JP2007333280A - Ejector type refrigeration cycle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a refrigerant condensed by an evaporator from returning to a compressor at the time of defrosting. <P>SOLUTION: When an outdoor heat exchanger 26 working as the evaporator is defrosted, hot gas emitted from the compressor 12 is directly made to flow into the outdoor heat exchanger 26, and an intake side heat exchanger part 26b to evaporate the refrigerant taken into a refrigerant intake 25b of an ejector 25 in the outdoor heat exchanger 26 is heated by a heater 19. Further, the refrigerant on the downstream side of an outlet side heat exchanger part 26a for evaporating the refrigerant flowing out of the ejector 25 is evaporated by a subordinate evaporator 20. With this structure, the quantity of the refrigerant condensed by the outdoor heat exchanger when defrosted is reduced and the return of the refrigerant to the compressor 12 is prevented. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an ejector-type refrigeration cycle including an ejector serving as a refrigerant decompression unit and a refrigerant circulation unit.

  Conventionally, Patent Document 1 discloses an ejector-type refrigeration cycle that performs defrosting when a heat exchanger functioning as an evaporator is frosted.

  In the ejector-type refrigeration cycle of Patent Document 1, a gas-liquid separator is disposed on the downstream side of the ejector, and a liquid-phase refrigerant outlet of the gas-liquid separator and a refrigerant suction port of the ejector are connected. An evaporator is arranged, and further, a bypass passage for connecting the compressor discharge side and the evaporator inlet side to introduce refrigerant discharged from the compressor directly into the evaporator, and opening and closing for opening and closing the bypass passage And a valve.

At the time of defrosting, the on-off valve of the bypass passage is opened, and the high-temperature refrigerant (hot gas) discharged from the compressor is introduced into the evaporator from the bypass passage to defrost the evaporator. Further, by connecting the bypass passage to the downstream side of the throttling mechanism, the high-temperature refrigerant is prevented from moving toward the liquid-phase refrigerant outlet side of the gas-liquid separator, and the high-temperature refrigerant from the bypass passage is reliably transferred to the evaporator 16. It can be introduced.
JP 2003-83622 A

  Further, the present applicant previously described in Japanese Patent Application No. 2005-225189 (hereinafter referred to as the prior application example), as shown in FIG. 6, a first evaporator 26 a that evaporates the refrigerant flowing out from the ejector 25, In an ejector-type refrigeration cycle including a second evaporator 26b that evaporates the refrigerant sucked into the refrigerant suction port 25b of the ejector 25, a cycle configuration that simultaneously defrosts the first and second evaporators 26a and 26b is proposed. Yes.

  The cycle further includes a bypass passage 32 that connects between the discharge side of the compressor 12 and the inlet side of the second evaporator 26b to allow the refrigerant discharged from the compressor 12 to flow directly into the second evaporator 26b, and the bypass passage. An opening / closing valve 33 for opening and closing 32 is provided.

  At the time of defrosting, the on-off valve 33 of the bypass passage 32 is opened, the high-temperature refrigerant (hot gas) discharged from the compressor 12 is introduced into the second evaporator 26b from the bypass passage 32, and the refrigerant suction port 25b. The first and second evaporators 26a and 26b are defrosted at the same time by causing the refrigerant that has passed through the second evaporator 26b to flow out of the ejector 25 and be introduced into the first evaporator 26a.

  By the way, in the ejector refrigeration cycle of Patent Document 1 and the prior application example, when the defrosting operation is performed, a liquid back in which the compressor 12 sucks the liquid phase refrigerant may occur. When this liquid back is generated, an excessive stress due to the liquid compression is generated in the compressor, which causes a problem of adversely affecting the durable life of the compressor.

  Then, when this inventor investigated the cause, it turned out that it is because the refrigerant | coolant introduced into the evaporator via the bypass channel dissipated heat and condensed at the time of defrosting. This is because if the refrigerant condenses in the evaporator during defrosting, the amount of liquid-phase refrigerant on the downstream side of the evaporator temporarily increases.

  For this reason, even if the gas-liquid separator is arranged downstream of the ejector as in the cycle of Patent Document 1, the temporarily increased liquid-phase refrigerant overflows from the gas-liquid separator, and the overflowed liquid-phase refrigerant is Inhaled by the compressor. Even when the gas-liquid separator is not arranged downstream of the first evaporator 26a as in the cycle of the washing example, the temporarily increased liquid phase refrigerant is sucked into the compressor.

  An object of this invention is to prevent the liquid back | bag to the compressor at the time of defrosting in view of the said point.

  In order to achieve the above object, in the present invention, a compressor (12, 50) for compressing and discharging a refrigerant, a use side heat exchanger (34) for exchanging heat between the refrigerant and a heat exchange target fluid, and utilization A side heat exchanger (34), an ejector (25) having a refrigerant suction port (25b) for sucking refrigerant into the interior by a high-speed refrigerant flow injected from a nozzle portion (25a) for decompressing and expanding the refrigerant flowing out, and a refrigerant suction port The outdoor heat exchanger (26) having a suction side heat exchange part (26b) for exchanging heat between the refrigerant sucked by (25b) and outdoor air, and the high-temperature refrigerant discharged from the compressors (12, 50) directly A bypass passage (32) to be introduced into the outdoor heat exchanger (26), a bypass passage opening / closing mechanism (33) for opening and closing the bypass passage (32), and auxiliary heating means (19, 19) for heating the outdoor heat exchanger (26) 51) and heat In the heating operation mode in which the fluid to be exchanged is heated, the use side heat exchanger (34) acts as a radiator that radiates the refrigerant discharged from the compressor (12, 50), and the outdoor heat exchanger (26) is a compressor. The bypass passage opening / closing mechanism (33) serves as an evaporator for evaporating the refrigerant sucked into (12, 50) and defrosts the frost generated in the outdoor heat exchanger (26). Is characterized by an ejector refrigeration cycle in which the bypass passage (32) is opened and the auxiliary heating means (19, 51) are adapted to heat the outdoor heat exchanger (26).

  According to this, at the time of defrosting which defrosts the outdoor heat exchanger (26) which acts as an evaporator in the heating operation mode, the bypass passage opening / closing mechanism (33) opens the bypass passage (32) and the compressor (12, 50) The high-temperature refrigerant (hot gas) discharged from 50) is guided to the outdoor heat exchanger (26), and the auxiliary heating means heats the outdoor heat exchanger (26). Therefore, the heat quantity of the high-temperature refrigerant and the heat quantity by the auxiliary heating means Both of these can be used to defrost the outdoor heat exchanger (26).

  Therefore, the amount of the high-temperature refrigerant condensed in the outdoor heat exchanger (26) acting as an evaporator can be reduced compared to the case where the defrosting is performed only with the high-temperature refrigerant as in the prior art. The liquid back to the compressor can be prevented. Furthermore, the defrosting time can be shortened.

  Further, in the ejector refrigeration cycle having the above characteristics, the outdoor heat exchanger (26) has an outflow side heat exchange section (26a) for exchanging heat between the ejector (25) outflow refrigerant and the outdoor air in the heating operation mode, The bypass passage (32) may lead the high-temperature refrigerant to the inlet side of the suction side heat exchanger (26b) in the heating operation mode in the outdoor heat exchanger (26).

  By the way, in the heating operation mode, in the outdoor heat exchanger (26) having the outflow side heat exchange section (26a) for exchanging heat between the ejector (25) outflow refrigerant and the outdoor air, the refrigerant in the outflow side heat exchange section (26a). The refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side heat exchange unit (26b) connected to the refrigerant suction port (25b) is lower than the evaporation pressure (refrigerant evaporation temperature).

  Therefore, in the outdoor heat exchanger (26), the suction side heat exchange part (26b) having a lower refrigerant evaporation temperature than the outflow side heat exchange part (26a) is more likely to be frosted. Therefore, if the bypass passage (32) guides the high temperature refrigerant to the inlet side of the suction side heat exchange section (26b) in the heating operation mode, the outdoor heat exchanger (26) can be efficiently defrosted. it can.

  In the ejector refrigeration cycle having the outflow side heat exchange section (26a), the auxiliary heating means (19, 51) includes the suction side heat exchange section (26b) in the outdoor heat exchanger (26). You may come to heat. According to this, since the auxiliary heating means (19, 51) heats the suction side heat exchange section (26b) that easily forms frost in the outdoor heat exchanger (26), the outdoor heat exchanger (26) can be efficiently defrosted.

  Further, the ejector refrigeration cycle having the above-described characteristics may include an evaporating heating means (20, 52) for heating and evaporating the refrigerant sucked into the compressor (12, 50) during defrosting. According to this, since the evaporating heating means (20, 52) heats and evaporates the refrigerant sucked into the compressor (12, 50), liquid back to the compressor during defrosting is further prevented. it can.

  In the ejector-type refrigeration cycle having the above-described characteristics, the compressor is an engine-driven compressor (12) driven by the engine (13), and the auxiliary heating means uses the cooling water of the engine (13) as a heat source. A warm water heater (19) may be used. According to this, engine waste heat can be effectively utilized at the time of defrosting.

  Further, for example, when the compressor (50) is an electrically driven compressor, the engine waste heat cannot be used, so the auxiliary heating means is an electric heater (51) that generates heat when power is supplied. Also good.

  The ejector-type refrigeration cycle having the above-described features further includes a flow path switching means (21) for switching between a refrigerant flow path in the heating operation mode and a refrigerant flow path in the cooling operation mode for cooling the heat exchange target fluid. In the operation mode, the outdoor heat exchanger (26) acts as a radiator that dissipates the refrigerant discharged from the compressor (12, 50), and the use side heat exchanger (34) sucks into the compressor (12, 50). It may act as an evaporator for evaporating the refrigerant to be produced.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
FIG. 1 is an overall configuration diagram of an example in which the ejector-type refrigeration cycle of the present invention is applied to an engine-driven heat pump air conditioner. The heat pump air conditioner has a heating operation mode (heating operation mode) and a cooling operation mode (cooling). (Operation mode) is configured to be switchable. Accordingly, the heat exchange target fluid of this embodiment is air blown into the room.

  First, the heat pump air conditioner is roughly divided into an outdoor unit 10 and an indoor unit 11. The outdoor unit 10 includes a compressor 12 and a water-cooled engine 13 that drives the compressor 12.

  The compressor 12 sucks, compresses and discharges the refrigerant in the ejector refrigeration cycle, and the driving force is transmitted from the engine 13 via the pulley and the belt V. Therefore, the compressor 12 is an engine driven compressor driven by the engine 13. Further, in the present embodiment, a known swash plate type variable displacement compressor capable of continuously variably controlling the discharge capacity by a control signal from the outside is adopted as the compressor 12.

  The swash plate type variable displacement compressor can adjust the discharge capacity by changing the discharge capacity. The change in the discharge capacity is performed by controlling the pressure Pc in a swash plate chamber (not shown) formed in the compressor 12 and changing the tilt angle of the swash plate to change the piston stroke. The discharge capacity is the geometric volume of the working space where the refrigerant is sucked and compressed. Specifically, it is the cylinder volume between the top dead center and the bottom dead center of the piston stroke.

  The pressure Pc in the swash plate chamber changes the rate at which the discharge refrigerant pressure Pd and the suction refrigerant pressure Ps are introduced into the swash plate chamber by an electromagnetic capacity control valve 12a driven by an output signal of the air conditioning controller 40 described later. It is controlled by that. Thereby, the compressor 12 can continuously change the discharge capacity within a range of approximately 0% to 100%.

  Further, since the compressor 12 can continuously change the discharge capacity in the range of approximately 0% to 100%, the compressor 12 is substantially stopped by reducing the discharge capacity to approximately 0%. Can be in a state. Therefore, in the present embodiment, a clutchless configuration in which the rotating shaft of the compressor 12 is always connected to the engine 13 via a pulley and a belt V is employed.

  Of course, even a variable displacement compressor may transmit power from the engine 13 via an electromagnetic clutch. Further, when a fixed capacity compressor is employed as the compressor 12, the discharge capacity may be controlled by operating rate control in which the compressor is intermittently operated by an electromagnetic clutch to control the on / off operation ratio.

  The engine 13 is a diesel engine that uses kerosene as fuel, and is configured to have a starter (not shown). The fuel to the engine 13 is changed by changing the valve opening degree of the fuel injection valve by the fuel injection valve driving device. The engine speed can be controlled by controlling the injection amount. The fuel injection valve driving device is controlled by an output signal of an air conditioning control device 40 described later.

  The engine 13 is a water-cooled engine, and the outdoor unit 10 includes a cooling water circuit 14 that circulates the cooling water of the engine 13. The cooling water is circulated through the cooling water circuit 14 by the electric water pump 15 and is cooled by the radiator 16 in a heating operation mode and a cooling operation mode described later. The radiator 16 is a radiator that exchanges heat between cooling water and outside air.

  Further, the cooling water circuit 14 has a thermo valve 17, and a circuit for introducing cooling water into the radiator 16 and a circuit for bypassing the radiator 16 are switched by the thermo valve 17. This thermo-valve 17 is a known temperature response valve that displaces the valve body by utilizing the change in the volume of the wax, and switches to the radiator 16 introduction circuit when the cooling water temperature exceeds a predetermined temperature, and bypasses when the temperature becomes lower than the predetermined temperature. Switch to circuit.

  The cooling water circuit 14 is provided with an electric three-way valve 18. The electric three-way valve 18 is a cooling water flow path switching valve that switches between a circuit that introduces cooling water into the radiator 16 and a circuit that introduces cooling water into the heater 19 and the sub-evaporator 20. This electric three-way valve 18 is also controlled by an output signal of an air conditioning control device 40 described later.

  The heater 19 is a hot water heater that heats the outdoor heat exchanger 26 during a defrosting operation to be described later, and has a configuration equivalent to a well-known fin-and-tube heat exchanger. Therefore, in this embodiment, the heater 19 is an auxiliary heating means. Moreover, this heater 19 is comprised integrally with the outdoor heat exchanger 26 mentioned later. Specific configurations of the heater 19 and the outdoor heat exchanger 26 will be described later.

  The sub-evaporator 20 is connected to the downstream side of the cooling water flow of the heater 19 and exchanges heat between the refrigerant sucked into the compressor 12 and the cooling water downstream of the heater 19 during the defrosting operation described later. 12 is a heat exchanger that evaporates the refrigerant sucked by the heat exchanger 12. Accordingly, in the present embodiment, the sub-evaporator 20 constitutes a heating means for evaporation.

  Such a sub-evaporator 20 can be easily configured by joining a tube through which cooling water of the engine 13 passes to a refrigerant pipe connecting the outdoor heat exchanger 26 and the compressor 12 in the heating operation mode. For example, the tubes may be arranged so as to be wound around the refrigerant pipe, and these may be joined by means such as brazing, screwing, caulking, or adhesion.

  Next, the discharge side of the compressor 12 is connected to the electric four-way valve 21. The electric four-way valve 21 is a circuit that connects the compressor 12 discharge side and the indoor unit 11 and the outdoor heat exchanger 26 and the compressor 12 suction side, which will be described later, simultaneously (indicated by solid arrows in FIG. 1). And a circuit (circuit indicated by a broken line arrow in FIG. 1) for simultaneously connecting between the compressor 12 discharge side and the outdoor heat exchanger 26 and between the indoor unit 11 and the compressor 12 suction side. Is to switch.

  The electric four-way valve 21 switches the flow path as described above, thereby switching the refrigerant flow path in the heating operation mode and the cooling operation mode described later. Therefore, the electric four-way valve 21 is a flow path switching unit in the present embodiment. This electric four-way valve 21 is also controlled by an output signal of an air conditioning control device 40 described later.

  Next, the downstream side of the electric four-way valve 21 in the heating operation mode is connected to the first connection port 22 of the indoor unit 11 as in the circuit indicated by the solid line arrow in FIG. A second connection port 23 for allowing the refrigerant that has passed through the indoor unit 11 to flow into the outdoor unit 10 is connected to the receiver 24 side of the outdoor unit 10. Details of the internal configuration of the indoor unit 11 will be described later.

  The receiver 24 is a gas-liquid separator for high-pressure refrigerant that separates gas-phase refrigerant and liquid-phase refrigerant and stores the liquid-phase refrigerant. Further, on the liquid phase refrigerant outlet side of the receiver 24, there is an ejector 25 that is a pressure reducing means for reducing the pressure of the refrigerant and a refrigerant circulating means for circulating the refrigerant by a suction action (winding action) of the refrigerant flow ejected at high speed. It is connected.

  In the heating operation mode, the ejector 25 squeezes the passage area of the liquid-phase refrigerant flowing from the receiver 24 to a small size so that the refrigerant is isentropically decompressed and expanded, and communicates with the refrigerant outlet of the nozzle portion 25a. The refrigerant suction port 25b for sucking the refrigerant, the mixing unit 25c for mixing the high-speed refrigerant flow from the nozzle unit 25a and the suction refrigerant from the refrigerant suction port 25b, and the downstream side of the mixing unit 25c Thus, it is configured to have a diffuser portion 25d that forms a pressure increasing portion that decelerates the refrigerant flow and increases the refrigerant pressure.

  Further, the ejector 25 is provided with a passage area adjusting mechanism 25e that variably controls the refrigerant passage area of the nozzle portion 25a. Specifically, the passage area adjusting mechanism 25e has a needle 25f disposed in the passage of the nozzle portion 25a so as to be movable in the passage longitudinal direction, and a drive portion 25g for moving the needle 25f.

  The tip of the needle 25f has an elongated and sharp shape, and the root of the needle 25f is connected to the drive unit 25g, and the needle 25f moves along the passage of the nozzle unit 25a by the operating force of the drive unit 25g. To do.

  The refrigerant passage area formed between the outer peripheral surface of the needle 25f and the minimum passage portion of the nozzle portion 25a is changed. Furthermore, the passage of the nozzle portion 25a can be fully closed by the outer peripheral surface of the needle 25f contacting the inner wall surface of the minimum passage portion of the nozzle portion 25a.

  As the drive unit 25g, a motor actuator such as a stepping motor, an electromagnetic solenoid mechanism, or the like can be used, and various drive units can be used as long as they can be electrically controlled. Further, the drive unit 25g of the passage area adjusting mechanism 25e is controlled by a control signal of an air conditioning control device 40 described later.

  Furthermore, the outdoor heat exchanger 26 is connected to the diffuser part 25d. In the heating operation mode, the outdoor heat exchanger 26 is a refrigerant sucked by the outflow side heat exchanging portion 26a that exchanges heat between the refrigerant flowing out of the diffuser portion 25d of the ejector 25 and the outdoor air and the refrigerant suction port 25b of the ejector 25. And a suction side heat exchanging portion 26b for exchanging heat with the outdoor air.

  Therefore, the outflow side heat exchanging portion 26a of the outdoor heat exchanger 26 is connected to the diffuser portion 25d. The outdoor heat exchanger 26 is a heat exchanger that exchanges heat between the refrigerant and outdoor air blown by the outdoor fan 27, and the outdoor fan 27 is an electric fan driven by a motor 27a. The motor 27a is rotationally driven by a control voltage output from an air conditioning control device 40 described later.

  The outflow side heat exchanging portion 26a and the suction side heat exchanging portion 26b are integrally coupled so that the heat exchanging regions overlap each other when viewed from the air flow direction (arrow A direction) of the outdoor air. 26, the outflow side heat exchanging portion 26a is disposed on the windward side in the outdoor air flow direction, and the suction side heat exchanging portion 26b is disposed on the leeward side. However, heat can be exchanged in the suction side heat exchanging portion 26b.

  Here, with reference to FIG. 2, details of specific configurations of the outdoor heat exchanger 26 and the heater 19 will be described. FIG. 2 is a schematic overall perspective view of the outdoor heat exchanger 26 and the heater 19. As described above, the outdoor heat exchanger 26 and the heater 19 of this embodiment are integrally coupled.

  The basic configuration of the outflow side heat exchanging portion 26a and the suction side heat exchanging portion 26b of the outdoor heat exchanger 26 is the same, and each exchanges heat between the tubes through which the refrigerant passes and the refrigerant passing through the tubes and the outdoor air. A fin-and-tube heat exchanger configured to have plate-like fins to be promoted. Accordingly, the basic configuration of the outflow side heat exchange unit 26 a and the suction side heat exchange unit 26 b is the same as the basic configuration of the heater 19.

  Therefore, a specific configuration of the fin-and-tube heat exchanger will be described by taking the heater 19 as an example. The fins 19a have a flat plate shape, and a large number of fins 19a are stacked so that the plate surfaces of the fins 19a are parallel to the outdoor air flow direction (arrow A direction), so that outdoor air can pass between the fins 19a. It is like that. And the some tube 19b is arrange | positioned so that the plate | board surface of each laminated | stacked fin 19a may be penetrated in the shape of a skewer.

  In addition, the end portions of each predetermined tube 19b are connected by a U vent pipe or the like as appropriate to communicate with each other, thereby forming a single fluid passage as a whole. That is, the cooling water flowing in from the cooling water inlet port 19c passes through each tube 19b and flows out from the cooling water outlet port 19d.

  The heat exchange region (heating region) formed by the fins 19a and the tubes 19b is substantially rectangular when viewed from the outdoor air flow direction (arrow A direction), and further, the outflow side heat exchange unit 26a and the suction side heat The heat exchanging area of the exchanging portion 26b is also substantially rectangular like the heat exchanging area of the heater 19.

  In the present embodiment, the outflow side heat exchanging portion 26a, the suction side heat exchanging portion 26b, and the heater 19 are made of the same material (for example, aluminum) and viewed from the air flow direction of the outdoor air (in the direction of arrow A). Sometimes, these heat exchange regions are joined together by brazing so that they overlap each other. The heater 19 is joined to the outdoor heat exchanger 16 on the downstream side in the outdoor air flow direction (on the suction side heat exchange unit 26b side).

  Next, as shown in FIG. 1, the downstream side of the outflow side heat exchange unit 26 a in the heating operation mode is connected to an accumulator 28 via an electric four-way valve 21. The accumulator 28 is a gas-liquid separator that separates the gas-phase refrigerant and the liquid-phase refrigerant. The gas-phase refrigerant outlet side of the accumulator 28 and the compressor 12 refrigerant suction side are connected.

  Further, a branch passage 30 for branching the refrigerant flow is provided between the liquid-phase refrigerant outlet side of the receiver 24 and the refrigerant inlet side of the ejector 25 (specifically, the upstream side of the nozzle portion 25a). The passage 30 is connected to the suction side heat exchange part 26 b of the outdoor heat exchanger 26. Further, the other end side of the suction side heat exchange unit 26 is connected to the refrigerant suction port 25 b of the ejector 25.

  The branch passage 30 is provided with an outdoor variable throttle valve 31 that depressurizes the refrigerant by changing the refrigerant passage area according to a control signal output from an air conditioning control device 40 described later. It should be noted that the outdoor variable throttle valve 31 can simply function as a refrigerant passage without exhibiting a pressure reducing action when fully opened (when the refrigerant passage area is maximum).

  Furthermore, the outdoor unit 10 of the present embodiment is provided with a bypass passage 32 that introduces the refrigerant discharged from the compressor 12 directly into the outdoor heat exchanger 26. Specifically, the bypass passage connects between the electric four-way valve 21 and the first connection port 22 of the indoor unit 11 between the outdoor variable throttle valve 31 of the branch passage 30 and the suction side heat exchange unit 26b. It is provided as follows.

  The bypass passage 32 is provided with an opening / closing valve 33 which is a bypass passage opening / closing mechanism for opening and closing the bypass passage 32. The on-off valve 33 is an electromagnetic valve that is driven by a control signal output from the air conditioning control device 40 described later.

  Next, the indoor unit 11 will be described. The indoor unit 11 includes an indoor heat exchanger 34, an indoor variable throttle valve 35, an indoor fan 36, and a motor 36a.

  The indoor heat exchanger 34 is a heat exchanger that exchanges heat between the indoor air blown by the indoor fan 36 and the refrigerant, and is a use side heat exchanger in the present embodiment. The indoor fan 36 is an electric fan driven by a motor 36a. The rotation speed of the motor 36a is controlled by a control voltage output from an air conditioning control device 40 described later.

  The indoor side variable throttle valve 35 changes the refrigerant passage area by a control signal output from an air conditioning control device 40 described later, and depressurizes the refrigerant. The indoor variable throttle valve 35 can simply function as a refrigerant passage without exerting a pressure reducing action when fully open (when the refrigerant passage area is maximum).

  Next, the air conditioning control device 40 is composed of a well-known microcomputer including a CPU, ROM, RAM and the like and its peripheral circuits, and performs various calculations and processing based on a control program stored in the ROM, thereby air conditioning equipment. Control the group's operation.

  A sensor group and a remote controller 43 are connected to the input side of the air conditioning controller 40, and a detection signal of the sensor group and an operation signal of the remote controller 43 are input. The air conditioning control device 40 performs predetermined arithmetic processing based on these input signals and outputs a control signal to the air conditioning equipment group connected to the output side.

  Specifically, the sensor group includes an outdoor heat exchanger outlet temperature sensor 44 and an outdoor heat exchanger outlet pressure sensor 45 provided at the outlet of the outflow side heat exchanger 26a in the heating operation mode, and the indoor heat in the cooling operation mode. An indoor heat exchanger outlet temperature sensor 46 and an indoor heat exchanger outlet pressure sensor 47 provided at the outlet of the exchanger 34 are provided. The temperature sensors 44 and 46 employ thermistors that detect the pipe surface temperature.

  The remote controller 43 includes a temperature setting switch for setting the indoor air temperature to be air-conditioned by the indoor unit 11, an air volume switching switch for switching the air volume of the indoor fan 36, a wind direction switching switch for switching the blowing direction of the indoor blowing air, and a refrigeration cycle A plurality of operation switches such as a cooling / heating switching switch for switching between the cooling / heating modes and an operation display unit (none of which are shown) are provided.

  As the air conditioning equipment group, the electromagnetic capacity control valve 12a, the electric water pump 15, the electric three-way valve 18, the electric four-way valve 21, the ejector 25 passage area adjusting mechanism 25e, the outdoor fan motor 27a, the outdoor side, and the like. The variable throttle valve 31, the indoor variable throttle valve 35, the indoor fan motor 36a, the on-off valve 33, and the like are connected.

  Next, the operation of the present embodiment in the above configuration will be described. First, the operation in the heating operation mode will be described. The heating operation mode is started when the cooling / heating switching switch of the remote controller 43 is switched to the heating side. The heating switching signal of the cooling / heating switching switch is input to the air conditioning control device 40, and the air conditioning control device 40 outputs a control signal so that the air conditioning device group is in the operating state of the heating operation mode of FIG.

  By this control signal, for example, the electric three-way valve 18 switches the cooling water flow path to the radiator 16 side, the electric four-way valve 21 switches the refrigerant flow path to the circuit side indicated by the solid line arrow in FIG. 31 is in a throttle state where the refrigerant is decompressed and expanded, the indoor variable throttle valve 35 is fully opened, and the on-off valve 33 is closed.

  In the cooling water circuit 14 in the heating operation mode, the electric three-way valve 18 switches to a circuit for introducing the cooling water to the radiator 16 side, so that the cooling water does not flow to the heater 19 and the sub-evaporator 20.

  As shown by the solid line in FIG. 1, the electric four-way valve 21 compresses between the compressor 12 outlet side and the indoor unit 11 and the outdoor heat exchanger 26 (specifically, the outflow side heat exchange unit 26a). It switches so that it may connect between the machine 12 inlet side simultaneously. Accordingly, the high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 12 passes through the electric four-way valve 21 and flows into the indoor unit 11.

  The refrigerant flowing into the indoor unit 11 side exchanges heat with the indoor air blown from the indoor fan 36 in the indoor heat exchanger 34 and condenses. Therefore, the indoor heat exchanger 34 acts as a radiator (condenser) that radiates and condenses the refrigerant. The air blown from the indoor fan 36 is heated in the indoor heat exchanger 34 and blown out into the room to heat the room.

  In the heating operation mode, the indoor variable throttle valve 35 is fully opened and functions as a simple refrigerant passage, so that the refrigerant flows out of the indoor unit 11 without being depressurized. The refrigerant that flows out from the indoor unit 11 and flows into the outdoor unit 10 flows into the receiver 24. The liquid-phase refrigerant that has flowed out of the receiver 24 is branched on the downstream side of the refrigerant flow of the receiver 24, and flows out to the nozzle portion 25 a side of the ejector 25 and the outdoor variable throttle valve 31.

  First, the refrigerant flowing into the nozzle portion 25a side of the ejector 25 is decompressed and expanded by the nozzle portion 25a. Here, the air-conditioning control device 40 sets the target refrigerant at the outlet of the outlet heat exchanger 26a based on the detected value of the outdoor heat exchanger outlet pressure sensor 45 provided at the outlet of the outlet heat exchanger 26a in the heating operation mode. The temperature is determined, and the passage area adjusting mechanism 25e of the ejector 25 is controlled so that the detected value of the outdoor heat exchanger outlet temperature sensor 44 approaches the target refrigerant temperature.

  When the refrigerant expands under reduced pressure at the nozzle portion 25a, the pressure energy of the refrigerant is converted into velocity energy, so that the refrigerant is ejected at a high speed from the outlet of the nozzle portion 25a. And the refrigerant | coolant of the suction side heat exchange part 26b downstream is attracted | sucked from the refrigerant | coolant suction port 25b by the refrigerant | coolant suction action of this refrigerant | coolant jet flow.

  The refrigerant ejected from the nozzle portion 25a and the refrigerant sucked from the refrigerant suction port 25b are mixed in the mixing portion 25c on the downstream side of the nozzle portion 25a and flow into the diffuser portion 25d. In the diffuser portion 25d, the passage area is enlarged, so that the velocity energy of the refrigerant is converted into pressure energy, and the pressure of the refrigerant rises. The refrigerant flowing out of the diffuser section 25d evaporates by exchanging heat with the outdoor air blown by the outdoor fan 27 in the outflow side heat exchanging section 26a.

  On the other hand, the liquid refrigerant that has flowed out toward the outdoor variable throttle valve 31 is depressurized in the outdoor variable throttle valve 31. Here, the opening degree of the outdoor variable throttle valve 31 is determined based on the flow rate of the refrigerant passing through the outflow side heat exchange unit 26a and the suction side heat exchange unit 26b based on the passage area of the nozzle portion 25a adjusted by the passage area adjustment mechanism 25e. Is determined such that the flow rate ratio of the refrigerant flow rate passing through the refrigerant reaches a predetermined value.

  The refrigerant decompressed in the outdoor variable throttle valve 31 flows into the suction side heat exchanging portion 26b, evaporates by exchanging heat with the outdoor air blown by the outdoor fan 27 and passed through the outflow side heat exchanging portion 26a. The refrigerant that has flowed out of the suction side heat exchange unit 26b is sucked into the refrigerant suction port 25b, mixed with the refrigerant jetted from the nozzle unit 25a, and sucked into the compressor 12 again.

  Therefore, the outflow side heat exchanging portion 26a and the suction side heat exchanging portion 26b function as an evaporator that absorbs heat by the refrigerant and evaporates. Thus, in the heating operation mode, a cycle in which the refrigerant flows in the direction of the solid line arrow in FIG. 1 is configured, the outdoor heat exchanger 26 acts as an evaporator, and the indoor heat exchanger 34 acts as a radiator, The air is heated.

  Furthermore, in the present embodiment, since the outdoor air blown from the outdoor fan 27 is passed in the order of the outflow side heat exchange unit 26a → the suction side heat exchange unit 26b, the two heat exchange units 26a and 26b simultaneously use the refrigerant. Can absorb heat.

  At that time, the refrigerant evaporating pressure of the outflow side heat exchanging portion 26a is set as the pressure after being increased by the diffuser portion 25d, while the suction side heat exchanging portion 26b is connected to the refrigerant suction port 14b. The refrigerant evaporation pressure of 26b can be set to the lowest pressure immediately after the nozzle portion 25a is depressurized.

  Therefore, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side heat exchange unit 26b can be made lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side heat exchange unit 26a. A temperature difference between the refrigerant evaporation temperature of the side heat exchange unit 26 b and the outdoor air blown by the outdoor fan 27 can be secured, and the refrigerant passing through the outdoor heat exchanger 26 can efficiently absorb heat.

  Next, the operation in the cooling operation mode will be described. The cooling operation mode is started when the cooling / heating switching switch of the remote controller 43 is switched to the cooling side. The air conditioning control device 40 outputs a control signal so that the air conditioning equipment group is in the operation state of the cooling operation mode of FIG.

  By this control signal, for example, the electric three-way valve 18 switches the coolant flow path to the radiator 16 side, and the electric four-way valve 21 switches the refrigerant flow path to the circuit side indicated by the broken line arrow in FIG. 31 is in a fully open state, the indoor variable throttle valve 35 is in a throttle state in which the refrigerant is decompressed and expanded, the passage area adjustment mechanism 25e fully closes the nozzle portion 25a, and the on-off valve 33 is closed.

  The electric four-way valve 21 is compressed between the compressor 12 outlet side and the outdoor heat exchanger 26 (specifically, the outflow side heat exchanging portion 26a) and between the indoor unit 11 and the compression as shown by the broken line in FIG. It switches so that it may connect between the machine 12 inlet side simultaneously. Accordingly, the high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 12 passes through the electric four-way valve 21 and flows into the outflow side heat exchange unit 26a.

  The refrigerant that has flowed into the outflow side heat exchange unit 26a is condensed by exchanging heat with the outdoor air blown from the outdoor fan 27 in the outflow side heat exchange unit 26a. In the refrigerant operation mode, the passage area adjusting mechanism 25e of the ejector 25 causes the nozzle part 25a to be fully closed, so that the refrigerant that has flowed out of the outflow side heat exchange part 26a does not pass through the nozzle part 25a of the ejector 25.

  Therefore, the refrigerant that has flowed out of the outflow side heat exchange unit 26a flows out of the refrigerant suction port 25b and flows into the suction side heat exchange unit 26b. The refrigerant flowing into the suction side heat exchange unit 26b exchanges heat with the outdoor air blown by the outdoor fan 27 and passed through the outflow side heat exchange unit 26a in the suction side heat exchange unit 26b, and further condensed. Therefore, the outflow side heat exchanging portion 26a and the suction side heat exchanging portion 26b act as a condenser that radiates and condenses the refrigerant.

  In the cooling operation mode, since the outdoor variable throttle valve 31 is fully open, the outdoor variable throttle valve 31 functions as a simple refrigerant passage. Therefore, the refrigerant that has flowed out of the suction side heat exchange unit 26b flows into the receiver 24 without being depressurized.

  The liquid-phase refrigerant that has flowed out of the receiver 24 flows out to the indoor unit 11. The liquid-phase refrigerant that has flowed into the indoor unit 11 is depressurized by the indoor variable throttle valve 35. Here, the air conditioning controller 40 sets the target refrigerant temperature at the outlet of the indoor heat exchanger 34 based on the detected value of the indoor heat exchanger outlet pressure sensor 47 provided at the outlet of the indoor heat exchanger 34 in the cooling operation mode. The indoor variable throttle valve 35 is controlled so that the detected value of the indoor heat exchanger outlet temperature sensor 46 approaches the target refrigerant temperature.

  The refrigerant decompressed by the indoor variable throttle valve 35 flows into the indoor heat exchanger 34 and exchanges heat with the indoor air blown by the indoor fan 36 to evaporate. Therefore, the indoor heat exchanger 34 acts as an evaporator that absorbs heat from the refrigerant and evaporates it. The air blown from the indoor fan 36 is cooled in the indoor heat exchanger 34 and blown out into the room to cool the room.

  The refrigerant that has flowed out of the indoor heat exchanger 34 flows into the outdoor unit 10, flows into the accumulator 28 through the electric four-way valve 21, and is sucked into the compressor 12 again. Thus, in the cooling operation mode, a cycle in which the refrigerant flows in the direction of the broken line arrow in FIG. 1 is configured, the outdoor heat exchanger 26 acts as a condenser, and the indoor heat exchanger 34 acts as an evaporator, Air is being cooled.

  By the way, in the heat pump air conditioner of this embodiment, when the outdoor heat exchanger 26 which functions as an evaporator forms frost in heating operation mode, the defrost of the outdoor heat exchanger 26 is performed. If defrosting is not performed, frost grows and outdoor air blown from the outdoor fan 27 cannot pass between the fins of the outdoor heat exchanger 26, and the heat exchange capacity of the outdoor heat exchanger 26 is significantly reduced. Because.

  Therefore, in this embodiment, the air conditioning control device 40 indicates that the outdoor heat exchanger 26 is frosted when the detection value of the outdoor heat exchanger outlet temperature sensor 44 reaches a predetermined value (for example, 0 ° C. or less). Determine and start the defrosting operation.

  During the defrosting operation, the air conditioning control device 40 outputs a control signal so that the air conditioning equipment group is in the operating state of the defrosting operation of FIG. By this control signal, the electric three-way valve 18 switches the cooling water flow path to the heater 19 and the sub-evaporator 20 side, the outdoor variable throttle valve 31 is fully closed, and the passage area adjusting mechanism 25e fully opens the nozzle portion 25a. In the closed state, the on-off valve 33 is opened.

  When the on-off valve 33 is opened, the high-temperature refrigerant (hot gas) discharged from the compressor 12 flows into the branch passage 30 via the bypass passage 32. Here, since the outdoor variable throttle valve 31 is fully closed, the hot gas that has flowed into the branch passage 30 flows into the suction-side heat exchange unit 26b. And the frost outside the suction side heat exchange part 26b is melted by the amount of heat of the hot gas.

  Furthermore, since the passage area adjusting mechanism 25e of the ejector 25 causes the nozzle part 25a to be fully closed, the refrigerant that has passed through the suction side heat exchange part 26b does not pass through the nozzle part 25a of the ejector 25. Accordingly, the refrigerant that has passed through the suction side heat exchange unit 26b passes through the refrigerant suction port 25b → the mixing unit 25c → the diffuser unit 25d and flows into the outflow side heat exchange unit 26a. And the frost outside the outflow side heat exchange part 26a is melted by the amount of heat of the hot gas.

  Further, during the defrosting operation, the electric three-way valve 18 switches the cooling water flow path to the heater 19 and the sub-evaporator 20 side, so that the cooling water of the engine 13 flows through the heater 19 and the sub-evaporator 20. Thereby, the frost outside the outdoor heat exchanger 26 is melted by the amount of heat of the cooling water, and the refrigerant on the downstream side of the outflow side heat exchanger 26a is heated.

  And the air-conditioning control apparatus 40 determines with the defrosting of the outdoor heat exchanger 26 having been completed when the detected value of the outdoor heat exchanger outlet temperature sensor 44 reaches a predetermined value (for example, 1 ° C. or more). Then, the defrosting operation is shifted to the heating operation mode. The temperature difference between the determination values at the start and end of the defrosting operation is a hysteresis width for preventing control hunting.

  As described above, in the present embodiment, during the defrosting, the outdoor heat exchanger uses both the amount of heat of the high-temperature refrigerant (hot gas) discharged from the compressor 12 and the amount of cooling water flowing through the heater 19. 26 can be defrosted, the amount of the high-temperature refrigerant condensed in the outdoor heat exchanger 26 can be reduced as compared with the case where the defrost is performed only with the high-temperature refrigerant as in the prior art.

  Accordingly, it is possible to prevent the liquid phase refrigerant from being temporarily condensed in the indoor heat exchanger 26 during defrosting and overflowing from the accumulator 28. As a result, it is possible to prevent the liquid back from overflowing liquid phase refrigerant being sucked into the compressor. Furthermore, the defrosting time can be shortened.

  Furthermore, since the bypass passage 32 is adapted to guide hot gas to the inlet side of the suction side heat exchange section 26a that is more likely to form frost than the outflow side heat exchange section 26a of the outdoor heat exchanger 26, the outdoor heat The exchanger 26 can be defrosted efficiently.

  Furthermore, since the sub-evaporator 20 that heats and evaporates the refrigerant sucked into the compressor 12 at the time of defrosting can be evaporated, the refrigerant sucked into the compressor 12 can be evaporated. Liquid back to the machine can be prevented.

  Furthermore, since the heater 19 is composed of a hot water heater that uses the cooling water of the engine 13 as a heat source, engine waste heat can be effectively utilized.

(Second Embodiment)
In the first embodiment, an engine-driven compressor is adopted as the compressor 12, but in this embodiment, an electric compressor 50 driven by power supply is adopted. The compressor 50 does not have the electromagnetic capacity control valve 12a because the rotation speed is controlled by the frequency control of the inverter built in the air conditioning control device 40 and the discharge capacity is controlled.

  Further, by adopting the compressor 50, the engine 13 and the cooling water circuit 14 are abolished as shown in FIG. For this reason, the heater 19 and the sub-evaporator 20 which use the cooling water of the engine 13 as a heat source are abolished, and electric heaters 51 and 52 which generate heat by supplying power are provided.

  The electric heater 51 heats the outdoor heat exchanger 26 during the defrosting operation, and is an auxiliary heating means of this embodiment. The electric heater 52 evaporates the refrigerant sucked into the compressor 12 during the defrosting operation, and is the evaporating heating means of the present embodiment. The electric heaters 51 and 52 are supplied with power from the air conditioning controller 40.

  In the present embodiment, specifically, a positive temperature coefficient thermistor (PTC heater) is employed as the electric heater 51. Then, a honeycomb structure in which the positive temperature coefficient thermistor element itself can be ventilated, or a laminated structure of plate-shaped positive temperature coefficient thermistor elements and corrugated fins, etc., has a substantially rectangular shape similar to the heat exchange area of the outdoor heat exchanger 26. It has a shape.

  Further, a heating wire is employed as the electric heater 52, and the heating wire is wound around the refrigerant pipe connecting the outdoor heat exchanger 26 and the compressor 12 in the heating operation mode. Other configurations are the same as those of the first embodiment.

  The operation of the present embodiment in the above configuration will be described. In the heating operation mode and the cooling operation mode, the air conditioning control device 40 outputs a control signal so that the air conditioning equipment group is in the operation state of each operation mode shown in FIG. In addition, since the operation | movement of each air conditioning equipment group in heating operation mode and air_conditionaing | cooling operation mode is the same as that of 1st Embodiment, the operation | movement in a defrost operation is demonstrated in the following description.

  At the time of the defrosting operation, as in the first embodiment, the air conditioning control device 40 outputs a control signal so that the air conditioning equipment group is in the operating state of the defrosting operation of FIG. By this control signal, electric power is supplied to the electric heaters 51 and 52, the outdoor variable throttle valve 31 is fully closed, the passage area adjusting mechanism 25e sets the nozzle portion 25a to be fully closed, and the on-off valve 33 is opened. The

  As a result, the defrosting of the outdoor heat exchanger 26 can be performed using both the amount of heat of the high-temperature refrigerant (hot gas) discharged from the compressor 12 and the amount of heat generated by the electric heater 51 during defrosting. In contrast to the case where the defrosting is performed only with the high-temperature refrigerant as in the prior art, the amount of the high-temperature refrigerant condensed in the outdoor heat exchanger 26 can be reduced. As a result, the same effect as that of the first embodiment can be obtained.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows.

  (1) In the first embodiment described above, a diesel engine using kerosene as fuel is employed, but other types of engines using gasoline, kerosene, hydrogen, or the like as fuel may be employed.

  (2) In the second embodiment, the electric compressor 50 is employed, and the electric heaters 51 and 52 are employed as the auxiliary heating means and the evaporation heating means. However, the compressor 50 is cooled by water cooling. In the case of the configuration, similarly to the first embodiment, the auxiliary heating means and the evaporation heating means may be configured using the cooling water of the compressor 50.

  (3) In the above-described embodiment, the passage area adjustment mechanism 25e of the ejector 25 is fully closed during the defrosting operation. However, the indoor variable throttle valve 35 is fully opened, and the passage area adjustment mechanism 25e is a nozzle. You may make it flow in into the part 25a. According to this, defrosting operation can be performed simultaneously while maintaining heating operation.

  (4) In the above-described embodiment, the outdoor variable throttle valve 31 and the indoor variable throttle valve 35 employ an electric variable throttle mechanism that changes the refrigerant passage area using an electrical control signal. May be adopted.

  In addition, when switching between the function of depressurizing the refrigerant in the heating operation mode and the cooling operation mode and the function as the refrigerant passage as in the above-described embodiment, the first check is made in series with the fixed throttle mechanism (for example, the capillary tube). A second check valve provided with a valve, further provided with a bypass passage connected in parallel with the fixed throttle mechanism and the first check valve, and allowing the flow in the direction opposite to the flow direction of the first check valve in the bypass passage May be provided.

  (5) In the above-described embodiment, the passage area adjusting mechanism 25e is provided in the ejector 25 and the variable flow type ejector is used. However, the fixed flow type ejector and the variable throttle mechanism may be combined. In this case, a variable throttle mechanism having a fully closed function may be disposed upstream of the nozzle portion.

  (6) In the above embodiment, the ejector refrigeration cycle of the present invention is applied to a heat pump air conditioner in which the heat exchange target fluid is indoor air. However, the ejector refrigeration cycle may be applied to a hot water supply device in which the heat exchange target fluid is water. .

It is a whole block diagram of the heat pump air conditioner of 1st Embodiment. It is a whole perspective view of the outdoor heat exchanger and heater of a 1st embodiment. It is a chart which shows the operating state of the air-conditioning equipment group of a 1st embodiment. It is a whole block diagram of the heat pump air conditioner of 2nd Embodiment. It is a graph which shows the operating state of the air conditioning equipment group of 2nd Embodiment. It is a cycle block diagram which shows the ejector type refrigeration cycle of a prior application example.

Explanation of symbols

12, 50 ... compressor, 13 ... engine, 19 ... heater, 21 ... electric four-way valve,
25 ... Ejector, 25a ... Nozzle part, 25b ... Refrigerant suction port,
26 ... Outdoor heat exchanger, 26a ... Outflow side heat exchange part, 26b ... Suction side heat exchange part,
32 ... Bypass passage, 33 ... Open / close valve, 34 ... Indoor heat exchanger, 51, 52 ... Electric heater.

Claims (7)

A compressor (12, 50) for compressing and discharging the refrigerant;
A use side heat exchanger (34) for exchanging heat between the refrigerant and the heat exchange target fluid;
An ejector (25) having a refrigerant suction port (25b) for sucking the refrigerant into the inside by a high-speed refrigerant flow injected from the nozzle (25a) for decompressing and expanding the refrigerant flowing out of the use side heat exchanger (34);
An outdoor heat exchanger (26) having a suction side heat exchange part (26b) for exchanging heat between the refrigerant sucked into the refrigerant suction port (25b) and outdoor air;
A bypass passage (32) for introducing the high-temperature refrigerant discharged from the compressor (12, 50) directly into the outdoor heat exchanger (26);
A bypass passage opening and closing mechanism (33) for opening and closing the bypass passage (32);
Auxiliary heating means (19, 51) for heating the outdoor heat exchanger (26),
In the heating operation mode in which the heat exchange target fluid is heated, the use side heat exchanger (34) acts as a radiator that radiates the refrigerant discharged from the compressor (12, 50), and the outdoor heat exchanger (26 ) Acts as an evaporator for evaporating the refrigerant sucked into the compressor (12, 50),
At the time of defrosting for defrosting the frost generated in the outdoor heat exchanger (26), the bypass passage opening / closing mechanism (33) opens the bypass passage (32), and the auxiliary heating means (19, 51) An ejector-type refrigeration cycle, wherein the outdoor heat exchanger (26) is heated. The outdoor heat exchanger (26) has an outflow side heat exchange section (26a) for exchanging heat between the ejector (25) outflow refrigerant and the outdoor air in the heating operation mode,
The bypass passage (32) guides the high-temperature refrigerant to an inlet side of the suction side heat exchange section (26b) in the heating operation mode in the outdoor heat exchanger (26). The ejector type refrigeration cycle according to claim 1. The said auxiliary | assistant heating means (19, 51) heats the said suction side heat exchange part (26b) among the said outdoor heat exchangers (26), The Claim 2 characterized by the above-mentioned. Ejector refrigeration cycle. The evaporating heating means (20, 52) for heating and evaporating the refrigerant sucked into the compressor (12, 50) during the defrosting is provided. The ejector refrigeration cycle described. The compressor is an engine driven compressor (12) driven by an engine (13),
The ejector refrigeration cycle according to any one of claims 1 to 4, wherein the auxiliary heating means is a hot water heater (19) that uses cooling water of the engine (13) as a heat source. The ejector refrigeration cycle according to any one of claims 1 to 4, wherein the auxiliary heating means is an electric heater (51) that generates heat when power is supplied thereto. A flow path switching means (21) for switching between the refrigerant flow path in the heating operation mode and the refrigerant flow path in the cooling operation mode for cooling the heat exchange target fluid,
In the cooling operation mode, the outdoor heat exchanger (26) acts as a radiator that radiates the refrigerant discharged from the compressor (12, 50), and the use side heat exchanger (34) The ejector refrigeration cycle according to any one of claims 1 to 6, wherein the ejector refrigeration cycle functions as an evaporator for evaporating the refrigerant sucked into 12, 50).

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