, and the pump 212 is operated until the water in the tank 211 reaches the predetermined temperature. Hot water at a predetermined temperature in the tank is supplied to the outside through a valve 216 at appropriate times.

  If the temperature of the hot water flowing out of the radiator 14 is approximately 65 ° C., for example, the radiator 14 becomes a high temperature, approximately 120 ° C., and the gas piston side compression chamber 21 becomes a higher temperature (approximately 140 ° C.). . As described above, the pulse tube type heat storage engine 1 includes the second pulse tube 17 and the first pulse tube 13 even when the temperatures of the radiator 14 and the heat absorber 16 are increased. In addition, the temperature of the displacer unit 50 becomes a predetermined appropriate temperature close to substantially room temperature. As a result, the reliability of the pulse tube heat storage engine 1 is improved, and a highly reliable cogeneration system 400 can be provided.

  Moreover, since the compression heat of helium and the exhaust gas of the combustion gas are effectively used, it is possible to provide the cogeneration system 400 having a high energy saving effect.

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 of the flow-path switching valve of FIG. It is explanatory drawing concerning 4th 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 the 1st adaptive embodiment of this invention. It is explanatory drawing concerning the 2nd adaptive embodiment of this invention. It is explanatory drawing concerning the 3rd adaptive embodiment of this invention. It is explanatory drawing concerning the 4th adaptive embodiment of this invention. It is explanatory drawing concerning the 5th adaptive embodiment of this invention. It is explanatory drawing concerning 9th Embodiment of this invention.

Explanation of symbols

1, 2, 3, 4, 301 Pulse tube type heat storage engine 10, 10C, 10D, 70 Heat exchange operation part 13 Second pulse tube 13a, 17a One end 13b, 17b Other end 15, 71, 72 Regenerative heat exchanger 14 Radiator (second heat exchanger)
15a, 15b end 16 heat absorber (first heat exchanger)
17 first pulse tube 30 compressor section 31 compression chamber 32 compression side compression chamber 33 power cylinder 34 power piston 40 compression side drive means 50 displacer section 51, 58 expansion chamber 52 displacer cylinder 53 displacer piston 53a front surface 53b back surface 54 rod 55 expansion side Compression chamber 60 Expansion side drive means 73 Heat exchanger 80 Flow path switching valve (flow path switching means)

Claims (3)

A pulse tube type heat storage engine that generates refrigeration or power by giving a phase difference between reciprocation of working gas and pressure fluctuation,
A displacer piston, a displacer cylinder that forms an expansion side compression chamber with a rear surface of the displacer piston that forms an expansion chamber with the front surface of the displacer piston and is connected to a rod; and an expansion side that allows the displacer piston to reciprocate A displacer unit provided with a driving means;
A compressor provided with a power piston, a power cylinder that forms a compression-side compression chamber with the power piston, and compression-side drive means that enables the power piston to reciprocate;
One end of a first pulse tube, a first heat exchanger that absorbs or dissipates the working gas, a regenerative heat exchanger that alternately repeats the working gas, heat absorption, and exhaust heat, and a first heat exchanger that dissipates or absorbs heat. Two heat exchangers, and one end of the second pulse tube, and a heat exchange operation unit that sequentially communicates,
The expansion chamber communicates with either the other end side of the first pulse tube or the other end side of the second pulse tube,
The compression side compression chamber and the expansion side compression chamber communicate with the other end side of the second pulse tube when the expansion chamber communicates with the other end side of the first pulse tube, and When the chamber communicates with the other end side of the second pulse tube, the chamber communicates with the other end side of the first pulse tube. The regenerative heat exchanger includes a heat exchanger between a high temperature side end of the regenerative heat exchanger and a low temperature side end lower in temperature than the end. The pulse tube type heat storage engine described in 1. A flow path switching means for opening and closing a flow path is provided in the compression chamber and the expansion chamber,
When the compression chamber is communicated with the other end side of the second pulse tube, the expansion chamber is communicated with the other end side of the first pulse tube.
The expansion chamber is communicated with the other end side of the second pulse tube when the compression chamber communicates with the other end side of the first pulse tube. Item 3. A pulse tube heat storage engine according to any one of Items 2 to 3.

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