JP2010071481A - Thermal compressor and air conditioning device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To compress a refrigerant by thermal energy and to use it without being restricted by electric power use in a cooling power peak in summer or a remote island, and at a low cost and having high thermal efficiency, and its thermal type To provide a cooling / heating device that uses a compressor, has a simple structure, is inexpensive, and has high thermal efficiency.
A thermal compressor 1 compresses a refrigerant with heat, and a displacer piston 78 and a pulse tube 71 reciprocated by a drive unit 30 expand to a front surface 78a side and a back surface 78b of the displacer piston 78, respectively. The chamber 75 and the compression chamber 41 are formed, and the compression chamber 41, the heat accumulator 50, the heat absorber 60, and the expansion chamber 75 are sequentially communicated, and the discharge valve 46 and the suction valve 44 are provided in the compression chamber 41. The preheat combustor 10 is disposed in the heat absorber 60.
[Selection] Figure 1

Description

  The present invention relates to a thermal compressor that forms a pulse tube type heat storage cycle in which a pulse tube and a heat accumulator are arranged and compresses a refrigerant with heat energy, and to a cooling and heating apparatus using the thermal compressor.

  As a pulse tube type heat storage engine used in a conventional air conditioner, a vibration generator, a heat accumulator, a cold head, and a pulse tube are connected in series sequentially, and the reciprocating motion and pressure fluctuation of the working fluid flowing into these are connected. In a pulse tube type heat storage engine that generates a low temperature or power by giving a phase difference between the two, a displacer system that connects them between the connection portion between the vibration generator and the heat storage device and the high temperature end of the pulse tube is provided. The displacer system includes a displacer working space into which working fluid flows in and out, a displacer section that constitutes at least a part of the displacer working space and is reciprocally movable with respect to the displacer working space; The displacer working space is isolated from the displacer working space in the reciprocating direction of the displacer working space. Disclosed is a pulse tube type heat storage engine having a buffer space, and a displacer that extends in the reciprocating direction of the displacer part, and that has one end attached to the displacer part and at least a part of which is disposed in the buffer space. (For example, refer to Patent Document 1).

In addition, a cooling / heating device using a compressor (for example, a scroll compressor) that compresses refrigerant with an electric motor is known. An air-conditioning apparatus using a compressor (for example, a scroll compressor) that compresses a refrigerant with an engine is known.
JP 2006-275352 A

  However, according to Patent Document 1, when cooling or heating a room with room temperature or heat generated in a pulse tube type heat storage engine, the heat or heat is transferred to the room. Alternatively, a compressor for circulating the refrigerant that transfers the heat to the air conditioning circuit and an air conditioning circuit are required. For this reason, there exists a problem which an air conditioning apparatus becomes complicated. Moreover, since a compressor is newly provided, there exists a problem that the cost of an air conditioning apparatus becomes high.

  In addition, the known air-conditioning compressor driven by an electric motor has a problem of power shortage at the peak of cooling power in summer and a problem of restriction of power use on a remote island where power is difficult to obtain. Further, when the size is increased, there is a problem that the efficiency is lower than that of an air-conditioning compressor driven by an engine.

  In addition, the known air-conditioning compressor driven by the engine does not cause a problem of power shortage at the cooling power peak in summer, but has a problem of increasing the cost of the compressor including the engine.

  The present invention has been made in view of the above-mentioned problems, and by compressing the refrigerant with thermal energy, it can be used without restrictions on the use of electric power at the peak of cooling power in the summer or on remote islands, and the cost is low. It is an object of the present invention to provide a thermal compressor with high thermal efficiency, and an air conditioning apparatus that uses the thermal compressor, has a simple configuration, is inexpensive, and has high thermal efficiency.

In order to solve the above-mentioned problem, the invention described in claim 1 includes a displacer piston that reciprocates by reciprocating means, a pulse tube that forms an expansion chamber on the front side of the displacer piston,
A regenerator is installed between the high temperature end of the regenerator and the expansion chamber, and the reciprocating flow is between the high temperature end of the regenerator and the expansion chamber. A heat absorber that absorbs heat by the flowing refrigerant, a suction valve that is provided on the compression chamber side and sucks the refrigerant, and a discharge valve that is provided on the compression chamber side and discharges the compressed refrigerant.

  According to a second aspect of the present invention, the compression chamber includes compression ratio increasing means that communicates with the compression chamber and increases the compression ratio of the refrigerant.

  The drive unit may include a housing that forms a buffer chamber isolated from the compression chamber, a rod that is connected to the back surface of the displacer piston, partially extends to the buffer chamber, and reciprocates. Elastic means for applying a spring force to the rod provided in the buffer chamber.

  According to a fourth aspect of the present invention, there is provided an air conditioning apparatus comprising: an air conditioning circuit that cools and heats a room; and a thermal compressor that supplies compressed refrigerant to the air conditioning circuit. A displacer piston that reciprocates by means, a pulse tube that forms an expansion chamber on the front surface side of the displacer piston, and a suction tube that is provided on the compression chamber side formed on the back surface of the displacer piston by the pulse tube and the displacer piston. A valve, a discharge valve provided on the compression chamber side for discharging the compressed refrigerant, a regenerator that exchanges heat with a refrigerant whose low temperature end communicates with the compression chamber and reciprocates, and a high temperature end of the regenerator and an expansion chamber And a heat absorber that absorbs heat from the reciprocating refrigerant, and the air conditioning circuit is connected to the indoor heat exchanger and expands the refrigerant by being connected to the indoor heat exchanger. And an outdoor heat exchanger connected to the expansion means, a discharge port through which the refrigerant is discharged and a suction port through which the refrigerant is sucked, which is provided in the thermal compressor, and the discharge port is used as an indoor heat source during heating. A refrigerant flow path switching valve that communicates with the exchanger and communicates the suction port with the outdoor heat exchanger, communicates the discharge port with the outdoor heat exchanger during cooling, and communicates the suction port with the indoor heat exchanger; Is provided.

  In the invention according to claim 5, the air conditioning circuit includes an exhaust heat recovery heat exchanger that heats the refrigerant discharged from the thermal compressor by the exhaust gas discharged from the exhaust port of the thermal compressor. The refrigerant side of the heat recovery heat exchanger is provided between the discharge port and the refrigerant flow switching valve, and the exhaust gas side of the exhaust heat recovery heat exchanger is connected to the exhaust port to control the flow of exhaust gas Is provided.

  In the invention according to claim 1, in the thermal compressor, the expansion chamber and the compression chamber are respectively formed on the front side and the back side of the displacer piston that reciprocates by the driving means. The expansion stroke, the suction stroke, the compression stroke, and the discharge stroke are sequentially performed to form one cycle.

  That is, in the expansion stroke, the displacer piston moves in the direction of arrow A (FIG. 1), that is, in the direction of the expansion chamber while the suction valve and the discharge valve are kept closed. By this movement, the refrigerant (for example, carbon dioxide) having a high temperature (for example, approximately 550 ° C.) in the expansion chamber sequentially passes through the heat absorber and the heat accumulator and is cooled by the heat storage material element, and the pressure gradually decreases. It becomes a low temperature (for example, approximately 60 ° C.) and moves to the compression chamber. Then, the pressure in the compression chamber reaches a predetermined low pressure, and the expansion stroke ends.

  In the suction stroke, when the pressure in the compression chamber reaches a predetermined low pressure, the pressure difference between the pressure in the suction passage and the compression chamber and the spring load of the suction valve act on the suction valve, and the suction valve is automatically activated. Opened, low-pressure refrigerant is sucked into the compression chamber from the cooling / heating circuit, and the mass of the refrigerant in the compression chamber increases. Then, when the suction valve is automatically closed, the suction stroke ends.

  The compression stroke is performed after the suction stroke is completed, and the displacer piston moves in the direction of arrow B (FIG. 1), that is, toward the compression chamber while the suction valve and the discharge valve are kept closed, and the refrigerant in the compression chamber is sequentially stored in the heat accumulator. Move to heat absorber, expansion chamber. By this movement, the low-temperature refrigerant in the compression chamber is sequentially heated by high-temperature heat such as combustion passing through the heat accumulator and the heat absorber, and the heat input to the heat absorber, and the pressure gradually increases. The temperature becomes high (for example, approximately 550 ° C.) and moves to the expansion chamber. Then, the pressure in the expansion chamber reaches a predetermined high pressure, and the compression stroke ends.

  In the discharge stroke, the compression chamber reaches a predetermined high pressure, the differential pressure between the pressure in the compression chamber and the pressure in the valve chamber in which the discharge valve is installed, and the spring load of the discharge valve act on the discharge valve. It is automatically opened and the high-pressure refrigerant in the compression chamber is discharged and supplied to the cooling / heating circuit. Then, the discharge valve is automatically closed and the discharge stroke is completed.

  As described above, since the refrigerant is compressed by high-temperature heat energy such as combustion and supplied to the cooling and heating circuit, it is possible to provide a thermal compressor that can be used without being restricted by the use of electric power at the peak of cooling power in summer or on remote islands. .

  In addition, although the engine heat pump compressor of the prior art requires an engine, the thermal compressor of the present invention compresses the refrigerant with high-temperature thermal energy such as combustion, so the cost is lower than that of the engine heat pump compressor. Become.

  The thermal compressor includes a pulse tube and a heat accumulator. In the pulse tube, a gas piston that reciprocates in the pulse tube is formed by the displacer piston. The gas piston functions as a heat insulating material, and suppresses conduction heat loss that enters the displacer piston from the high-temperature expansion chamber. In addition, the pulse tube and the regenerator container are made of a material with low thermal conductivity such as stainless steel and have a thin wall and a long pipe shape in the heat conduction direction. Therefore, the compression tube is transferred from the expansion chamber to the pulse tube and the regenerator container. Conductive heat loss entering the side is suppressed. Furthermore, since at least air of the air and fuel introduced by the preheater is preheated by the exhaust heat of the exhaust gas combusted in the combustor, the combustion temperature rises and the heat energy of combustion is efficiently absorbed by the heat absorber. The As described above, a thermal compressor having high thermal efficiency can be provided.

  In the invention according to claim 2, the compression ratio increasing means is provided in at least one of the compression chamber or between the compression chamber and the low temperature end of the regenerator. As a result, when the displacer piston reciprocates, the refrigerant amount of the compression ratio increasing means changes in substantially the same phase as the refrigerant amount in the compression chamber. This does not change the scavenging volume of the expansion chamber, and is equivalent to an increase in the scavenging volume of the compression chamber. Therefore, the amount of refrigerant moving from the compression chamber to the expansion chamber increases, and the compression ratio increases. As a result, in the thermal compressor, the discharge pressure and the discharge flow rate are increased, and the thermal efficiency is improved.

  In the invention according to claim 3, spring force is applied to the rod by elastic means such as a flexible bearing provided in the housing. As a result, the spring of the elastic means (for example, a pair of flexible bearings) and the magnetic spring (considering the magnetic spring if there is a linear motor) and a gas spring based on the pressure of the refrigerant, the combined spring, the displacer piston, the rod, and the mover The total mass forms a spring / mass resonance vibration system.

  The displacer piston has a force F = F1-F2 which is a difference between a force F1 based on the pressure acting on the front surface of the displacer piston and a force F2 based on the pressure acting on the back surface, and a pressure acting on the end surface of the rod on the buffer chamber side. Based on the force F3, the driving force F4 by the driving means (the spring force due to the bending of the pair of flexible bearings, and the driving force if a linear motor is provided), and the total mass of the displacer piston, rod and mover Inertial force F5 acts. The displacer piston increases in amplitude and reciprocates at the resonance frequency of the spring (synthetic spring) / mass (total mass) or near the resonance frequency, and the scavenging volume of the compression chamber and the expansion chamber increases. As a result, the amount of refrigerant moving between the compression chamber and the expansion chamber increases, and the compression ratio increases. As a result, in the thermal compressor, the discharge pressure and the discharge flow rate are increased, and the thermal efficiency is improved.

  In the invention according to claim 4, the air conditioning apparatus combines a thermal compressor and an air conditioning circuit, compresses a refrigerant (for example, carbon dioxide) with the thermal compressor, and supplies the compressed air to the air conditioning circuit. Cooling or heating is performed, and the low-pressure refrigerant returns to the thermal compressor.

  In a thermal compressor, when both the suction valve and the discharge valve are closed and the displacer piston moves in the direction of the compression chamber and the volume of the compression chamber decreases, the refrigerant (for example, carbon dioxide) in the compression chamber becomes a heat accumulator and heat absorber. To move to the expansion chamber. In this process, the refrigerant is heated and heated by the heat accumulator, further absorbs high-temperature heat such as combustion through a heat absorber, and is heated and pressurized to reach a predetermined high pressure. Since the discharge valve is an automatic valve, it is automatically opened. Then, the refrigerant in the compression chamber is discharged and supplied to the air conditioning circuit until the discharge valve is automatically closed. Next, when the displacer piston moves toward the expansion chamber with the suction valve and the discharge valve closed, the expansion chamber refrigerant moves to the compression chamber through the heat accumulator and the heat absorber. . In this process, the refrigerant is cooled by the heat accumulator, the temperature is lowered, the pressure is gradually reduced, and a predetermined low pressure is reached. Since the suction valve is an automatic valve, it is automatically opened, and low-pressure refrigerant is sucked into the compression chamber from the cooling / heating circuit until the suction valve is automatically closed.

  The cooling / heating circuit includes a refrigerant flow switching means, an indoor heat exchanger, a JT valve, and an outdoor heat exchanger. The refrigerant flow switching means switches the flow path of the refrigerant between the heating time and the cooling time. And cool. That is, during heating, the refrigerant channel switching means sets the heating channel, the refrigerant compressed by the thermal compressor is introduced into the indoor heat exchanger, and the room is heated by the compression heat of the refrigerant generated by the compression. During cooling, the refrigerant flow switching means sets the cooling flow path, introduces the compressed refrigerant into the outdoor heat exchanger, dissipates the heat of compression, and then liquefies part of the refrigerant with an expansion means such as a JT valve. To. This mist is passed through the indoor heat exchanger, and the room is cooled by the cold heat of the mist (the latent heat and sensible heat of the refrigerant). As a result, the cooling / heating device of the present invention is configured by combining a thermal compressor and a cooling / heating circuit as compared with a conventional engine heat pump or a cooling / heating device combining a pulse tube type heat storage engine, a compressor, and a cooling / heating circuit. Therefore, the configuration is simple and the cost can be reduced.

  In addition, since the thermal compressor compresses the refrigerant with thermal energy, it can provide a cooling / heating device that can be used without any restrictions on the use of electric power at the peak of cooling power in summer or on remote islands.

  The thermal compressor includes a pulse tube and a heat accumulator. In the pulse tube, a gas piston that reciprocates in the pulse tube is formed by the displacer piston. The gas piston functions as a heat insulating material, and suppresses conduction heat loss that enters the displacer piston from the high-temperature expansion chamber.

  In addition, the pulse tube and the regenerator container are made of a material with low thermal conductivity such as stainless steel and have a thin wall and a long pipe shape in the heat conduction direction. Therefore, the compression tube is transferred from the expansion chamber to the pulse tube and the regenerator container. Conductive heat loss entering the side is suppressed. Furthermore, since at least air of the air and fuel introduced by the preheater is preheated by the exhaust heat of the exhaust gas combusted in the combustor, the combustion temperature rises and the heat energy of combustion is efficiently absorbed by the heat absorber. The As a result, the thermal efficiency of the thermal compressor is improved.

  As described above, the air-conditioning apparatus performs air-conditioning using a thermal compressor having high thermal efficiency, so that the thermal efficiency is increased.

  In the invention according to claim 5, the cooling and heating circuit is provided with an exhaust heat recovery heat exchanger, and heats the refrigerant discharged from the thermal compressor with the exhaust gas of the thermal compressor during heating. The exhaust heat of the exhaust gas absorbed by the refrigerant and the compression heat generated by the thermal compressor are used as heating heat through an indoor heat exchanger. As a result, since the thermal energy of the exhaust gas of the thermal compressor is effectively used without exhausting wastefully, the thermal efficiency of the air conditioner increases.

(First embodiment)
FIG. 1 is an explanatory diagram according to the first embodiment of the present invention. As shown in FIG. 1, a thermal compressor 1 using a pulse tube 71 is composed of a preheating combustor 10 and a compressor body 20, and carbon dioxide is used as a refrigerant.

  The preheating combustor 10 includes a preheater 14 and a combustor 15. The preheater 14 is provided to preheat the air introduced into the preheater 14 and the fuel with the exhaust heat of the exhaust gas burned in the combustor 15. The preheater 14 exhausts the exhaust gas through the fuel inlet 11, the air inlet 12, and the exhaust gas. An exhaust port 13 is provided. The combustor 15 mixes and heats preheated air and fuel, and heats the heat absorber 60 of the compressor body 20. Thereby, the carbon dioxide gas reciprocatingly flowing through the heat absorber 60 is heated. The fuel may be introduced into the combustor 15 without being preheated by the preheater 14 and mixed with preheated air.

  The compressor body 20 includes a compression unit 40, a heat accumulator 50, a heat absorber 60, and an expansion unit 70.

  The inflating unit 70 includes a pulse tube 71, a displacer piston 78, a head 77, and a distributor 74. The pulse tube 71 and the displacer piston 78 form an expansion chamber 75 in which the refrigerant expands on the front surface 78 a side of the displacer piston 78. A gas piston 72 is formed between the front surface 78 a of the displacer piston 78 and the expansion chamber 75. The low temperature end 72 b of the gas piston 72 is adjacent to the front surface 78 a of the displacer piston 78, and the high temperature end 72 a of the gas piston 72 is adjacent to the expansion chamber 75. One end of the rod 36 is connected to the back surface 78 b of the displacer piston 78.

  The gas piston 72 is formed of a cylindrical carbon dioxide gas having the same diameter as the inner periphery of the pulse tube 71, has a constant mass, and forms an elastic piston whose volume changes in accordance with the pressure fluctuation of the carbon dioxide gas. That is, the gas piston 72 reciprocates between the front surface 78 a of the displacer piston 78 and the expansion chamber 75 in the pulse tube 71 while changing the volume in accordance with the reciprocation of the displacer piston 78. As the gas piston 72 reciprocates, the volume of the expansion chamber 75 changes.

  The drive unit 30 (reciprocating means) is a linear drive type, and includes a linear motor 33, a housing 31 provided with the linear motor 33, a pair of flexible bearings 32 (elastic means), and a part extending to the buffer chamber 37. And a reciprocating rod 36. The open end of the housing 31 is airtightly fixed to the lower surface of the valve box 42 in the figure, and a buffer chamber 37 is formed by the housing 31 and the lower surface of the valve box 42.

  The linear motor 33 is provided to assist the reciprocating movement of the displacer piston 78, and is disposed on the outer peripheral surface of the housing 31. The linear motor 33 includes a coil 34 a wound with a copper wire, and the buffer chamber 37 includes a stator 34. And a mover 35 provided with a permanent magnet 35a.

  The rod 36 connected to the back surface 78b of the displacer 78 passes through and is fixed to the center of the mover 35. The inner peripheral side of the thin flexible bearing 32 made of spring steel having a slide is fixed to the rods 36 near both ends of the mover 35, and the outer peripheral side of the flexible bearing 32 is fixed to the inner peripheral surface side of the housing 31. Thereby, the mover 35 is supported so as to be able to reciprocate with a small gap without contacting the inner peripheral surface of the housing 31. Similarly, the displacer 78 is supported so as to be able to reciprocate with a minute gap without contacting the inner peripheral surface of the pulse tube 71. The flexible bearing 32 applies a spring force to the rod 36 by the spring of the flexible bearing 32 as the rod 36 reciprocates.

  The compression unit 40 includes a displacer piston 78 connected to the rod 36, a pulse tube 71, and a valve box 42 fixed to the low temperature end of the pulse tube 71, and is configured on the back surface 78 b of the displacer piston 78. The compression chamber 41 of the compression unit 40 is formed by being surrounded by the low temperature side inner peripheral surface of the pulse tube 71, the upper surface of the valve box 42, the back surface 78 b of the displacer 78, and the rod 36. The volume changes due to reciprocation.

  In the valve box 42, a valve chamber 43b in which a suction valve 44 is disposed between the suction flow path 43a and the flow path 43c, and a discharge valve 46 is disposed between the flow path 45c and the discharge flow path 45a. And a valve chamber 45b. The valve chamber 43b communicates with the compression chamber 41 via the flow path 43c, and the valve chamber 45b communicates with the compression chamber 41 via the flow path 45c when the discharge valve 46 is open. When the suction valve 44 is open, the suction flow path 43a communicates with the valve chamber 43b. The suction port 43d of the suction channel 43a is connected to a refrigerant outlet 107 (FIG. 8) of the cooling / heating circuit 101 described later, and the discharge port 45d of the discharge channel 45a is connected to the refrigerant inlet 102 (FIG. 8) of the cooling / heating circuit 101. Connected.

  A through hole is provided in the center of the valve box 42, and the rod 36 reciprocates with a minute gap. The minute gap has a function of a clearance seal that seals carbon dioxide gas between the compression chamber 41 and the buffer chamber 37, whereby the buffer chamber 37 is isolated from the compression chamber 41.

  The suction valve 44 is a reed valve made of a thin spring steel plate, and the suction valve 44 resists the spring force of the suction valve 44 when the differential pressure between the compression chamber 41 and the suction passage 43a having the same pressure as the valve chamber 43b reaches a predetermined value. Is an automatic valve that opens. The discharge valve 46 is a reed valve made of a thin spring steel plate. When the pressure difference between the valve chamber 45b and the flow path 45c and the compression chamber 41 having the same pressure reaches a predetermined value, the discharge valve 46 resists the spring force of the discharge valve 46. It is an automatic valve that is opened.

  A large number of flow paths 53 are provided at the low temperature end of the pulse tube 71, and the flow paths 53 communicate with a flow path 52 disposed on the low temperature end 50 b side of the heat accumulator 50. As a result, the compression chamber 41 communicates with the low temperature end 50 b of the heat accumulator 50 via the flow path 53 and the flow path 52.

  The heat accumulator 50 is filled with a large number of heat storage material elements 51 such as a stainless steel wire mesh, and the heat storage material element 51 exchanges heat with the carbon dioxide gas reciprocatingly flowing through the heat storage device 50.

  The container of the pulse tube 71 and the heat accumulator 50 is made of a material having a low thermal conductivity such as stainless steel, and has a thin wall shape and a long pipe shape in the conduction direction.

  The heat absorber 60 is connected to the high temperature end 50 a of the heat accumulator 50, includes a large number of flow paths (not shown), and is provided in the combustion chamber 15. Carbon dioxide gas reciprocates inside the flow path, the outside of the flow path is heated with combustion gas, and the carbon dioxide gas is heated with combustion gas through the flow path wall. The heat absorber 60 communicates with the expansion chamber 75 through a flow path 76 formed by the head 77 and a distributor 74.

  Further, the inner peripheral surface of the heat accumulator 50 and the inner peripheral surface of the heat absorber 60 circumscribe the outer peripheral surface of the pulse tube 71. A pulse tube may be formed by the inner peripheral surface of the heat accumulator 50 and the inner peripheral surface of the heat absorber 60.

  The flexible bearing 32 may be replaced with an elastic means such as a conical coil spring (elastic means), and the spring force of the conical coil spring may be applied to the rod 36. In this case, the displacer piston 78 is capable of reciprocating on the inner peripheral surface of the pulse tube 71 by coating the outer peripheral surface with a resin sliding material and making the outer diameter slightly smaller than the inner diameter of the pulse tube 71, and carbonic acid. Gas can be sealed.

  The refrigerant of the thermal compressor 1 is carbon dioxide, but other gases, for example, HC natural refrigerants such as isobutane and butane may be used.

  The suction valve 44 and the discharge valve 46 are provided in the valve box 42 and the valve box 42 is attached to the compression chamber 41. However, the suction valve 44 and the discharge valve 46 may be provided directly in the compression chamber 41. Alternatively, it may be provided in the flow path 52 that communicates with the compression chamber 41 through the flow path 53.

  FIG. 2 shows the volume of the expansion chamber 75 (solid line in the figure) and the pressure of the compression chamber 41 (thick solid line in the figure) with respect to the phase of the displacer piston 78 in one cycle. The operation and effect of the thermal compressor 1 will be described with reference to FIGS. 1 and 2.

  Fuel and air are introduced into the preheater 14 from the fuel inlet 11 and the air inlet 12, respectively. Air and fuel are preheated by the exhaust gas flowing into the preheater 14 from the combustion chamber 15 and mixed in the combustion chamber 14 to burn the fuel. The carbon dioxide gas reciprocatingly flowing through the heat absorber 60 is heated to a high temperature (for example, approximately 600 ° C.) by the combustion gas through the heat absorber 60, and one cycle of the thermal compressor 1 described below is formed.

  As shown in FIG. 2, the thermal compressor 1 is sequentially subjected to four strokes: an expansion stroke (NK interval), a suction stroke (KL interval), a compression stroke (LM interval), and a discharge stroke (MN interval). One cycle of the pulse tube type heat storage cycle is formed.

  The expansion stroke is performed in the interval NK. When the displacer piston 78 moves in the direction of arrow A (FIG. 1), that is, in the direction of the expansion chamber 75 while the suction valve 44 and the discharge valve 46 are kept closed, the gas pist 72 is also in the direction of arrow A. Move to. By this movement, the volume of the expansion chamber 75 is reduced, and the carbon dioxide gas in the expansion chamber 75 sequentially flows into the heat absorber 60 and the heat accumulator 50 and is cooled by the heat storage material element 51, which is higher than the ambient air temperature and the expansion chamber. The temperature becomes lower than 75 (for example, approximately 60 ° C.) and flows into the compression chamber 41. Since the carbon dioxide gas at a high temperature (for example, approximately 550 ° C.) in the expansion chamber 75 becomes a temperature lower than that of the expansion chamber 75 and moves to the compression chamber 41 whose volume is increasing, the pressure of the carbon dioxide gas decreases the volume of the expansion chamber 75. Accordingly, the pressure gradually decreases, and the pressure in the compression chamber 41 reaches a predetermined low pressure.

  The suction stroke is performed in a section of KL, the pressure of the compression chamber 41 reaches a predetermined low pressure, and the force ((Pi) acting on the suction valve 44 based on the pressure difference between the pressure Pi of the suction passage 43a and Pc of the compression chamber 41. When -Pc) × Ai, Ai is the pressure receiving area of the suction valve 44) is larger than the spring force of the suction valve 44, the suction valve 44 is automatically opened. Then, low-pressure carbon dioxide gas is sucked into the compression chamber 41 from an air conditioning circuit 101 (FIG. 8) described later. That is, the carbon dioxide gas flows into the compression chamber 41 whose volume is increasing through the suction passage 43a, and the mass of the carbon dioxide gas in the compression chamber 41 increases while the pressure in the compression chamber 41 is maintained at a constant value. When the force ((Pi−Pc) × Ai) acting on the suction valve 44 based on the differential pressure between the pressure Pi of the suction flow path 43a and Pc of the compression chamber 41 becomes smaller than the spring force of the suction valve 44, the suction valve 44 is automatically closed and the inhalation stroke is completed.

  The compression stroke is performed in the section MN after the suction stroke is completed, and the displacer piston 78 moves in the direction of arrow B (FIG. 1), that is, in the direction of the compression chamber 41 while the suction valve 44 and the discharge valve 46 are kept closed. Then, the carbon dioxide gas in the compression chamber 41 whose volume is reduced moves sequentially to the heat accumulator 50, the heat absorber 60, and the expansion chamber 75. Due to this movement, the carbon dioxide gas in the compression chamber 41 is heated by the heat storage material element 51 and further heated by the combustion gas in the heat absorber 60 to become a high temperature (for example, approximately 550 ° C.) and moves to the expansion chamber 75. The gas pressure gradually increases as the volume of the compression chamber 41 decreases, and reaches a predetermined high pressure.

  The discharge stroke is made in the section MN, the pressure in the compression chamber 41 reaches a predetermined high pressure, and the acting force ((Pc−) on the discharge valve 46 based on the pressure difference between the pressure Pc in the compression chamber 41 and the pressure Po in the valve chamber 45b. (Po) × Ao, Ao is the pressure receiving area of the discharge valve 46) becomes larger than the spring force of the discharge valve 46, the discharge valve 46 is automatically opened, and the carbon dioxide gas in the compression chamber 41 passes through the flow path 45a from the compression chamber 41. Discharged through. The compressed carbon dioxide gas is supplied to the cooling / heating circuit 101 (FIG. 8).

  Based on the pressure difference between the pressure Pc in the compression chamber 41 and the pressure Po in the valve chamber 45b, the acting force ((Pc−Po) × Ao) on the discharge valve 46 becomes smaller than the spring force of the discharge valve 46, and the discharge valve 46 is automatically turned on. When closed, the discharge stroke ends, and the process proceeds to the expansion stroke of the next cycle again.

  As described above, the thermal compressor 1 compresses the refrigerant with heat energy and supplies the compressed refrigerant to the cooling / heating circuit 100 to be described later. Machine 1 can be provided.

  Further, the gas piston 72 moves in substantially the same manner as the movement of the displacer piston 78 while changing the volume in accordance with the pressure fluctuation with a constant gas mass. Since the thermal conductivity of the carbon dioxide gas is significantly lower than that of the solid material, the gas piston 72 functions as a heat insulating material, and suppresses conduction loss heat that enters the displacer piston 78 from the expansion chamber 75.

  In addition, since the regenerator element 51 is configured by laminating a large number of metal meshes such as stainless steel, the contact heat resistance between the regenerator elements 51 by the lamination is significantly larger than the thermal resistance of the solid material, and the regenerator 50 Conductive heat loss entering the regenerator cold end 50b from the high temperature end 50a is suppressed.

  The container of the pulse tube 71 and the heat accumulator 50 is made of a material having a low thermal conductivity such as stainless steel and has a thin wall shape and a long pipe shape in the heat conduction direction. Conduction loss heat that enters the compression chamber 41 side through the container is suppressed.

  Furthermore, since the air and fuel introduced by the preheater 14 are preheated by the exhaust heat of the exhaust gas combusted in the combustor 15, the fuel temperature becomes high, and the heat energy from the combustion is carbonated via the heat absorber 60. Heat is absorbed efficiently by the gas.

  As described above, it is possible to provide the thermal compressor 1 that has low conduction loss heat, efficiently uses thermal energy by combustion, and has high thermal efficiency.

  The displacer piston 78 includes a difference force F = F1-F2 between the force F1 based on the pressure acting on the front surface 78a of the displacer piston 78 and the force F2 based on the pressure acting on the back surface 78b, and the rod 36 on the buffer chamber 37 side. A force F3 based on the pressure acting on the end face, a driving force F4 by the driving unit 30 (driving means) (a spring force by the bending of the pair of flexible bearings 32 and a driving force of the linear motor 33), the displacer piston 78 and the rod 36. The inertial force F5 based on the total mass with the mover 35 acts and reciprocates. The displacer piston 78 forms a vibration system having a resonance frequency with a synthetic spring obtained by synthesizing a spring of the pair of flexible bearings 32, a magnetic spring of the linear motor 33, and a gas spring based on the pressure of carbon dioxide gas, and the total mass described above. To do. By operating the thermal compressor 1 at this resonance frequency or a nearby frequency, the amplitude of the reciprocating motion of the displacer piston 78 increases even if the driving force of the linear motor 33 is small. Therefore, the amount of refrigerant moving between the compression chamber 41 and the expansion chamber 75 due to the reciprocating movement of the displacer piston 78 increases, so the compression ratio increases. As a result, in the thermal compressor 1, the discharge pressure and the discharge flow rate are increased, and the thermal efficiency is improved.

  Although the linear motor 33 uses electric power, since the diameter of the rod 36 is significantly smaller than the diameter of the displacer piston 78, the aforementioned force F is also minute, and is driven at the resonance frequency or a nearby frequency. The required power of the linear motor 33 is very small. Therefore, it does not become a cause of the occurrence of peak cooling power in summer. As will be described later, if the flexible bearing 32 is provided, the linear motor 33 may not be provided.

(Second Embodiment)
FIG. 3 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 parts having the same shapes as those in FIG.

  As shown in FIG. 3, the thermal compressor 2 is provided with a compression ratio increasing means 80 in the compression chamber 41. Other configurations are the same as those in FIG. That is, the thermal compressor 2 includes the preheating combustor 10, the compressor body 20, and the compression ratio increasing means 80.

  The compression ratio increasing means 80 includes a cylinder 81, a piston 82, a rod 83 connected to the back surface 82 b of the piston 82, a pair of flexible bearings 84 that support the piston 82 through the rod 83, and a pipe 87. The

  The working chamber 85 on the front surface 82 a side of the piston 82 communicates with the compression chamber 41 through a pipe 87, a flow path 52, and a flow path 53. The outer peripheral side and the inner peripheral side of the pair of flexible bearings 84 are fixed to the inner peripheral surface side of the cylinder 81 and the rod 83, respectively, so that the piston 82 has a minute gap with respect to the inner peripheral surface of the cylinder 81. It is supported so that it can reciprocate. The minute gap performs a clearance sealing function for sealing carbon dioxide between the working chamber 85 and the buffer chamber 86 on the back surface 82b side.

  The piston 82 is a combined spring of the total mass of the piston 82 and the rod 83 and a spring of a pair of flexible bearings 84 and a gas spring based on the pressure of carbon dioxide gas, and has a resonance frequency substantially the same as the resonance frequency of the displacer 78. Form a system. As a result, the piston 82 reciprocates at the resonance frequency of the displacer 78 or a nearby operating frequency, and the volume fluctuation of the working chamber 85 is substantially in phase with the volume fluctuation of the compression chamber 41. This is equivalent to an increase in the scavenging volume of the compression chamber 41 without changing the scavenging volume of the expansion chamber 75. That is, the amount of refrigerant that moves from the compression chamber 41 and the working chamber 85 of the compression ratio increasing means 80 to the expansion chamber 75 increases due to the provision of the compression ratio increasing means 80, so the compression ratio increases. As a result, the thermal compressor 2 can increase the compression ratio with respect to the same amount of heat energy supplied to the heat absorber 60 of the thermal compressor 1 of FIG. The thermal compressor 2 having a higher discharge pressure and discharge amount and high thermal efficiency can be provided.

(Third embodiment)
FIG. 4 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 parts having the same shapes as those in FIG.

  As shown in FIG. 4, the thermal compressor 3 is provided with a compression ratio increasing means 90 in the compression chamber 41. Other configurations are the same as those in FIG. That is, the thermal compressor 3 includes the preheating combustor 10, the compressor body 20, and the compression ratio increasing means 90.

  The compression ratio increasing means 90 includes a buffer tank 91 and an inert pipe 92 having an elongated pipe whose one end communicates with the buffer tank 91. The other end of the inertance tube 92 communicates with the compression chamber 41 through the flow path 52 and the flow path 53.

  By adjusting the inner diameter and length of the inertance tube 92 and the volume of the buffer tank 91, the compression ratio increases with the mass of carbon dioxide gas in the inertance tube 92 and the gas spring of carbon dioxide gas in the buffer tank 91. The means 90 forms a vibration system having a resonance frequency substantially the same as the resonance frequency of the displacer 78. Thus, when the displacer piston 78 reciprocates at an operating frequency near the resonance frequency, the carbon dioxide in the inertance tube 92 reciprocates at the same frequency, and the total amount of carbon dioxide in the inertance tube 92 and the buffer 91 is compressed. It changes in substantially the same phase as the amount of carbon dioxide in the chamber 41. This is equivalent to an increase in the scavenging volume of the compression chamber 41 without changing the scavenging volume of the expansion chamber 75. That is, the amount of carbon dioxide gas moving from the compression chamber 41 and the compression ratio increasing means 80 to the expansion chamber 75 is increased by providing the compression ratio increasing means 90, and the compression ratio is increased. As a result, the thermal compressor 3 can increase the compression ratio with respect to the same amount of heat energy supplied to the heat absorber 60 of the thermal compressor 1 of FIG. The thermal compressor 3 having a higher discharge pressure and discharge amount and high thermal efficiency can be provided.

  In addition, the compression ratio increasing means 90 of the thermal compressor 3 is simpler in configuration than the compression ratio increasing means 80 of the thermal compressor 2, although the compression ratio is lower, and the thermal compressor 3 is lower in cost.

(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 parts having the same shapes as those in FIG.

  As shown in FIG. 5, the thermal compressor 4 includes a preheating combustor 10 and a compressor body 24. And the drive part 130 (reciprocating means) of the compressor main body 24 is comprised by removing the linear motor 33 arrange | positioned at the drive part 30 of the thermal compressor 1 of FIG. That is, the drive unit 130 includes a housing 131 that forms a buffer chamber 137, a pair of flexible bearings 32, and a rod 136 that is connected to the back surface 78 b of the displacer piston 78.

  The outer peripheral side and the inner peripheral side of the flexible bearing 32 are fixed to the inner peripheral surface side of the housing 131 and the outer peripheral surface of the rod 136, respectively. Accordingly, the displacer piston 78 can reciprocate between the rod 136 and the through hole of the valve box 42 and between the outer peripheral surface of the displacer piston 78 and the inner peripheral surface of the pulse tube 71 with a small gap. . The minute gap described above fulfills a clearance seal function that prevents the carbon dioxide gas from flowing in and out of the compression chamber 41. Then, the compression chamber 41 and the buffer chamber 137 are dynamically separated by the clearance seal (the average pressures of the compression chamber 41 and the buffer chamber 137 are equal and the pressure fluctuations are different).

  Similar to the first embodiment of FIG. 1, the displacer piston 78 of FIG. 5 is a composite spring that combines the total mass of the displacer piston 78 and the rod 136, the spring of the pair of flexible bearings 32, and a gas spring based on the pressure of the refrigerant. Thus, a vibration system having a resonance frequency is formed.

  The vibration system of FIG. 5 is different from the vibration system of FIG. 1 in that the driving force F4 of the vibration system of FIG. 5 does not include the driving force of the linear motor 33, and the composite spring is the spring force of the pair of flexible bearings 32 and the gas spring. And that the total mass of the vibration system in FIG. 5 does not include the mass of the mover 35.

  The thermal compressor 4 is activated by heating the heat absorber 60 with combustion gas and applying a slight shock (for example, tapping the thermal compressor 4) to the thermal compressor 4 for a moment. It reciprocates at the above resonance frequency.

  As described above, the displacer piston 78 reciprocates at the resonance frequency even if the thermal compressor 4 is not provided with the linear motor 33. As a result, the configuration of the drive unit 130 is simple, small, and low-cost, and accordingly, the configuration is simple, and the compact and low-cost thermal compressor 4 can be provided.

  Moreover, since a drive motor is unnecessary, the thermal compressor 4 can be operated only with thermal energy. Other configurations and effects are the same as those of the thermal compressor 1.

(Fifth embodiment)
FIG. 6 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 parts having the same shapes as those in FIG.

  As shown in FIG. 6, the thermal compressor 5 includes a preheating combustor 10 and a compressor body 25. And the shape of the drive part 150 and the valve box 142 of the compressor main body 25 differs from the shape of the drive part 30 and the valve box 42 of the thermal compressor 1 of FIG. That is, the linear motor 153 of the drive unit 150 (reciprocating means) is smaller than the linear motor 33 (FIG. 1), and the movable element 155 is provided in the compression chamber 141. The compression chamber 141 is surrounded by a compression chamber 141 a formed by the pulse tube 71, the back surface 78 b of the displacer piston 78, the upper surface of the valve box 142, and the rod 156, the housing 151, the mover 155, and the rod 156. And the compression chamber 141b formed as a result.

  The linear motor 153 includes a stator 154 provided on the outer peripheral surface of the housing 151 and having a coil 154a, and a mover 155 having a permanent magnet 155a. A convex rod 156 passes through and is fixed to the center of the mover 155, and one end of the rod 156 is connected to the back surface 78 b of the displacer piston 78. The other end side of the rod 156 is fixed to the inner diameter side of the flexible bearing 152 (elastic means), and the outer diameter side of the flexible bearing 152 is fixed to the inner peripheral surface side of the housing 151. The displacer piston 78 is supported by the flexible bearing 152 so as to be able to reciprocate with a small gap with respect to the inner peripheral surface of the pulse tube 71, and this minute gap serves as a clearance seal.

  A gap is secured between the inner peripheral surface of the housing 151, the outer peripheral surface of the rod 156, and the outer peripheral surface of the mover 155 so that carbon dioxide gas can move between the compression chamber 141a and the compression chamber 141b without pressure loss.

  Further, when the mover 155 is disposed in the compression chamber 141, the diameter of the through hole that penetrates the rod 156 of the valve box 142 increases. For this reason, the shapes of the valve chamber 143b and the valve chamber 145b of the valve box 142 are different from the shapes of the valve chamber 43b and the valve chamber 45b (FIG. 1) of the thermal compressor 1, and accordingly, the shape of the valve box 142 is heated. The shape of the valve box 42 (FIG. 1) of the compressor 1 is different.

  Thus, the drive unit 150 is smaller and lighter than the drive unit 30 of the thermal compressor 1 of FIG.

  Further, the volume scavenged by the reciprocation of the rod 36 in FIG. 1 and the scavenging volume of the compression chamber 141 are larger than the compression chamber 41 in FIG. 1 by the volume scavenged by the reciprocation of the rod 36 (FIG. 1). Also, the compression ratio increases. Other configurations and other effects are the same as those of the thermal compressor 1 of FIG.

  The mover 155 of the linear motor 153 is connected to the back surface 78b of the displacer piston 78 through the rod 156, but may be directly fixed to the back surface 78b of the displacer piston 78.

(Sixth embodiment)
FIG. 7 is an explanatory diagram according to the sixth embodiment of the present invention. The same reference numerals as those in FIG. 1 denote the same parts and the parts having the same shapes as those in FIG.

  As shown in FIG. 7, the thermal compressor 6 includes a compressor body 26, a heater 16, and a heat insulating material 17. The difference from the thermal compressor 1 of FIG. 1 is that the preheating type combustor 10 of the thermal compressor 1 is replaced with a heater 16. That is, the heater 16 is installed in the heat absorber 60, and the heat insulating material 17 is applied around the heater 16. Other configurations are the same as those in FIG.

  The heater 16 is supplied with electric power from the fuel cell 18, and the carbon dioxide gas reciprocatingly flowing through the heat absorber 60 is heated by the heater 16. Thereby, the thermal compressor 6 can be used for, for example, a fuel cell vehicle or an air conditioner such as a remote island where it is difficult to secure electric power.

  Moreover, since it heat-insulates with the heat insulation material 17 favorably, the heat | fever which generate | occur | produces with the heater 16 is used for the heating of the heat absorber 60, without being thrown away around. As a result, a highly efficient thermal compressor 6 can be provided.

  Other operations are the same as those of the thermal compressor 1. The other effects are the same as those of the thermal compressor 1 except for the effects caused by the preheater 14 of the thermal compressor 1.

  The heat source of the thermal compressor may be in any form other than combustion heat or fuel cell, such as solar heat, geothermal heat, exhaust heat from the combustion furnace, and the like. In this case, the preheating combustor 10 or the heater 16 is replaced with a device suitable for the form of thermal energy.

(First adaptive embodiment)
FIG. 8 is an explanatory diagram according to the first adaptive embodiment of the present invention. As shown in FIG. 8, the air conditioning apparatus 100 is configured by connecting an air conditioning circuit 101 to the thermal compressor 1 in FIG. 1, and the thermal compressor 1 schematically illustrates the thermal compressor 1 in FIG. 1. Shown in That is, the discharge port 45d, the suction port 43d, and the exhaust port 13 of the thermal compressor 1 are connected to the refrigerant inlet 102, the refrigerant outlet 107, and the exhaust gas inlet 109 of the air conditioning circuit 101, respectively.

  The air conditioning circuit 101 includes an exhaust heat recovery heat exchanger 103, a refrigerant flow switching valve 120 connected to the outflow side of the refrigerant flow path 103 a of the exhaust heat recovery heat exchanger 103, and an exhaust gas of the exhaust heat recovery heat exchanger 103. The exhaust gas flow path switching valve 111 (control valve) connected to the flow path 103b, the indoor heat exchanger 104, the JT valve 105 (expansion means), and the outdoor heat exchanger 106 are configured.

  The exhaust heat recovery heat exchanger 103 includes a refrigerant channel 103a through which carbon dioxide gas flows and an exhaust gas channel 103b through which exhaust gas flows, and the carbon dioxide gas flowing through the refrigerant channel 103a is heated by the exhaust gas flowing through the exhaust gas channel 103b. .

  The refrigerant flow path switching valve 120 includes a three-way valve 121 and a three-way valve 122, and switches a flow path through which carbon dioxide gas flows corresponding to cooling and heating. The exhaust gas flow path through which the exhaust gas flows is switched by the exhaust gas flow path switching valve 111 in conjunction with the switching of the refrigerant flow path switching valve 120. That is, at the time of heating, the discharge port 45d includes the refrigerant inlet 102, the refrigerant flow path 103a, the port 121a and the port 121b of the three-way valve 121, the indoor heat exchanger 104, the JT valve 105, the outdoor heat exchanger 106, and the three-way valve. The port 122b, the port 122a, the refrigerant outlet 107, and the suction port 43d are sequentially communicated. In this state, the exhaust port 13 of the thermal compressor 1 is sequentially communicated with the exhaust gas inlet 109, the port 111a, the port 111b, and the flow channel 103b of the exhaust gas flow switching valve 111.

  During cooling, the discharge port 45d is connected to the refrigerant inlet 102, the refrigerant channel 103a, the port 121a, the port 121c, the channel 124, the outdoor heat exchanger 106, the JT valve 105, the indoor heat exchanger 104, the flow of the three-way valve 121. The passage 123, the port 122c of the three-way valve 122, the port 122a, the refrigerant outlet 107, and the suction port 43d are sequentially communicated. In this state, the exhaust port 13 is sequentially opened to the exhaust gas inlet 109, the port 111a of the exhaust gas flow path switching valve 111, the port 111c, and the atmosphere.

  Next, operations and effects of heating and cooling of the air conditioning apparatus 100 will be described. That is, during heating, high-pressure carbon dioxide gas heated by compression heat (for example, approximately 60 ° C.) from the compression chamber 41 (FIG. 1) of the thermal compressor 1 passes through the discharge valve 46 and the flow path 45a (FIG. 1). And discharged from the discharge port 45d. And sequentially, the flow path 103a of the exhaust heat recovery heat exchanger 103, the port 121a of the three-way valve 121, the port 121b, the indoor heat exchanger 104, the JT valve 105, the outdoor heat exchanger 106, the port 122b of the three-way valve 122, It returns to the compression chamber 41 through the port 121a, the suction port 43d of the thermal compressor 1, and the suction valve 44 (FIG. 1).

  The carbon dioxide gas flowing through the refrigerant flow path 103a of the exhaust heat recovery heat exchanger 103 is heated by the exhaust gas having a relatively high temperature (for example, approximately 150 ° C.) from the thermal compressor 1, and is further heated (for example, 80 ° C.). And flows into the indoor heat exchanger 104.

  In the indoor heat exchanger 104, the room is heated with the compression heat of the carbon dioxide gas generated when compressed by the thermal compressor 1 and the heat absorbed by the carbon dioxide gas from the exhaust gas through the exhaust heat recovery heat exchanger 103.

  In the JT valve, the flow of the high-pressure carbon dioxide gas that has flowed out of the indoor heat exchanger 104 and finished indoor heating is throttled, and is approximately enthalpy-expanded to a pressure close to the suction pressure, and a part of the carbon dioxide gas is liquefied to become mist. .

  In the outdoor heat exchanger 106, the mist (for example, approximately −10 ° C.) flowing out from the JT valve 105 is heated to raise the temperature to substantially atmospheric temperature, and the heated carbon dioxide gas passes through the suction valve 44 and is compressed. Inhaled.

  During cooling, carbon dioxide gas compressed from the compression chamber 41 of the thermal compressor 1 and warmed by the compression heat is discharged through the discharge valve 46 and the discharge port 45d. Then, the flow path 103a of the exhaust heat recovery heat exchanger 103, the port 121a of the three-way valve 121, the port 121c, the outdoor heat exchanger 106, the JT valve 105, the indoor heat exchanger 104, and the port 122c of the three-way valve 122 are sequentially provided. , Return to the compression chamber 41 through the port 122a, the suction passage 43a of the thermal compressor 1, and the suction valve 44. In this case, the exhaust gas flowing out from the exhaust port 13 of the thermal compressor 1 passes through the ports 111a and 111c of the exhaust gas flow path switching valve 111 and is released to the atmosphere. Thereby, the carbon dioxide gas is not heated by the exhaust gas in the exhaust heat recovery heat exchanger 103.

  The outdoor heat exchanger 106 dissipates the compression heat of the carbon dioxide gas, and lowers the temperature of the carbon dioxide gas to a substantially atmospheric temperature. The JT valve 105 squeezes the carbon dioxide gas that has passed through the external heat exchanger 106 and finishes radiating heat, and expands the carbon dioxide gas to a mist by liquefying part of the carbon dioxide gas to a pressure close to the suction pressure. The mist flows into the internal heat exchanger 104 and cools the room with the cold heat of the mist, that is, the latent heat and sensible heat of carbon dioxide, via the indoor heat exchanger 104.

  As described above, the cooling / heating apparatus 100 of the present invention is configured by combining the thermal compressor 1 and the cooling / heating circuit 101 as compared with the cooling / heating apparatus combining the engine heat pump or the pulse tube type heat storage engine of the prior art, the compressor, and the cooling / heating circuit. Therefore, the air conditioning apparatus 100 with a simple configuration and low cost can be provided.

  In addition, since the thermal compressor 1 compresses carbon dioxide gas by heat energy, it is possible to provide a cooling / heating device 100 that can be used without being restricted by the use of power at the cooling power peak in the summer or at a remote island.

  In addition, the cooling / heating circuit 101 is provided with an exhaust heat recovery heat exchanger 103, which heats the carbon dioxide gas discharged from the thermal compressor 1 with the exhaust gas of the thermal compressor 1 during heating, and interposes the indoor heat exchanger 104. To effectively use heat for indoor heating. In addition, the carbon dioxide gas after heating is partially liquefied by the JT valve, becomes mist, flows into the outdoor heat exchanger 106, and absorbs heat there. And the cold heat of mist can be utilized for an ice machine etc., for example. Furthermore, the compression heat radiated by the outdoor heat exchanger 106 during cooling can be used for, for example, a water heater.

  Further, as described in the first embodiment, the gas piston 72, the cool storage element 51, the tube wall of the pulse tube 71, and the container of the heat storage 50 are transmitted from the heat absorber 60 or the expansion chamber 71 to the compression chamber 41 side. The heat conduction loss is suppressed by the same reason as in the first embodiment. Further, at least air of the air and fuel introduced by the preheater 14 is preheated by the exhaust heat of the exhaust gas combusted by the combustor 15, so that the combustion temperature rises and the heat energy of the combustion is efficiently absorbed by the heat absorber 60. It absorbs heat well.

  As described above, the air-conditioning apparatus 100 with high thermal efficiency can be provided.

  In the first adaptive embodiment, the air conditioning apparatus 100 uses the thermal compressor 1, but the thermal compressor 2, the thermal compressor 3, the thermal compressor 4, the thermal compressor 5, and the thermal compression. Any of the machines 6 may be used.

  Moreover, although the exhaust gas flow path switching valve 111 of this adaptive embodiment is a three-way valve, the exhaust gas discharged from the exhaust port 13 is other than the exhaust heat recovery heat exchanger 103 and the exhaust gas is other than the exhaust heat recovery heat exchanger 103. For example, when used in a water heater or the like, the exhaust gas flow path switching valve 111 may be an on-off valve (control valve) that stops the flow.

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

  As shown in FIG. 9, in the air conditioning apparatus 200, the one-stage compression thermal compressor 1 of the air-conditioning apparatus 100 in FIG. 8 is replaced with a two-stage compression thermal compressor 7. That is, the thermal compressor 7 includes a first-stage thermal compressor 7a and a second-stage thermal compressor 7b having a scavenging volume smaller than that of the thermal compressor 7a. The structure of the thermal compressors 7a and 7b is the same as that of the thermal compressor 1 of FIG.

  The discharge port 45d of the first-stage thermal compressor 7a is connected to the suction port 43f of the second-stage thermal compressor 7b. The discharge port 45f of the thermal compressor 7b is connected to the refrigerant inlet 102 of the cooling / heating circuit 101, and the refrigerant outlet 107 of the cooling / heating circuit 101 is connected to the inlet 43d of the first-stage thermal compressor 7a.

  The flow path from the exhaust port 13 of the first-stage thermal compressor 7a and the flow path from the exhaust port 13f of the second-stage thermal compressor 7b merge to form an exhaust gas inlet 109, an exhaust gas flow path switching valve. 111 ports 111a are sequentially connected. The port 111b of the exhaust gas flow path switching valve 111 is connected to the inflow side of the flow path 103b of the exhaust heat recovery heat exchanger 103, and the port 111c is opened to the atmosphere.

  The exhaust gases from the first-stage thermal compressor 7a and the second-stage thermal compressor 7b join together and flow into the port 111a of the exhaust gas flow path switching valve 111. During heating, the exhaust heat recovery heat passes through the port 111b. The carbon dioxide flowing into the flow path 103b of the exchanger 103 and flowing through the flow path 103a is heated. During cooling, the combined exhaust gas is discharged from the port 111a through the port 111c to the atmosphere.

  Carbon dioxide gas sucked from the suction port 43d of the first-stage thermal compressor 7a is compressed to a predetermined pressure and discharged from the discharge port 45d. The discharged carbon dioxide gas is sucked from the suction port 43f of the second-stage thermal compressor 7b, is compressed to a higher predetermined pressure, passes through the second-stage discharge valve (not shown), and is discharged to the discharge port 45f. It is discharged from. Thereby, since the compression ratio of the carbon dioxide gas discharged from the thermal compressor 7 is larger than that of the thermal compressor 1 of FIG. 1, the cooling / heating capacity of the cooling / heating system 200 is increased.

  Other configurations, operations, and effects are the same as those of the air conditioning apparatus 100 of FIG.

  The structure of the thermal compressors 7a and 7b of the thermal compressor 7 is the same as that of the compressor body 1, but the thermal compressor 2, the thermal compressor 3, the thermal compressor 4, and the heat The structure of either the compressor 5 or the thermal compressor 6 may be the same.

(Third adaptive embodiment)
FIG. 10 is an explanatory diagram according to the third adaptive embodiment of the present invention. The same reference numerals as those in FIG. 8 denote the same parts and the same parts as those in FIG.

  As shown in FIG. 10, in the air conditioning circuit 301 of the air conditioning apparatus 300, the JT valve 105 of the air conditioning circuit 101 in FIG. 8 is replaced with an expander 110 (expansion means). That is, the high-pressure carbon dioxide gas that has flowed into the expander 110 expands substantially isentropically to a pressure in the vicinity of the suction pressure and performs expansion work outside, and flows out as low-temperature carbon dioxide gas or carbon dioxide mist. .

  Cooling and heating are performed by switching the flow path by the refrigerant flow path switching valve 120 in the same manner as the cooling and heating circuit 101 of FIG. The difference between the operation of the cooling / heating circuit 301 and the operation of the cooling / heating circuit 101 is that the expansion mode of the carbon dioxide gas is different. That is, the expander 110 of the cooling / heating circuit 301 expands substantially isentropically and performs expansion work to the outside, but the JT valve of the cooling / heating circuit 101 expands approximately equal enthalpy and does not perform expansion work to the outside. Therefore, the air-conditioning apparatus 300 improves thermal efficiency by collecting the expansion work of the expander 110 as power or electric power.

  In the case where the expander 110 is a piston reciprocating type, the expander 110 has a built-in flow path switching valve (not shown) that switches between an inflow path and an outflow path for carbon dioxide during heating and cooling. Yes.

  Other configurations, operations, and effects are the same as those of the air conditioning apparatus 100 of FIG.

  In the first adaptive embodiment, the air-conditioning apparatus 300 uses the thermal compressor 1, but the thermal compressor 2, the thermal compressor 3, the thermal compressor 4, the thermal compressor 5, and the thermal compression. Any of the machines 6 may be used.

(Seventh embodiment)
FIG. 11 is an explanatory diagram according to the seventh embodiment of the present invention. The same reference numerals as those in FIG. 1 denote the same parts and the parts having the same shapes as those in FIG. As shown in FIG. 11, the thermal compressor 8 is a modified embodiment of the thermal compressor 1 of FIG. That is, in the thermal compressor 8, the configuration of the drive unit 30 and the valve box 42 is the same as that of the thermal compressor 1, and the other configuration is different from that of the thermal compressor 1.

  The low temperature side expansion section 160 includes a displacer piston 162 connected to the rod 36, a cylinder 163, and a valve box 42 (including a suction valve 44 and a discharge valve 46) fixed to the lower end surface of the cylinder 163. The expansion chamber 161 on the low temperature side of the expansion section 160 is formed by being surrounded by the inner peripheral surface of the cylinder 163, the upper surface of the valve box 42, the back surface 162 b of the displacer 162, and the rod 36. A compression chamber 164 is formed surrounded by the front surface 162 a of the displacer 162 and the inner peripheral surface of the cylinder 163. Due to the reciprocating motion of the displacer piston 162, the volumes of the expansion chamber 161 and the compression chamber 164 on the low temperature side change in opposite phases.

  The high temperature side expansion section 170 includes a high temperature side of the pulse tube 171 and a high temperature side of the gas pist 172 formed in the pulse tube 171. The expansion chamber 173 on the high temperature side is formed by being surrounded by the pulse tube 171, the high temperature end 172 a of the gas pist 172, and the heat absorber 166. The working chamber 178 is formed by being surrounded by the pulse tube 171, the low temperature end 172 b of the gas pist 172, and the distributor 174.

  The compression chamber 164 communicates with the expansion chamber 173 on the high temperature end 171a side of the pulse tube 171 via the flow path 175, the heat accumulator 165, the flow path 176, and the heat absorber 166 sequentially. The working chamber 178 communicates with the low temperature side expansion chamber 161 via the flow path 177. In the heat accumulator 165, the end on the flow path 175 side is the low temperature end 165b, and the end on the flow path 176 side is the high temperature end 165a.

  The heater 191 is provided in the heat absorber 166. A heat insulating material 192 is applied around the high temperature side of the heat accumulator 165, the flow path 176, the heat absorber 166, and the high temperature side of the pulse tube 171.

  When the displacer piston 162 is moved upward by the drive unit 30, the carbon dioxide gas in the compression chamber 164 is heated by the heat accumulator 165 and the heat absorber 166, and is heated and pressurized to flow into the expansion chamber 173 on the high temperature side. The piston 172 is moved downward. Due to the downward movement of the gas piston 172, the carbon dioxide gas whose pressure is increased in the working chamber 174 flows into the expansion chamber 161 on the low temperature side, and is discharged from the discharge port 45d through the discharge valve 46. When the displacer piston 162 is moved downward by the drive unit 30, the carbon dioxide gas in the low temperature side expansion chamber 161 flows into the working chamber 178, and moves the gas piston 172 upward. Then, the carbon dioxide gas in the high-temperature side expansion chamber 173 passes through the heat absorber 166 and the heat accumulator 165, and the temperature is lowered and lowered by the heat accumulator 165 and flows into the compression chamber 164. Further, the carbon dioxide gas flows from the suction port 43d through the suction valve 44 to the low temperature side expansion chamber 161 where the pressure is low. In this way, one cycle of carbon dioxide compression by the thermal compressor 8 is formed.

  As described above, the thermal compressor 8 has the same effects as the thermal compressor 1 of FIG. 1 and the thermal compressor 6 of FIG.

(Eighth embodiment)
FIG. 12 is an explanatory diagram according to the eighth embodiment of the present invention. The same reference numerals as those in FIG. 11 denote parts having the same shape as those in FIG. As shown in FIG. 12, in the thermal compressor 9, the linear motor 33 of the thermal compressor 8 in FIG. 11 is disposed across the displacer piston 182 and the cylinder 185. Accordingly, the shape of the valve box 47 is different from that of the valve box 42 of FIG. 11, and there is no hole through which the rod 36 (FIG. 11) passes.

  The low temperature side expansion section 180 includes a displacer piston 182, a cylinder 185, and a valve box 47 (including a suction valve 44 and a discharge valve 46) fixed to the lower end surface of the cylinder 185. The displacer piston 182 includes a piston body 182a, a pair of rods 182b provided at both ends of the piston body 182a, a pair of flexible bearings 182f fixed to the rod 182b, and a permanent magnet 182c provided on the outer peripheral side of the piston body 182a. Is provided. The pair of flexible bearings 182f are fixed to the inner peripheral surface of the cylinder 185. As a result, the displacer piston 182 can reciprocate with a small gap with respect to the cylinder 185. A stator 183 provided with a coil 183a facing the permanent magnet 182c is provided on the outer peripheral surface of the cylinder 185. The displacer piston 182 also serves as a mover and constitutes a linear motor 184 with the stator 183. The drive unit 190 includes a cylinder 185, a displacer piston 182, and a stator 183.

  The expansion chamber 181 on the low temperature side is formed surrounded by the cylinder 185 and the back surface 182e of the displacer piston 182. The compression chamber 186 is formed surrounded by the cylinder 185 and the front surface 182d of the displacer piston 182. Further, the flexible bearing 182f includes a slit, and carbon dioxide gas can pass through the slit.

  The other configuration is the same as that of the seventh embodiment in FIG. 11, and the operation is also the same as that of the seventh embodiment. The thermal compressor 8 is smaller than the thermal compressor 8 of FIG. 11 because the linear motor 184 is disposed in the compression unit. Other effects are the same as those of the seventh embodiment of FIG.

It is explanatory drawing concerning 1st Embodiment of this invention. It is a figure which shows the volume of the expansion chamber and the pressure of a compression chamber of the thermal compressor of FIG. 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 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 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 7th Embodiment of this invention. It is explanatory drawing concerning 8th Embodiment of this invention.

Explanation of symbols

1, 2, 3, 4, 5, 6, 7, 8, 9 Thermal compressor 13, 13f Exhaust 30, 130, 150 Drive unit (reciprocating means)
31, 131 Housing 32, 152 Flexible bearing (elastic means)
36, 136 Rod 37, 137 Buffer chamber 41, 141 Compression chamber 43d Suction port 45d, 45f Discharge port 44 Suction valve 46 Discharge valve 50 Heat accumulator 50a High temperature end 50b Low temperature end 60 Heat absorber 71 Pulse tube 75 Expansion chamber 78 Displacer piston 78a Front surface 78b Rear surface 80, 90 Compression ratio increasing means 100, 200, 300 Air conditioning system 101, 301 Air conditioning system 103 Waste heat recovery heat exchanger 104 Indoor heat exchanger 105 JT valve (expansion means)
106 outdoor heat exchanger 110 expander (expansion means)
111 Exhaust gas flow path switching valve (control valve)
120 Refrigerant flow path switching valve

Claims (5)

A displacer piston that reciprocates by reciprocating means;
A pulse tube that forms an expansion chamber on the front side of the displacer piston;
A regenerator that exchanges heat with the refrigerant that reciprocally flows in a compression chamber formed at a back surface of the displacer piston at a low-temperature end by the pulse tube and the displacer piston;
A heat absorber that absorbs heat from the refrigerant that is reciprocated between the high temperature end of the heat accumulator and the expansion chamber;
A suction valve provided on the compression chamber side for sucking the refrigerant;
A discharge valve provided on the compression chamber side for discharging the compressed refrigerant;
A thermal compressor characterized by comprising: The thermal compressor according to claim 1, wherein the compression chamber includes a compression ratio increasing unit that communicates with the compression chamber and increases a compression ratio of the refrigerant. The drive unit is provided in the buffer chamber, a housing that forms a buffer chamber isolated from the compression chamber, a rod that is connected to the back surface of the displacer piston, partially extends to the buffer chamber, and reciprocates. The thermal compressor according to claim 1, further comprising: an elastic unit that applies a spring force to the rod. An air conditioning apparatus comprising: an air conditioning circuit that heats and cools the room; and a thermal compressor that supplies compressed refrigerant to the air conditioning circuit,
The thermal compressor includes a displacer piston that reciprocates by reciprocating means;
A pulse tube that forms an expansion chamber on the front side of the displacer piston;
A suction valve for sucking the refrigerant, provided on the compression chamber side formed on the back surface of the displacer piston by the pulse tube and the displacer piston;
A discharge valve provided on the compression chamber side for discharging the compressed refrigerant;
A heat accumulator that exchanges heat with the refrigerant whose low temperature end communicates with the compression chamber and reciprocates;
A heat absorber that absorbs heat from the refrigerant that is disposed between the high temperature end of the heat accumulator and the expansion chamber and reciprocally flows;
The air conditioning circuit includes an indoor heat exchanger that heats and cools the room;
Expansion means connected to the indoor heat exchanger for expanding the refrigerant;
An outdoor heat exchanger connected to the expansion means;
Connected to a discharge port through which the refrigerant is discharged and a suction port through which the refrigerant is sucked, which is provided in the thermal compressor, communicates the discharge port with the indoor heat exchanger during heating and connects the suction port with the suction port. A refrigerant flow path switching valve that communicates with an outdoor heat exchanger, communicates the discharge port with the outdoor heat exchanger during cooling, and communicates the suction port with the indoor heat exchanger. A featured air conditioning unit. The air conditioning circuit includes an exhaust heat recovery heat exchanger that heats the refrigerant discharged from the thermal compressor by exhaust gas discharged from an exhaust port of the thermal compressor,
The refrigerant side of the exhaust heat recovery heat exchanger is provided between the discharge port and the refrigerant flow switching valve,
The air conditioning apparatus according to claim 4, wherein a control valve connected to the exhaust port and controlling the flow of the exhaust gas is provided on the exhaust gas side of the exhaust heat recovery heat exchanger.

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