JP5372473B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner including a compressor driven by an engine.

Conventionally, an air conditioner in which a compressor is driven by an engine is known. In this type of air conditioner, a plate heat exchanger for exchanging heat between engine cooling water for cooling the engine and refrigerant sucked into the compressor is provided in the refrigerant circuit, and the compressor is used during heating operation. There is one that improves the operating efficiency during heating operation by heating the sucked refrigerant with engine cooling water (see, for example, Patent Document 1).
JP 2005-226873 A

However, in the conventional technology, engine exhaust heat can be used for air conditioning operation via engine cooling water only during heating operation. During cooling operation, the heat energy of the engine exhaust gas is released to the outside as it is. There was a problem that had to be done.
Accordingly, an object of the present invention is to provide an air conditioner that solves the above-described problems of the prior art and that can effectively use the thermal energy discharged from the engine regardless of the cooling operation or the heating operation.

In order to solve the above problems, the present invention provides a refrigerant circuit formed by connecting a compressor driven by an engine, a four-way valve, and an outdoor heat exchanger, and cools the engine by sending engine cooling water to the engine by a cooling water pump. An air conditioner including an engine cooling water circuit that operates, and a Stirling engine that is driven by using the exhaust gas of the engine as a high-temperature heat source, and an auxiliary that is connected to the output shaft of the Stirling engine and operates with the compressor. A cooling water circuit used as a low-temperature heat source of the Stirling engine, the cooling water circuit being used as a low-temperature heat source of the Stirling engine. with the circuit provided in another system, was passed through the low-temperature cooling water than the engine cooling water in the cooling water circuit this The features.
According to this configuration, the Stirling engine can drive the auxiliary compressor using the thermal energy of the exhaust gas of the engine. Therefore, the compressor is driven at a low rotational speed as the auxiliary compressor operates. Can be made. As a result, regardless of the cooling operation or the heating operation, the fuel consumption of the engine for driving the compressor can be suppressed, and the energy consumption can be reduced. Moreover, it is good also as a structure provided with the cooling water circuit utilized as a low-temperature heat source of the said Stirling engine, and providing this cooling water circuit in the system | strain different from the engine cooling water circuit which cools the said engine. According to this configuration, since the cooling water can be supplied to the Stirling engine regardless of the temperature of the engine cooling water flowing through the engine cooling water circuit, a large temperature difference between the high temperature heat source and the low temperature heat source of the Stirling engine is taken. be able to. As a result, a large amount of energy output from the Stirling engine can be secured, and energy consumption can be reduced accordingly.

  In this configuration, the auxiliary compressor may be provided on the refrigerant circuit in parallel with the compressor. According to this configuration, since the compressor can be driven at a low rotational speed while maintaining the amount of refrigerant circulating in the refrigerant circuit, the fuel for the engine for driving the compressor without reducing the air conditioning capability Consumption can be suppressed, and energy consumption can be reduced.

  Moreover, it is good also as a structure provided with the cooling water circuit utilized as a low-temperature heat source of the said Stirling engine, and providing this cooling water circuit in the system | strain different from the engine cooling water circuit which cools the said engine. According to this configuration, since the cooling water can be supplied to the Stirling engine regardless of the temperature of the engine cooling water flowing through the engine cooling water circuit, a large temperature difference between the high temperature heat source and the low temperature heat source of the Stirling engine is taken. be able to. As a result, a large amount of energy output from the Stirling engine can be secured, and energy consumption can be reduced accordingly.

Further, connected to an output shaft of the front Symbol Stirling engine, it may be provided with a power generator that generates power supplied to the load device of the blower fan such of the cooling water pump or the outdoor heat exchanger.
According to this configuration, the generator can be driven by the Stirling engine using the thermal energy of the exhaust gas from the engine. Therefore, a load device such as a cooling water pump or a blower fan can be installed using the electric power generated by the generator. I can drive. Thereby, regardless of the cooling operation or the heating operation, the amount of power supplied to the air conditioner can be reduced, and the energy consumption can be reduced.

  According to the present invention, the auxiliary compressor can be driven by the Stirling engine using the thermal energy of the exhaust gas of the engine. Therefore, the compressor is driven at a low rotational speed as the auxiliary compressor operates. Can be made. As a result, regardless of the cooling operation or the heating operation, the fuel consumption of the engine for driving the compressor can be suppressed, and the energy consumption can be reduced.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a diagram showing a configuration of a refrigerant circuit of a gas heat pump (GHP) type air conditioner 10 according to the present embodiment.
The air conditioner 10 includes an outdoor unit 11 and a plurality of (for example, five) indoor units 12A to 12E, and includes an outdoor refrigerant pipe 13 of the outdoor unit 11 and indoor refrigerant pipes 14A to 14E of the indoor units 12A to 12E. Are connected. In FIG. 1, the refrigerant circuit of the air conditioner 10 is denoted by reference numeral 1, and the cooling water circuit that cools the gas engine 30 is denoted by reference numeral 43.

  The outdoor unit 11 is installed outside, a compressor 15 is disposed in the outdoor refrigerant pipe 13, an accumulator 16 is provided on the suction side of the compressor 15, and a check valve 71 is provided on the discharge side. 17 and a four-way valve 18 are disposed, respectively, and an outdoor heat exchanger 19, an outdoor expansion valve 20, and a dry core 21 are sequentially disposed on the four-way valve 18 side. An outdoor fan (blower fan) 22 that blows air toward the outdoor heat exchanger 19 is disposed adjacent to the outdoor heat exchanger 19. The compressor 15 is connected to the gas engine (engine) 30 via a V-belt 30A that is stretched between a pulley (not shown) on the compressor 15 side and a pulley (not shown) on the gas engine 30 side. And is driven by the gas engine 30.

The oil separator 17 is provided with an oil return pipe 23 for returning the oil separated by the oil separator 17 to the compressor 15, and the oil return pipe 23 is connected to the inlet of the accumulator 16.
The refrigerant high pressure side (discharge side of the compressor 15) and the refrigerant low pressure side (in the illustrated example, the inlet of the accumulator 16) are connected via a bypass valve 24. The outdoor refrigerant pipe 13 is provided with closing valves 25A and 25B. Further, the outdoor refrigerant pipe 13 is provided with a liquid pipe 26 for appropriately supplying the liquid refrigerant flowing through the outdoor refrigerant pipe 13 to the front side of the accumulator 16, and the liquid pipe 26 is provided with a liquid valve 26A.

  On the other hand, the indoor units 12A to 12E are installed in each room, and are disposed in the vicinity of the indoor heat exchangers 27A to 27E and the indoor heat exchangers 27A to 27E respectively disposed in the indoor refrigerant pipes 14A to 14E. Indoor expansion valves 28A to 28E are provided. Moreover, indoor fan 29A-29E which ventilates to these indoor heat exchangers 27A-27E is arrange | positioned adjacent to indoor heat exchanger 27A-27E.

The outdoor unit 11 includes a control device (not shown) that controls the entire air conditioner 10, and the control device switches the four-way valve 18 to perform a cooling operation or a heating operation. In other words, when the four-way valve 18 is switched to the cooling side, the refrigerant flows as indicated by solid arrows, the outdoor heat exchanger 19 functions as a condenser, and the indoor heat exchangers 27A to 27E function as an evaporator to enter a cooling operation state. Each of the indoor heat exchangers 27A to 27E cools the room. Further, when the four-way valve 18 is switched to the heating side, the refrigerant flows as shown by broken arrows, the indoor heat exchangers 27A to 27E function as a condenser, and the outdoor heat exchanger 19 functions as an evaporator to enter a heating operation state. The indoor heat exchangers 27A to 27E heat the room.
Further, during the cooling operation, the respective valve openings of the indoor expansion valves 28A to 28E are controlled according to the air conditioning load. During the heating operation, the opening degrees of the outdoor expansion valve 20 and the indoor expansion valves 28A to 28E are controlled according to the air conditioning load.

On the other hand, an air-fuel mixture of fuel and air is supplied from an engine fuel supply device 31 to the combustion chamber of the gas engine 30 that drives the compressor 15. In this engine fuel supply device 31, a fuel cutoff valve 33, a zero governor 34, a fuel adjustment valve 35, and a throttle 36 are sequentially disposed in a fuel supply pipe 32, and the end of the fuel supply pipe 32 on the throttle 36 side is a gas engine. It is configured to be connected to 30 combustion chambers.
The fuel cut-off valve 33 constitutes a closed type fuel cut-off valve mechanism, and the fuel cut-off valve 33 is fully closed or fully opened, and the cut-off and communication without leakage of the fuel gas are performed alternatively.
The zero governor 34 is caused by fluctuations in the primary pressure a among the primary fuel gas pressure (primary pressure a) and the secondary fuel gas pressure (secondary pressure b) before and after the zero governor 34 in the fuel supply pipe 32. Also, the secondary pressure b is adjusted to a constant predetermined pressure to stabilize the operation of the gas engine 30.

The fuel adjustment valve 35 optimally adjusts the air-fuel ratio of the air-fuel mixture generated by introducing air from the upstream side of the throttle 36. An air supply pipe 37 for sucking air from outside the engine unit is connected to the upstream side of the throttle 36. An air filter 38 is disposed at the suction port of the air supply pipe 37.
An engine oil supply device 39 is connected to the gas engine 30. The engine oil supply device 39 is provided with a constant oil pan 41 having an oil level switch 41A and an oil supply pump 42 provided in an oil supply pipe 40, and appropriately supplies engine oil to the gas engine 30.

Further, the gas engine 30 is cooled by engine cooling water circulating in the engine cooling water circuit 43. The engine coolant circuit 43 is branched by a first coolant path 43A for circulating coolant between the radiator 49 and the gas engine 30, and a wax three-way valve 45 provided in the first coolant path 43A. A path for returning the cooling water to the gas engine 30 without passing through the radiator 49, that is, a second cooling water path 43B for circulating the cooling water between the wax three-way valve 45 and the gas engine 30, and a first cooling water path 43A. And a third cooling water path 43 </ b> C for branching the cooling water between the plate heat exchanger 48 and the gas engine 30.
The engine cooling water circuit 43 is provided with a reserve tank 50. When the cooling water in the engine cooling water circuit 43 decreases due to water leakage or the like, the internal pressure of the cooling water piping is reduced to the cooling water. Has been adjusted to automatically replenish by gravity.

  The wax three-way valve 45 is for quickly warming up the gas engine 30. A cooling water outlet of the gas engine 30 is connected to the inlet 45A of the wax three-way valve 45 via a cooling water pipe, and a circulation pump 46 and the gas engine 30 are attached to one outlet 45B of the wax three-way valve 45. A Stirling engine 70 is sequentially connected. The circulation pump 46 discharges engine cooling water during operation and circulates the engine cooling water in the engine cooling water circuit 43.

  The cooling water three-way valve 47 adjusts the flow rate that guides the high-temperature engine cooling water that has flowed in through the wax three-way valve 45 to either the radiator 49 or the plate heat exchanger 48 or both by changing the diversion ratio. It is a three-way valve of the formula. The other outlet 45C of the wax three-way valve 45 is connected to the inlet 47A of the cooling water three-way valve 47 via a cooling water pipe, and the one outlet 47B of the cooling water three-way valve 47 is connected to the cooling water pipe via a cooling water pipe. A plate heat exchanger 48 is connected, and a radiator 49 is connected to the other outlet 47C of the cooling water three-way valve 47 via a cooling water pipe. The cooling water three-way valve 47 is driven by a motor (not shown), and this motor is controlled by a control device (not shown).

The radiator 49 cools the engine coolant, and is disposed adjacent to the outdoor fan 22 so that the blown air of the outdoor fan 22 is supplied. The engine cooling water cooled by the radiator 49 is returned to the gas engine 30 by the circulation pump 46 via the Stirling engine 70 to cool the gas engine 30.
The plate heat exchanger 48 exchanges heat between the refrigerant in the refrigerant circuit 1 and the cooling water in the engine cooling water circuit, and the engine cooling water is heated by the heat of the gas engine 30. This is a cooling water / refrigerant heat exchanger for heating. The plate heat exchanger 48 is disposed between the four-way valve 18 of the refrigerant circuit 1 and the compressor 15, and exhausts the gas engine 30 into the refrigerant evaporated in the evaporator (that is, the outdoor heat exchanger 19) during the heating operation. It is a heat exchanger for exhaust gas heat recovery that increases the heating capacity by recovering heat. In particular, when the outside air temperature is low (for example, 0 ° C. or less), the heat exchange between the outside air and the refrigerant may not be sufficiently performed in the evaporator, so the plate heat exchanger 48 functions as a sub-evaporator. As a result, the heating capacity can be maintained and enhanced. Accordingly, the plate heat exchanger 48 is mainly used during heating operation.

The above Stirling engine 70 uses the engine cooling water flowing through the engine cooling water circuit 43 as a low-temperature heat source and uses exhaust gas discharged from the gas engine 30 as a high-temperature heat source. A type of external combustion engine driven by temperature differences.
The Stirling engine 70 includes an output shaft 70A, and an auxiliary compressor 72 separate from the compressor 15 is connected to the output shaft 70A. Specifically, the auxiliary compressor 72 includes a V-belt 73 spanned between a pulley (not shown) on the auxiliary compressor 72 side and a pulley (not shown) on the output shaft 70A side of the Stirling engine 70. To the Stirling engine 70 through which the Stirling engine 70 is driven.
In the present embodiment, the auxiliary compressor 72 is provided in parallel with the compressor 15 in the refrigerant circuit 1. That is, the suction pipe 72A of the auxiliary compressor 72 is connected to the suction pipe 15A of the compressor 15, and the discharge pipe 72B of the auxiliary compressor 72 is connected to the discharge pipe 15B of the compressor 15 on the downstream side of the check valve 71. It is connected. The discharge pipe 72B of the auxiliary compressor 72 is provided with a check valve 74. These check valves 71 and 74 are refrigerant discharged from one of the compressor 15 and the auxiliary compressor 72 arranged in parallel. Is a valve for preventing the reverse flow of the compressor to the other compressor.
Further, to the Stirling engine 70, a muffler 51, an exhaust top 52, and a neutralizing device 60 are connected for processing and discharging exhaust gas that has passed through the Stirling engine 70. The exhaust side of the Stirling engine 70 and the intake side of the muffler 51 are connected via an exhaust pipe 53 (including an exhaust hose), and exhaust gas containing drain discharged from the Stirling engine 70 passes through the exhaust pipe 53. It flows into the muffler 51. The exhaust gas collides with a silencer (not shown) in the muffler 51 and is silenced, and moisture in the exhaust gas collides with the silencer and becomes drain water.
The exhaust gas that has passed through the muffler 51 flows into the exhaust top 52. The exhaust gas is cooled in the exhaust top 52, moisture in the exhaust gas is condensed and drainage is generated, and the final exhaust gas is exhausted. The air is exhausted outside through the top 52. Drain generated inside the exhaust top 52 is returned to the muffler 51 via a return hose (not shown) and guided to the neutralization device 60. The neutralizer 60 neutralizes harmful substances such as SOx and NOx in the exhaust gas contained in the drain.

Next, the Stirling engine 70 will be described.
FIG. 2 is a schematic view showing the structure of a Stirling engine. The Stirling engine 70 includes a high-temperature heat source-side piston cylinder (hereinafter referred to as a piston and a cylinder) 80 and a low-temperature heat source-side piston cylinder 81, and these piston cylinders 80, 81 are filled with a working fluid. Connected in a state. In this embodiment, helium is used as the working fluid, but hydrogen, nitrogen, air, or the like can also be used.
The piston cylinders 80 and 81 are attached to the crankshaft 82 in a state where the phases of the pistons are shifted by 90 degrees. A fly hole (not shown) is attached to one end of the crankshaft 82, and the output shaft 70A (FIG. 1) is attached to the other end. The high temperature heat source side piston cylinder 80 is provided with a high temperature heat source side heat exchanger 83 for recovering the thermal energy of the exhaust gas discharged from the gas engine 30. The high temperature heat source side heat exchanger 83 includes an intake port 83A through which exhaust gas discharged from the gas engine 30 flows, and an exhaust port 83B through which this exhaust gas is discharged to the muffler 51.

  Further, the low temperature heat source side piston cylinder 81 is provided with a low temperature heat source side heat exchanger 84 for exchanging heat with the engine coolant of the gas engine 30. The low-temperature heat source side heat exchanger 84 has an inlet 84A through which engine cooling water cooled by the radiator 49 flows through the circulation pump 46, and an outlet 84B through which heat-exchanged engine cooling water is discharged to the gas engine 30. And is configured. A regenerator 85 is provided between the high temperature heat source side heat exchanger 83 and the low temperature heat source side heat exchanger 84 to connect the high temperature heat source side piston cylinder 80 and the low temperature heat source side piston cylinder 81. . As the working fluid in the Stirling engine 70 moves back and forth between these, the working fluid repeatedly expands and condenses, and rotates the output shaft 70 </ b> A via the crankshaft 82. Since the auxiliary compressor 72 is connected to the output shaft 70A, the auxiliary compressor 72 is driven by the rotation of the output shaft 70A of the Stirling engine 70. Thereby, the refrigerant compressed and discharged by the auxiliary compressor 72 together with the compressor 15 circulates in the refrigerant circuit 1, whereby the air conditioning operation is executed.

  As described above, according to this embodiment, the compressor 15 driven by the gas engine 30, the four-way valve 18, and the outdoor heat exchanger 19 are provided, and the exhaust gas of the gas engine 30 is provided. Since the Stirling engine 70 is driven by gas as a high-temperature heat source, and the auxiliary compressor 72 is connected to the output shaft 70A of the Stirling engine 70 and operates by assisting the compressor 15, the Stirling engine 70 The auxiliary compressor 72 can be driven using the heat energy of the exhaust gas. According to this, since the compressor 15 can be driven at a low rotational speed as the auxiliary compressor 72 operates, the fuel of the gas engine for driving the compressor 15 regardless of the cooling operation or the heating operation. Consumption can be suppressed, and energy consumption can be reduced.

  Further, according to this embodiment, since the auxiliary compressor 72 is provided in parallel with the compressor 15 in the refrigerant circuit 1, the compressor 15 is driven at a low rotational speed while maintaining the amount of refrigerant circulating in the refrigerant circuit 1. Can be made. For this reason, the fuel consumption of the gas engine for driving the compressor 15 can be suppressed without reducing the air conditioning capability, and the energy consumption can be reduced.

Next, another embodiment will be described.
FIG. 3 is a diagram illustrating a configuration of the refrigerant circuit of the air-conditioning apparatus 100 according to another embodiment. FIG. 3 shows only a portion corresponding to the outdoor unit 11 with a part omitted as compared with FIG. Among the devices constituting the air conditioning apparatus 100 of this other embodiment, those having the same configuration as the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
Since the output of the Stirling engine 70 increases as the temperature difference between the high temperature heat source and the low temperature heat source increases, the engine cooling water supplied to the low temperature heat source side heat exchanger (FIG. 2) 84 from the viewpoint of increasing the output. It is desirable to keep the temperature low.
On the other hand, when the engine cooling water falls below a predetermined temperature (for example, 70 ° C.), blow-by gas including oil mist present in the head cover of the gas engine 30 or blow-by hose is cooled and oil sludge (also referred to as mayonnaise sludge) is generated. . For this reason, in order to avoid the generation of oil sludge, the temperature of the engine coolant supplied to the low-temperature heat source side heat exchanger 84 of the Stirling engine 70 is set to be equal to or higher than the minimum temperature that prevents the generation of oil sludge (for example, 70 ° C. Need to be more than about). As a result, the output of the Stirling engine 70 is restricted by the engine coolant temperature.

  In this another embodiment, as shown in FIG. 3, the air conditioning apparatus 100 includes a cooling water circuit 90 that is used as a low-temperature heat source of the Stirling engine 70, and the cooling water circuit 90 includes the engine cooling water circuit described above. 43 is formed in a separate system. Specifically, the cooling water circuit 90 includes a Stirling engine cooler 91 disposed adjacent to the outdoor heat exchanger 19 and the radiator 49, and the Stirling engine cooler 91 and the Stirling engine 70 on the low-temperature heat source side. The heat exchanger 84 is connected by a cooling water pipe 92. The cooling water pipe 92 is provided with a pump 93 that circulates the cooling water in the cooling water circuit 90.

  According to this another embodiment, the cooling water circuit 90 used as a low-temperature heat source of the Stirling engine 70 is provided, and this cooling water circuit 90 is provided in a separate system from the engine cooling water circuit 43 that cools the gas engine 30. Therefore, the cooling water can be supplied to the low temperature heat source side heat exchanger 84 of the Stirling engine 70 regardless of the temperature of the engine cooling water flowing through the engine cooling water circuit 43. A large temperature difference from the heat source can be obtained. Thereby, since the energy output from the Stirling engine 70 can be ensured, the output of the auxiliary compressor 72 can be increased, and the energy consumption of the gas engine 30 can be reduced accordingly.

Next, another embodiment will be described.
FIG. 4 is a diagram illustrating a configuration of a refrigerant circuit of an air conditioner 200 according to another embodiment. In FIG. 4, only the portion corresponding to the outdoor unit 11 is described as in FIG. 3 described above. Among the devices constituting the air conditioning apparatus 200 according to another embodiment, the same components as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
In this other embodiment, the air conditioning apparatus 200 includes a generator 110 connected to the output shaft 70 </ b> A of the Stirling engine 70. The generator 110 is connected to the Stirling engine 70 via a V-belt 111 spanned between a pulley (not shown) on the generator 110 side and a pulley (not shown) on the output shaft 70A side of the Stirling engine 70. And is driven by the Stirling engine 70. In addition, a battery 112 that stores electric power generated by the generator 110 is connected to the generator 110. The battery 112 supplies power to a load device such as the outdoor fan 22, the circulation pump 46, or the pump 93 during operation of the air conditioner 200 under the control of a control device (not shown), and supplies power to these load devices. The amount can be reduced, and energy consumption can be reduced.

  In this other embodiment, the outdoor fan 22, the circulation pump 46, the pump 93, or the like is illustrated as an example of a load device to which the electric power generated by the generator 110 is supplied. It is good also as a structure which provides the auxiliary compressor driven with an electric motor. According to this configuration, although the use efficiency of exhaust heat is reduced as compared with the configuration in which the auxiliary compressor 72 is connected to the output shaft 70A of the Stirling engine 70, the auxiliary compressor driven by the electric motor is adjacent to the Stirling engine 70. Therefore, the degree of freedom of the layout configuration for arranging the auxiliary compressor can be increased.

While the embodiments of the present invention have been described above, modifications can be made as appropriate without departing from the spirit of the present invention. For example, in the above-described embodiment, the configuration in which the auxiliary compressor 72 is provided in parallel with the compressor 15 has been described. However, the present invention is not limited to this. For example, the auxiliary compressor 72 is on the low stage side and the compressor 15 is on the high stage. You may arrange in series with the side. According to this configuration, the refrigerant that has been raised to the intermediate pressure by the auxiliary compressor 72 may be raised to a desired high pressure by the compressor 15, so that the load on the compressor 15 can be reduced. According to this, fuel consumption of the gas engine for driving the compressor 15 can be suppressed, and energy consumption can be reduced.
Further, an exhaust gas heat exchanger that exchanges heat between the exhaust gas of the gas engine and the engine cooling water may be arranged on the downstream side of the Stirling engine 70. According to this configuration, in the exhaust gas heat exchanger, the exhaust gas heat energy used as the high-temperature heat source of the Stirling engine 70 is recovered in the engine cooling water, thereby further improving the utilization efficiency of the exhaust gas heat energy. it can.

It is a figure which shows the structure of the refrigerant circuit of the air conditioning apparatus which concerns on this Embodiment. It is the schematic which shows the structure of a Stirling engine. It is a figure which shows the structure of the refrigerant circuit of the air conditioning apparatus which concerns on another embodiment. It is a figure which shows the structure of the refrigerant circuit of the air conditioning apparatus which concerns on another embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Refrigerant circuit 10, 100, 200 Air conditioning apparatus 11 Outdoor unit 15 Compressor 18 Four-way valve 19 Outdoor heat exchanger 22 Outdoor fan (blower fan)
30 Gas engine (engine)
43 Engine cooling water circuit 46 Circulation pump (cooling water pump)
70 Stirling Engine 70A Output Shaft 71 Check Valve 72 Auxiliary Compressor 74 Check Valve 82 Crankshaft 83 High Temperature Heat Source Side Heat Exchanger 84 Low Temperature Heat Source Side Heat Exchanger 90 Cooling Water Circuit 91 Stirling Engine Cooler 93 Pump 110 Generator 112 battery

Claims (3)

An air conditioner provided with a compressor circuit driven by an engine, a four-way valve and an outdoor heat exchanger, and an engine cooling water circuit for cooling the engine by sending engine cooling water to the engine by a cooling water pump In the device
A Stirling engine driven by using the exhaust gas of the engine as a high-temperature heat source, and an auxiliary compressor connected to the output shaft of the Stirling engine and operating to assist the compressor, and disposed adjacent to the outdoor heat exchanger A cooling water circuit that is used as a low-temperature heat source for the Stirling engine. The cooling water circuit is provided in a separate system from the engine cooling water circuit. An air conditioner characterized by circulating cooling water having a temperature lower than that of the engine cooling water .   The air conditioning apparatus according to claim 1, wherein the auxiliary compressor is provided in parallel with the compressor on the refrigerant circuit. 3. The generator according to claim 1, further comprising: a generator that is connected to an output shaft of the Stirling engine and generates electric power to be supplied to a load device such as the cooling water pump or a blower fan of the outdoor heat exchanger. The air conditioning apparatus described .

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