WO2023136002A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2023136002A1
WO2023136002A1 PCT/JP2022/045448 JP2022045448W WO2023136002A1 WO 2023136002 A1 WO2023136002 A1 WO 2023136002A1 JP 2022045448 W JP2022045448 W JP 2022045448W WO 2023136002 A1 WO2023136002 A1 WO 2023136002A1
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Prior art keywords
refrigerant
chiller
heat medium
heat
mode
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PCT/JP2022/045448
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English (en)
Japanese (ja)
Inventor
淳司 山田
聡 鈴木
雛乃 大竹
直也 牧本
誠司 伊藤
憲彦 榎本
Original Assignee
株式会社デンソー
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Publication of WO2023136002A1 publication Critical patent/WO2023136002A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Definitions

  • the present disclosure relates to a refrigeration cycle device having a heat medium circuit.
  • Patent Document 1 the technology described in Patent Document 1 is known as a refrigeration cycle device having a heat medium circuit.
  • the refrigeration cycle device of Patent Document 1 is applied to a vehicle air conditioner, and has a plurality of evaporators such as an air conditioning evaporator and a cooling evaporator.
  • the air-conditioning evaporator cools the vehicle interior, and heat is absorbed from the outside air and on-vehicle equipment via the cooling evaporator and the heat medium circuit.
  • the present disclosure relates to a refrigeration cycle device having a heat medium circuit, and an object thereof is to provide a refrigeration cycle device capable of improving cooling performance for one object to be cooled.
  • a refrigeration cycle device is a refrigeration cycle device that has a refrigeration cycle and a heat medium circuit and cools a plurality of objects to be cooled.
  • the refrigeration cycle has a compressor, a condenser, a pressure reducing section, and multiple evaporators.
  • the compressor compresses and discharges refrigerant.
  • the condenser condenses the high pressure refrigerant discharged from the compressor.
  • the decompression unit decompresses the refrigerant flowing out of the condenser.
  • the plurality of evaporators evaporate the refrigerant decompressed in the decompression section to cool the heat medium circulating in the heat medium circuit.
  • the heat medium circuit has a plurality of cooling units that cool a plurality of objects to be cooled by heat exchange with the heat medium.
  • the heat medium circuit is configured to supply the heat medium cooled by at least one of the plurality of evaporators to at least one of the plurality of cooling units.
  • the heat medium circuit is configured to supply the heat medium cooled by at least one of the plurality of evaporators to at least one of the plurality of cooling units.
  • the cooled heat transfer medium can be supplied to one of the plurality of cooling sections. Therefore, the refrigeration cycle apparatus can cool the object to be cooled related to one cooling unit using a plurality of evaporators, and can improve the cooling performance for a specific object to be cooled.
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to the first embodiment
  • FIG. 2 is a configuration diagram of an indoor air conditioning unit according to the first embodiment
  • FIG. 3 is a block diagram showing the control system of the vehicle air conditioner according to the first embodiment
  • FIG. 4 is an explanatory diagram showing the operation mode of the multiple chiller cooling mode according to the first embodiment
  • FIG. 5 is an explanatory diagram showing an operation mode of a multiple chiller battery cooling mode according to the first embodiment
  • FIG. 6 is an explanatory diagram showing the operation mode of the multiple chiller waste heat recovery mode according to the first embodiment
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to the first embodiment
  • FIG. 2 is a configuration diagram of an indoor air conditioning unit according to the first embodiment
  • FIG. 3 is a block diagram showing the control system of the vehicle air conditioner according to the first embodiment
  • FIG. 4 is an explanatory diagram showing the operation mode of the multiple chiller cooling mode according to the first embodiment
  • FIG. 5 is an explanatory diagram showing
  • FIG. 7 is an explanatory diagram showing the operation mode of the multiple chiller outside air heat absorption mode according to the first embodiment
  • FIG. 8 is an explanatory diagram showing the operation mode of the cooling & battery cooling mode according to the first embodiment.
  • FIG. 9 is an explanatory diagram showing the operation mode of the dehumidification heating & waste heat recovery mode according to the first embodiment
  • FIG. 10 is an explanatory diagram showing the operation mode of the dehumidification heating & outside air heat absorption mode according to the first embodiment
  • FIG. 11 is a configuration diagram of a refrigeration cycle apparatus according to the second embodiment
  • FIG. 12 is an explanatory diagram showing the first aspect of the multiple chiller circulation mode in the refrigeration cycle according to the second embodiment;
  • FIG. 13 is an explanatory diagram showing a second aspect of the multiple chiller circulation mode in the refrigeration cycle according to the second embodiment
  • FIG. 14 is an explanatory diagram showing the first aspect of the first chiller circulation mode in the refrigeration cycle according to the second embodiment
  • FIG. 15 is an explanatory diagram showing a second aspect of the first chiller circulation mode in the refrigeration cycle according to the second embodiment
  • FIG. 16 is an explanatory diagram showing an example of the second chiller circulation mode in the refrigeration cycle according to the second embodiment
  • FIG. 17 is an explanatory diagram showing the operation mode of the multiple chiller cooling mode according to the second embodiment
  • FIG. 18 is an explanatory diagram showing the operation mode of the cooling & battery cooling mode according to the second embodiment.
  • FIG. 19 is an explanatory diagram showing the operation mode of the cooling mode using the second chiller according to the second embodiment
  • FIG. 20 is an explanatory diagram showing the operation mode of the dehumidification heating & outside air heat absorption mode according to the second embodiment
  • FIG. 21 is an explanatory diagram showing the operation mode of the second chiller use dehumidification heating mode according to the second embodiment
  • FIG. 22 is an explanatory diagram showing the operation mode of the dehumidification heating & waste heat recovery mode according to the second embodiment
  • FIG. 23 is an explanatory diagram showing the operation mode of the cooling mode using the first chiller according to the second embodiment
  • FIG. 24 is an explanatory diagram showing the operation mode of the first chiller use battery cooling mode according to the second embodiment
  • FIG. 25 is an explanatory diagram showing the operation mode of the first chiller use waste heat recovery mode according to the second embodiment
  • FIG. 26 is an explanatory diagram showing the operation mode of the first chiller use outside air heat absorption mode according to the second embodiment
  • FIG. 27 is an explanatory diagram showing the operation mode of the first chiller use dehumidification heating mode according to the second embodiment
  • FIG. 28 is a configuration diagram of a refrigeration cycle apparatus according to the third embodiment
  • FIG. 29 is an explanatory diagram showing an example of a multiple chiller circulation mode in the refrigeration cycle according to the third embodiment
  • FIG. 30 is an explanatory diagram showing an example of the first chiller circulation mode in the refrigeration cycle according to the third embodiment
  • FIG. 31 is an explanatory diagram showing the operation mode of the first chiller use battery cooling mode according to the third embodiment
  • FIG. 32 is an explanatory diagram showing the operation mode of the first chiller use outside air heat absorption mode according to the third embodiment
  • FIG. 33 is an explanatory diagram showing the operation mode of the first chiller use waste heat recovery mode according to the third embodiment
  • FIG. 34 is a configuration diagram of a refrigeration cycle apparatus according to the fourth embodiment.
  • FIG. A refrigeration cycle apparatus 1 according to the first embodiment is mounted on an electric vehicle, which is a vehicle that obtains driving force for running from an electric motor.
  • the refrigeration cycle device 1 air-conditions the interior of the vehicle, which is a space to be air-conditioned. That is, the refrigeration cycle device 1 can also be called an air conditioner with a device temperature control function.
  • the battery B is a secondary battery that stores power to be supplied to onboard equipment such as an electric motor, and is, for example, a lithium ion battery.
  • Battery B is a so-called assembled battery formed by stacking a plurality of battery cells and electrically connecting these battery cells in series or in parallel.
  • the higher the temperature of the battery the more likely the deterioration of the cells constituting the battery progresses.
  • the battery B can be cooled by cold heat generated by the refrigerating cycle 10 .
  • the electric vehicle according to the first embodiment is equipped with an inverter, a motor generator, a transaxle device, etc., as examples of in-vehicle devices that generate heat during operation.
  • An inverter is a power converter that converts direct current to alternating current.
  • the motor generator outputs driving force for running when supplied with electric power, and generates regenerative electric power at the time of deceleration or the like.
  • a transaxle device is a device that integrates a transmission, a final gear, and a differential gear (differential gear).
  • the refrigerating cycle device 1 is configured to recover the waste heat generated in the on-vehicle equipment using the refrigeration cycle 10 in order to effectively utilize the waste heat generated with the operation of these on-vehicle equipment. .
  • the refrigeration cycle device 1 has a refrigeration cycle 10, a heat medium circuit 30, an indoor air conditioning unit 60, a control device 70, and the like.
  • the refrigeration cycle 10 can cool or heat the heat medium circulating in the heat medium circuit 30 by heat exchange with the refrigerant.
  • the refrigerating cycle 10 in the refrigerating cycle device 1 includes, as components, a compressor 11, a heat medium refrigerant heat exchanger 13, a high-stage expansion valve 14, a gas-liquid separator 15, a first expansion valve 17a, and a second expansion valve 17b. , a first chiller 18 , a second chiller 19 and an accumulator 20 .
  • the refrigerating cycle 10 employs an HFO-based refrigerant (specifically, R1234yf) as a refrigerant.
  • the compressor 11 sucks, compresses, and discharges the refrigerant.
  • Compressor 11 is located in the hood of the vehicle.
  • the compressor 11 is configured by accommodating two compression mechanisms, a low-stage compression mechanism and a high-stage compression mechanism, and an electric motor for rotationally driving both compression mechanisms in a housing that forms an outer shell thereof. It is That is, the compressor 11 is a two-stage boost electric compressor.
  • the housing of the compressor 11 is provided with an intake port 11a, an intermediate pressure port 11b and a discharge port 11c.
  • the intake port 11a is an intake port for sucking low-pressure refrigerant from the outside of the housing into the low-stage compression mechanism.
  • the discharge port 11c is a discharge port that discharges the high-pressure refrigerant discharged from the high-stage compression mechanism to the outside of the housing.
  • the intermediate-pressure port 11b is an intermediate-pressure suction port for allowing intermediate-pressure refrigerant to flow from the outside of the housing to the inside to join the refrigerant in the compression process from low pressure to high pressure. That is, the intermediate pressure port 11b is connected inside the housing to the discharge port side of the low-stage compression mechanism and the suction port side of the high-stage compression mechanism.
  • the operation (rotational speed) of the electric motor is controlled by a control signal output from the control device 70, which will be described later. That is, the refrigerant discharge capacity of the compressor 11 is changed by this rotational speed control.
  • the refrigerant inlet side of the heat medium refrigerant heat exchanger 13 is connected to the discharge port 11c of the compressor 11 via the first three-way joint 12a.
  • the first three-way joint 12a has three inlets and outlets communicating with each other.
  • a joint portion formed by joining a plurality of pipes or a joint portion formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.
  • the first three-way joint 12 a is a branching portion that branches the flow of refrigerant discharged from the compressor 11 .
  • the refrigerant inlet side of the heat medium refrigerant heat exchanger 13 is connected to one outlet of the first three-way joint 12a.
  • a bypass passage 21 is connected to the other outflow port of the first three-way joint 12a.
  • a bypass side flow control valve 22 is arranged in the bypass passage 21 .
  • the bypass-side flow control valve 22 adjusts the discharged refrigerant that has flowed out from the other outlet of the first three-way joint 12a (that is, the other discharged refrigerant branched at the first three-way joint 12a) during a hot gas heating mode, etc., which will be described later. ) is a decompression part on the side of the bypass passage.
  • the bypass-side flow rate adjustment valve 22 is a bypass-side flow rate adjustment section that adjusts the flow rate (mass flow rate) of the refrigerant flowing through the bypass passage 21 .
  • the bypass side flow control valve 22 is an electric variable throttle mechanism having a valve body that changes the throttle opening and an electric actuator (specifically, a stepping motor) that displaces the valve body.
  • the operation of the bypass side flow control valve 22 is controlled by control pulses output from the control device 70 .
  • the bypass side flow control valve 22 By fully opening the valve opening, the bypass side flow control valve 22 has a fully open function that functions as a mere refrigerant passage without exerting almost any refrigerant decompression action or flow rate adjustment action. Further, the bypass side flow control valve 22 has a fully closing function of closing the refrigerant passage by fully closing the valve opening degree.
  • the heat medium refrigerant heat exchanger 13 has a refrigerant passage 13a through which the high-pressure refrigerant discharged from the compressor 11 flows, and a heat medium passage 13b through which the heat medium circulating in the heat medium circuit 30 flows.
  • the heat medium-refrigerant heat exchanger 13 is a condenser that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage 13a and the heat medium flowing through the heat medium passage 13b to condense. That is, the heat medium-refrigerant heat exchanger 13 radiates the heat of the high-pressure refrigerant discharged from the discharge port 11c of the compressor 11 to the heat medium circulating in the heat medium circuit 30, thereby heating the heat medium.
  • the inlet side of the high stage expansion valve 14 is connected to the refrigerant outlet side of the heat medium refrigerant heat exchanger 13 .
  • the high-stage expansion valve 14 has a valve element configured to be able to change the throttle opening degree, and an electric actuator composed of a stepping motor for changing the throttle opening degree of the valve body. make up the mechanism.
  • the high-stage expansion valve 14 is configured to be settable between a throttled state in which pressure reduction is achieved and a fully open state in which pressure reduction is not exhibited. Therefore, the high pressure side expansion valve 14 can reduce the pressure of the high pressure refrigerant flowing out of the heat medium refrigerant heat exchanger 13 to intermediate pressure refrigerant.
  • the operation of the high stage expansion valve 14 is controlled by a control signal output from the control device 70 .
  • a refrigerant inlet of the gas-liquid separator 15 is connected to the refrigerant outlet of the high stage expansion valve 14 .
  • the gas-liquid separator 15 is a gas-liquid separation unit that separates the gas-liquid two-phase refrigerant that has flowed out of the heat medium refrigerant heat exchanger 13 via the high-stage expansion valve 14 .
  • the gas-liquid separator 15 adopts a centrifugal separation method (cyclone separator method) that separates the gas and liquid of the refrigerant by the action of the centrifugal force generated by swirling the refrigerant that has flowed into the inner space of the cylindrical main body. It is
  • the internal volume of the gas-liquid separator 15 according to the first embodiment is such that even if the load fluctuation occurs in the cycle and the flow rate of the refrigerant circulating through the cycle fluctuates, surplus refrigerant cannot be substantially stored. Volume.
  • One end of the intermediate-pressure refrigerant passage 23 is connected to the gas-phase refrigerant outlet of the gas-liquid separator 15 .
  • the other end of the intermediate pressure refrigerant passage 23 is connected to the intermediate pressure port 11 b of the compressor 11 . Therefore, the intermediate-pressure refrigerant passage 23 can guide the gas-phase intermediate-pressure refrigerant separated by the gas-liquid separator 15 to the intermediate-pressure port 11 b of the compressor 11 .
  • a check valve (not shown) is arranged in the intermediate pressure refrigerant passage 23 to prevent the refrigerant from flowing back from the compressor 11 side to the gas-liquid separator 15 side.
  • the check valve may be arranged between the flow path from the gas-phase refrigerant outlet of the gas-liquid separator 15 to the intermediate pressure port 11b of the compressor 11. It may be arranged, or may be arranged at the gas-phase refrigerant outlet of the gas-liquid separator 15 .
  • the liquid-phase refrigerant outlet of the gas-liquid separator 15 is connected to the refrigerant branch portion 16a via a fixed throttle (not shown).
  • the fixed throttle is composed of a nozzle, an orifice, a capillary tube, etc. with a fixed throttle opening, and decompresses the liquid-phase refrigerant separated by the gas-liquid separator 15 .
  • a fixed orifice such as a nozzle or orifice
  • the area of the throttle passage rapidly shrinks or expands.
  • the dryness of the refrigerant on the upstream side of the fixed throttle can be self-adjusted (balanced).
  • the refrigerant branch portion 16a is formed in a three-way joint shape having three inlets and outlets communicating with each other. That is, the refrigerant branching part 16a has one refrigerant inlet and a plurality of refrigerant outlets, and branches the flow of the refrigerant flowing out from the liquid-phase refrigerant outlet side of the gas-liquid separator 15 into a plurality of flows. .
  • the refrigerant branch portion 16a has two refrigerant outlets.
  • a first expansion valve 17a, a first chiller 18, and an accumulator 20 are connected to one of the refrigerant outlets of the refrigerant branch portion 16a, and a second expansion valve 17b and a second chiller 19 are connected to the other refrigerant outlet. is connected. Therefore, the refrigerant branching part 16a branches the refrigerant flow that has flowed out from the gas-liquid separator 15 side into a refrigerant flow on the first chiller 18 side and a refrigerant flow on the second chiller 19 side.
  • the first expansion valve 17a has a valve element configured to be able to change the opening degree of the throttle, and an electric actuator that changes the opening degree of the valve element, and is configured as an electric variable throttle mechanism.
  • the first expansion valve 17a exhibits a throttling function that achieves an arbitrary refrigerant decompression action by setting the valve opening degree to an intermediate opening degree.
  • the first expansion valve 17a has a fully open function in which the valve opening degree is fully opened so that the valve opening degree is fully closed, and the valve opening degree is fully closed. It has a fully closed function to block the refrigerant passage.
  • the operation of the first expansion valve 17 a is controlled by a control signal (control pulse) output from the control device 70 .
  • the first expansion valve 17a can reduce the pressure of the refrigerant that has flowed in from one of the refrigerant outlets of the refrigerant branch portion 16a until it becomes a low-pressure refrigerant, and allows the refrigerant to flow out.
  • the first expansion valve 17a can adjust the flow rate of refrigerant flowing out of one of the refrigerant outlets of the refrigerant branch portion 16a, it is possible to relatively adjust the flow rate of refrigerant flowing out of the other refrigerant outlet. .
  • the refrigerant inlet side of the first chiller 18 is connected to the refrigerant outlet of the first expansion valve 17a.
  • the first chiller 18 includes a refrigerant passage 18a through which the low-pressure refrigerant decompressed by the first expansion valve 17a flows, and a heat medium passage 18b through which the heat medium circulating in the heat medium circuit 30 flows.
  • the first chiller 18 is an evaporator that exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage 18a and the heat medium flowing through the heat medium passage 18b to evaporate the low-pressure refrigerant and exhibit heat absorption.
  • An accumulator 20 is connected to the outlet side of the refrigerant passage 18a in the first chiller 18 via a second three-way joint 12b. As shown in FIG. 1, one of the refrigerant inlets of the second three-way joint 12b is connected to the refrigerant outlet side of the first chiller 18, and the other of the refrigerant inlets of the second three-way joint 12b is connected to a bypass passage. 21 is connected.
  • a refrigerant inlet of the accumulator 20 is connected to the refrigerant outlet of the second three-way joint 12b.
  • the accumulator 20 is a gas-liquid separation unit that separates the liquid-phase refrigerant and the gas-phase refrigerant of the outlet refrigerant in the first chiller 18 and stores surplus refrigerant in the cycle.
  • the outlet side of the accumulator 20 is connected to a refrigerant junction 16b formed in the shape of a three-way joint.
  • the second expansion valve 17b is connected to the other refrigerant outlet of the refrigerant branch portion 16a.
  • the second expansion valve 17b has a valve element configured to change the degree of throttle opening and an electric actuator that changes the degree of opening of the valve element. It is configured as a variable diaphragm mechanism.
  • the second expansion valve 17b can exhibit the throttling function, the fully open function, and the fully closed function by appropriately adjusting the valve opening degree from the fully open state to the fully closed state. can.
  • the operation of the second expansion valve 17 b is controlled by a control signal (control pulse) output from the control device 70 .
  • the second expansion valve 17b can reduce the pressure of the refrigerant that has flowed in from the other side of the refrigerant outlet port of the refrigerant branch portion 16a until it becomes a low-pressure refrigerant and allows the second expansion valve 17b to flow out.
  • the second expansion valve 17b can adjust the flow rate of refrigerant flowing from the other of the refrigerant outlets of the refrigerant branch portion 16a, it is possible to relatively adjust the flow rate of refrigerant flowing toward the first chiller 18 side. .
  • the refrigerant inlet side of the second chiller 19 is connected to the refrigerant outlet of the second expansion valve 17b.
  • the second chiller 19 has a refrigerant passage 19a through which the low-pressure refrigerant decompressed by the second expansion valve 17b flows, and a heat medium passage 19b through which the heat medium circulating in the heat medium circuit 30 flows.
  • the second chiller 19 is an evaporator that exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage 19a and the heat medium flowing through the heat medium passage 19b to evaporate the low-pressure refrigerant and exhibit heat absorption.
  • a refrigerant junction 16 b is connected to the outlet side of the refrigerant passage 19 a in the second chiller 19 .
  • the refrigerant merging portion 16b has a plurality of refrigerant inlets and one refrigerant outlet, and merges a plurality of refrigerant flows branched by the refrigerant branching portion 16a. As shown in FIG. 1, the refrigerant junction 16b has two refrigerant inlets. One of the refrigerant inlets of the refrigerant merging portion 16 b is connected to the refrigerant outlet side of the accumulator 20 , and the other is connected to the refrigerant outlet side of the second chiller 19 .
  • the refrigerant merging section 16b merges the refrigerant flow that has passed through the first chiller 18 side and the refrigerant flow that has passed through the second chiller 19 side into one refrigerant flow and causes it to flow out.
  • the suction port side of the compressor 11 is connected to the refrigerant outlet of the refrigerant junction 16b.
  • the refrigerant in the process of increasing pressure sucked from the suction port 11a of the compressor 11 is converted into a gas phase through the high-stage expansion valve 14 and the gas-liquid separator 15.
  • Intermediate pressure refrigerant can be merged via intermediate pressure port 11b. That is, the refrigerating cycle 10 can constitute a gas injection cycle.
  • the compression efficiency of the high-stage compression mechanism can be improved by causing the low-temperature mixed refrigerant to be sucked into the high-stage compression mechanism. Furthermore, the pressure difference between the suction refrigerant pressure and the discharge refrigerant pressure of both the low-stage compression mechanism and the high-stage compression mechanism can be reduced to improve the compression efficiency of both compression mechanisms. As a result, the COP of the refrigeration cycle 10 as a whole can be improved.
  • the heat medium circuit 30 is a heat medium circulation circuit in which a heat medium temperature-controlled by the refrigeration cycle 10 or the like circulates.
  • a heat medium ethylene glycol, dimethylpolysiloxane, a solution containing a nanofluid or the like, an antifreeze liquid, or the like can be used.
  • the heat medium circuit 30 includes a cooler core 31, a battery heat exchange section 32, an equipment heat exchange section 33, an outside air heat exchanger 34, a heater core 35, an electric heater 36, first pumps 37 to fourth It is configured by connecting pumps 40 and the like by heat medium flow paths.
  • the outlet side of the first pump 37 is connected to the inlet side of the heat medium passage 18b of the first chiller 18.
  • the first pump 37 is a heat medium pump that sucks and discharges the heat medium flowing through the heat medium circuit 30, and may be an electric water pump, for example.
  • the first pump 37 pumps the heat medium toward the inlet side of the heat medium passage 18 b in the first chiller 18 .
  • the outlet side of the second pump 38 is connected to the inlet side of the heat medium passage 19b of the second chiller 19 .
  • the second pump 38 is a heat medium pump that sucks and discharges a heat medium, like the first pump 37 , and pressure-feeds the heat medium toward the inlet side of the heat medium passage 19 b in the second chiller 19 .
  • a first connecting portion 45 a is connected to the outlet side of the heat medium passage 19 b of the second chiller 19 .
  • the first connecting portion 45a is formed in the shape of a three-way joint having three inlets and outlets communicating with each other.
  • a joint member formed by joining a plurality of pipes or a joint member formed by providing a plurality of refrigerant passages in a metal block or a resin block can be used as the first connection portion 45a.
  • the heat medium circuit 30 has a plurality of connection portions formed in the same manner as the first connection portion 45a. Specifically, the heat medium circuit 30 is provided with a first connection portion 45a to a ninth connection portion 45i, each of which is formed in the shape of a three-way joint.
  • the heat medium outlet of the heat medium passage 19b of the second chiller 19 is connected to one of the inlet and outlet ports of the first connection portion 45a.
  • One inlet/outlet of the second connection portion 45b is connected to the other inlet/outlet of the first connection portion 45a.
  • the heat medium inlet side of the cooler core 31 is connected to another inlet/outlet of the first connection portion 45a.
  • the cooler core 31 is a cooling heat exchange unit that exchanges heat between the heat medium flowing through the heat medium circuit 30 and the blown air supplied into the vehicle interior, which is the space to be air-conditioned, to cool the blown air.
  • the cooler core 31 is arranged inside an indoor air conditioning unit 60, which will be described later, and causes the heat medium to absorb heat from the air blown into the passenger compartment. Therefore, the cooler core 31 corresponds to an example of a cooling unit that cools the blown air.
  • a third inlet/outlet 44 c of the four-way valve 44 is connected to the heat medium outlet side of the cooler core 31 .
  • One of the inlets and outlets of the second connecting portion 45b is connected to the outlet side of the heat medium passage 18b in the first chiller 18.
  • the other inlet/outlet of the second connection portion 45b is connected to the other inlet/outlet of the first connection portion 45a, and the other inlet/outlet of the second connection portion 45b is connected to the first
  • the third inlet/outlet 41c of the five-way valve 41 is connected.
  • the first five-way valve 41 is a flow control valve having a first inlet/outlet 41a to a fifth inlet/outlet 41e.
  • the first five-way valve 41 can allow the heat medium that has flowed in from any one of the first inlet/outlet 41a to the fifth inlet/outlet 41e to flow out from any of the remaining inlets/outlets. Therefore, the first five-way valve 41 corresponds to a part of the switching section.
  • the first five-way valve 41 can be formed, for example, by combining a plurality of flow control valves such as three-way flow control valves.
  • the outlet side of the heat medium passage 13b in the heat medium refrigerant heat exchanger 13 is connected to the first inlet/outlet 41a of the first five-way valve 41, and the second inlet/outlet 41b of the first five-way valve 41 is connected to: One of the inlets and outlets of the third connecting portion 45c is connected.
  • the fourth inlet/outlet 41d of the first five-way valve 41 is connected to the heat medium inlet side of the outside air heat exchanger 34, and the fifth inlet/outlet 41e of the first five-way valve 41 is connected to the electric heater 36. is connected to the heat medium inlet side.
  • the heat medium refrigerant heat exchanger 13 is a condenser that condenses the refrigerant by heat exchange between the high-pressure refrigerant and the heat medium in the refrigeration cycle 10, and has the refrigerant passage 13a and the heat medium passage 13b. ing.
  • a fourth pump 40 is connected to the inlet side of the heat medium refrigerant heat exchanger 13 .
  • the fourth pump 40 is a heat medium pump that sucks and discharges the heat medium that has flowed through the seventh connection portion 45g, and can adopt the same configuration as the first pump 37 and the like.
  • the inlet side of the heat medium passage 13b of the heat medium refrigerant heat exchanger 13 is connected to the discharge port of the fourth pump 40 . Therefore, the fourth pump 40 pressure-feeds the heat medium toward the first inlet/outlet 41a side of the first five-way valve 41 through the heat medium passage 13b of the heat medium/refrigerant heat exchanger 13 .
  • the second inlet/outlet 41b of the first five-way valve 41 is connected to one of the inlet/outlets of the third connecting portion 45c.
  • the heat medium inlet side of the battery heat exchange portion 32 is connected to the other one of the inlets and outlets of the third connection portion 45c, and the other inlet and outlet of the third connection portion 45c is connected to the third five-way A third inlet/outlet 43c of the valve 43 is connected.
  • the battery heat exchange section 32 is a heat exchange section for adjusting the temperature of the battery B by exchanging heat between the heat medium flowing through the third connection section 45c and the battery cells that constitute the battery B.
  • the battery heat exchange unit 32 is an example of a cooling unit in which the battery B is the object to be cooled.
  • a heat medium passage is formed inside the battery heat exchange section 32 in which a plurality of passages are connected in parallel.
  • the heat medium passage of the battery heat exchange portion 32 is formed so as to be able to absorb the waste heat of the battery B from the entire area of the battery B evenly.
  • the heat medium passage of the battery heat exchange section 32 is formed so as to uniformly absorb the heat of all the battery cells and to cool all the battery cells equally.
  • the battery heat exchange section 32 may be formed by arranging heat medium passages between the stacked battery cells. Also, the battery heat exchange portion 32 may be formed integrally with the battery B. As shown in FIG. For example, the heat medium passage may be formed integrally with the battery B by providing a heat medium passage in a special case that accommodates the stacked battery cells.
  • One of the inflow/outlet ports of the fourth connection portion 45d is connected to the heat medium outlet side of the battery heat exchange portion 32 .
  • the fifth inflow/outlet 42e of the second five-way valve 42 is connected to another inflow/outlet in the fourth connection portion 45d, and the third five-way valve is connected to another inflow/outlet in the fourth connection portion 45d.
  • 43 is connected to the first inlet/outlet 43a.
  • the outside air heat exchanger 34 is a heat exchanger that exchanges heat between the heat medium flowing out from the fourth inlet/outlet 41d of the first five-way valve 41 and the outside air outside the passenger compartment.
  • the outside air heat exchanger 34 functions as a heat absorber that absorbs the heat of the outside air into the heat medium when the temperature of the heat medium is lower than the outside air temperature, and when the temperature of the heat medium is higher than the outside air temperature, It functions as a radiator that dissipates the heat of the heat medium to the outside air. Therefore, the outside air heat exchanger 34 corresponds to an example of a cooling unit that cools outside air.
  • the heat medium outlet of the outside air heat exchanger 34 is connected to one of the inlets and outlets of the eighth connection portion 45h.
  • Another inflow/outlet in the eighth connection portion 45h is connected to one inflow/outlet in the sixth connection portion 45f, and another inflow/outlet in the eighth connection portion 45h is connected to the inflow/outlet of the ninth connection portion 45i.
  • One of the outlets is connected.
  • a heat medium inlet side of the electric heater 36 is connected to the fifth inlet/outlet 41 e of the first five-way valve 41 .
  • the electric heater 36 has a heat medium passage through which the heat medium flowing out from the fifth inlet/outlet 41e of the first five-way valve 41 flows, and is a heating portion that heats the heat medium passing through the heat medium passage.
  • a PTC heater having a PTC element that generates heat when supplied with power is employed as the electric heater 36.
  • the amount of heat generated by the electric heater 36 is controlled by a control voltage output from the controller 70 .
  • the heating medium inlet side of the heater core 35 is connected to the heating medium outlet side of the electric heater 36 .
  • the heater core 35 is arranged in the indoor air conditioning unit 60 as shown in FIG. 2, and is a heating heat exchange section that exchanges heat between the heat medium flowing out from the electric heater 36 and the blown air supplied into the passenger compartment.
  • the heater core 35 radiates the heat of the heat medium to the blown air to heat the blown air.
  • a heat medium outlet of the heater core 35 is connected to one of the inlets and outlets of the ninth connection portion 45i.
  • the second five-way valve 42 is a flow control valve having first to fifth inflow/outlet 42a to fifth inflow/outlet 42e, and is configured similarly to the first five-way valve 41. As shown in FIG.
  • the second five-way valve 42 can allow the heat medium that has flowed in from any one of the first inflow/outlet 42a to the fifth inflow/outlet 42e to flow out from any of the remaining inflow/outlets. Therefore, the second five-way valve 42 corresponds to part of the switching section.
  • the first inlet/outlet 42a of the second five-way valve 42 is connected to one of the inlet/outlets of the seventh connecting portion 45g, and the second inlet/outlet 42b of the second five-way valve 42 is connected to the sixth connecting portion.
  • One of the inlets and outlets at 45f is connected.
  • the third inlet/outlet 42c of the second five-way valve 42 is connected to the outlet side of the heat medium passage 33a in the equipment heat exchange section 33, and the fourth inlet/outlet 42d of the second five-way valve 42 is connected to the One of the inflow/outlet in the 5 connection part 45e is connected.
  • the fourth inflow/outlet 43d of the third five-way valve 43 is connected to another inflow/outlet of the seventh connection portion 45g, and the other inflow/outlet of the seventh connection portion 45g is connected to the fourth inflow/outlet.
  • the suction port side of the pump 40 is connected.
  • One of the inlets and outlets of the sixth connection portion 45f is connected to one of the inlets and outlets of the eighth connection portion 45h, and the other inlet and outlet of the sixth connection portion 45f is connected to the four-way valve 44.
  • a second inlet/outlet 44b is connected.
  • the device heat exchange unit 33 is a heat exchange unit that is mounted on an electric vehicle and exchanges heat between the on-vehicle device that generates heat as it operates and the heat medium pressure-fed by the third pump 39 .
  • the in-vehicle equipment in the first embodiment may include an inverter, a motor generator, a transaxle device, and the like.
  • the equipment heat exchange unit 33 forms a heat medium passage through which the heat medium flowing out from the third pump 39 flows, in a housing or case forming the outer shell of the in-vehicle equipment such as an inverter, a motor generator, a transaxle device, or the like. It consists of
  • the device heat exchange unit 33 corresponds to an example of a cooling unit whose object to be cooled is an in-vehicle device.
  • a heat medium inlet side of the equipment heat exchange section 33 is connected to a discharge port side of the third pump 39 .
  • the third pump 39 is a heat medium pump that sucks and discharges the heat medium that has flowed through the fifth connection portion 45e, and can adopt the same configuration as the first pump 37 and the like.
  • a discharge port of the third pump 39 is connected to a heat medium inlet side of the equipment heat exchange section 33 . Therefore, the third pump 39 pressure-feeds the heat medium toward the heat medium inlet side of the equipment heat exchange section 33 .
  • the suction port side of the third pump 39 is connected to another one of the inlets and outlets of the fifth connection portion 45e, and the other inlet and outlet of the fifth connection portion 45e is connected to the third five-way valve 43.
  • a second inlet/outlet 43b is connected.
  • the third five-way valve 43 is a flow regulating valve having first to fifth inlets/outlets 43a to 43e, and is configured similarly to the first five-way valve 41 and the like.
  • the third five-way valve 43 can allow the heat medium that has flowed in from any one of the first to fifth inlets 43a to 43e to flow out from any of the remaining inlets. Therefore, the third five-way valve 43 corresponds to part of the switching section.
  • the first inflow/outlet 43a of the third five-way valve 43 is connected to one of the inflow/outlet of the fourth connecting portion 45d, and the second inflow/outlet 43b of the third five-way valve 43 is connected to the fifth connecting portion.
  • One of the inlets and outlets at 45e is connected.
  • the third inlet/outlet 43c of the third five-way valve 43 is connected to one of the inlet/outlets of the third connecting portion 45c, and the fourth inlet/outlet 43d of the third five-way valve 43 is connected to the seventh connecting portion.
  • One of the inlets and outlets at 45g is connected.
  • the fifth inlet/outlet 43e of the third five-way valve 43 is connected to one inlet/outlet of the ninth connecting portion 45i.
  • the first inflow/outlet 42a of the second five-way valve 42 is connected to another inflow/outlet of the seventh connection portion 45g, and the other inflow/outlet of the seventh connection portion 45g is connected to the fourth The suction port side of the pump 40 is connected.
  • the refrigerant outlet side of the cooler core 31 is connected to the other inlet/outlet of the eighth connection portion 45h, and the other inlet/outlet of the eighth connection portion 45h is connected to the inlet/outlet of the eighth connection portion 45h.
  • One of the outlets is connected.
  • the second inlet/outlet 44b of the four-way valve 44 is connected to another inlet/outlet of the sixth connection portion 45f.
  • the four-way valve 44 is a flow control valve having four heat medium inlets and outlets, ie, a first inlet/outlet 44a to a fourth inlet/outlet 44d.
  • the four-way valve 44 adjusts the flow rate of the heat medium flowing out from any one of the first to fourth inlets 44a to 44d. Therefore, the four-way valve 44 corresponds to a part of the switching section.
  • the first inlet/outlet 44a of the four-way valve 44 is connected to the suction port side of the first pump 37, and the second inlet/outlet 44b of the four-way valve 44 is connected to one of the inlets/outlets of the sixth connecting portion 45f. ing.
  • the heat medium outlet side of the cooler core 31 is connected to the third inlet/outlet 44c of the four-way valve 44, and the suction port side of the second pump 38 is connected to the fourth inlet/outlet 44d of the four-way valve 44. .
  • the heat medium circuit 30 configurations corresponding to the four cooling sections of the cooler core 31, the battery heat exchange section 32, the equipment heat exchange section 33, and the outside air heat exchanger 34 are arranged. Therefore, if one of the four cooling units corresponds to the first cooling unit, one of the remaining cooling units corresponds to the second cooling unit. For example, when the cooler core 31 corresponds to the first cooling section, any one of the battery heat exchanging section 32, the equipment heat exchanging section 33, and the outside air heat exchanger 34 corresponds to the second cooling section.
  • the indoor air conditioning unit 60 that constitutes the refrigeration cycle device 1 will be described with reference to FIG.
  • the indoor air conditioning unit 60 is for blowing out into the passenger compartment the blown air whose temperature has been adjusted by the refrigeration cycle 10 .
  • the interior air-conditioning unit 60 is arranged inside the dashboard (instrument panel) at the forefront of the vehicle interior.
  • the indoor air conditioning unit 60 accommodates a blower 62, a cooler core 31, a heater core 35, etc. inside an air passage formed in a casing 61 that forms its outer shell.
  • the casing 61 forms an air passage for air blown into the passenger compartment.
  • the casing 61 is molded from a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.
  • An inside/outside air switching device 63 is arranged on the most upstream side of the blown air flow of the casing 61 .
  • the inside/outside air switching device 63 switches and introduces inside air (vehicle interior air) and outside air (vehicle exterior air) into the casing 61 .
  • the inside/outside air switching device 63 continuously adjusts the opening areas of the inside air introduction port for introducing inside air into the casing 61 and the outside air introduction port for introducing outside air into the casing 61 by means of the inside/outside air switching door, so that the amount of introduced inside air and the amount of outside air are adjusted. Change the introduction ratio with the introduction air volume.
  • the inside/outside air switching door is driven by an electric actuator for inside/outside air switching door. The operation of this electric actuator is controlled by a control signal output from the control device 70 .
  • a blower 62 is arranged downstream of the inside/outside air switching device 63 in the blown air flow.
  • the blower 62 blows the air sucked through the inside/outside air switching device 63 into the vehicle interior.
  • the blower 62 is an electric blower that drives a centrifugal multi-blade fan with an electric motor.
  • the blower 62 has its rotation speed (that is, blowing capacity) controlled by a control voltage output from the control device 70 .
  • a cooler core 31 and a heater core 35 are arranged in this order with respect to the blown air flow downstream of the blower 62 . That is, the cooler core 31 is arranged upstream of the heater core 35 in the blown air flow.
  • a cold air bypass passage 65 is provided in the casing 61 for bypassing the heater core 35 and allowing the blown air after passing through the cooler core 31 to flow.
  • An air mix door 64 is arranged downstream of the cooler core 31 in the casing 61 and upstream of the heater core 35 in the air flow.
  • the air mix door 64 is an air volume ratio adjustment unit that adjusts the air volume ratio between the volume of the air passing through the heater core 35 side and the volume of the air passing through the cold air bypass passage 65 among the air that has passed through the cooler core 31. be.
  • the air mix door 64 is driven by an air mix door electric actuator. The operation of this electric actuator is controlled by a control signal output from the control device 70 .
  • a mixing space is arranged downstream of the heater core 35 and the cold air bypass passage 65 in the casing 61 .
  • the mixing space is a space in which the blast air heated by the heater core 35 and the unheated blast air passing through the cold air bypass passage 65 are mixed.
  • An opening hole for blowing out the blast air mixed in the mixing space (that is, the conditioned air) into the vehicle interior, which is the space to be air-conditioned, is arranged in the downstream portion of the blast air flow of the casing 61 .
  • the openings include a face opening, a foot opening, and a defroster opening (all not shown).
  • the face opening hole is an opening hole for blowing air conditioning air toward the upper body of the passenger inside the vehicle.
  • the foot opening hole is an opening hole for blowing the conditioned air toward the passenger's feet.
  • the defroster opening hole is an opening hole for blowing the conditioned air toward the inner surface of the window glass arranged on the front surface of the vehicle.
  • face opening hole, foot opening hole, and defroster opening hole are connected to the face outlet, foot outlet, and defroster outlet (none of which are shown) provided in the passenger compartment via ducts that form air passages. )It is connected to the.
  • the air mix door 64 adjusts the air volume ratio between the air volume passing through the heater core 35 and the air volume passing through the cold air bypass passage 65, thereby adjusting the temperature of the conditioned air mixed in the mixing space. Then, the temperature of the blown air (air-conditioned air) blown into the passenger compartment from each outlet is adjusted.
  • a face door, a foot door, and a defroster door are arranged on the upstream sides of the face opening hole, the foot opening hole, and the defroster opening hole, respectively.
  • the face door adjusts the opening area of the face opening hole.
  • the foot door adjusts the opening area of the foot opening hole.
  • the defroster door adjusts the opening area of the defroster opening hole.
  • the face door, foot door, and defroster door constitute an outlet mode switching device that switches the outlet mode.
  • These doors are connected to an electric actuator for driving the outlet mode door via a link mechanism or the like, and are rotated in conjunction with each other.
  • the operation of this electric actuator is also controlled by a control signal output from the control device 70 .
  • the face mode is an air outlet mode in which the face air outlet is fully opened and air is blown out from the face air outlet toward the upper body of the occupant in the passenger compartment.
  • the bi-level mode is an outlet mode that opens both the face and foot outlets to blow air toward the upper body and feet of the passengers inside the vehicle.
  • the foot mode is an air outlet mode in which the foot air outlet is fully opened and the defroster air outlet is opened by a small degree of opening so that air is mainly blown out from the foot air outlet.
  • the passenger can manually operate the blowout mode switch provided on the operation panel 71 to switch to the defroster mode.
  • the defroster mode is an outlet mode in which the defroster outlet is fully opened and air is blown from the defroster outlet to the inner surface of the windshield.
  • the control device 70 is composed of a well-known microcomputer including CPU, ROM, RAM, etc. and its peripheral circuits.
  • the control device 70 performs various calculations and processes based on the air conditioning control program stored in the ROM, and controls the operation of various controlled devices connected to the output side.
  • the control device 70 corresponds to an example of a control section.
  • the various devices to be controlled include the compressor 11, the high-stage expansion valve 14, the first expansion valve 17a, the second expansion valve 17b, and the bypass-side flow control valve 22. Furthermore, the various devices to be controlled include an electric heater 36, a first pump 37 to a fourth pump 40, a first five-way valve 41, a second five-way valve 42, a third five-way valve 43, a four-way valve 44, and a blower 62. , an inside/outside air switching device 63, an air mix door 64, and the like.
  • Control sensors include an inside air temperature sensor 72a, an outside air temperature sensor 72b, a solar radiation sensor 72c, a high pressure sensor 72d, a first chiller temperature sensor 72e, and a second chiller temperature sensor 72f.
  • Control sensors include an air-conditioning air temperature sensor 72g, an equipment temperature sensor 72h, and a battery temperature sensor 72i.
  • the inside air temperature sensor 72a is an inside air temperature detection unit that detects the inside air temperature Tr, which is the temperature inside the vehicle compartment.
  • the outside air temperature sensor 72b is an outside air temperature detection unit that detects the outside air temperature Tam, which is the temperature outside the vehicle compartment.
  • the solar radiation sensor 72c is a solar radiation amount detection unit that detects the amount of solar radiation As irradiated into the vehicle interior.
  • the high pressure sensor 72d is a high pressure detection unit that detects the high pressure Pd, which is the pressure of the high pressure refrigerant discharged from the compressor 11.
  • the first chiller temperature sensor 72e is a coolant temperature detection unit that detects the coolant evaporation temperature in the coolant passage 18a of the first chiller 18 .
  • the second chiller temperature sensor 72f is a second chiller-side refrigerant temperature detection unit that detects the refrigerant evaporation temperature in the refrigerant passage 19a of the second chiller 19 .
  • the air-conditioning air temperature sensor 72g is an air-conditioning air temperature detection unit that detects the temperature TAV of air blown out from the mixing space into the vehicle interior.
  • the device temperature sensor 72h is a device temperature detection unit that detects the temperature of an inverter or the like mounted as a vehicle device.
  • the equipment temperature sensor 72h has a plurality of temperature detection units and can detect the equipment temperature of each of the inverter, motor generator, and transaxle device.
  • the battery temperature sensor 72i is a battery temperature detection unit that detects a battery temperature TB, which is the temperature of the battery B.
  • the battery temperature sensor 72i has a plurality of temperature detection units and detects temperatures at a plurality of locations of the battery B. FIG. Therefore, the control device 70 can also detect the temperature difference between the parts of the battery B.
  • FIG. Furthermore, as the battery temperature TB, an average value of detection values of a plurality of temperature sensors is used.
  • a plurality of heat medium temperature sensors are connected to the input side of the control device 70 to detect the temperature of the heat medium in the heat medium circuit 30 .
  • the multiple heat medium temperature sensors include a first heat medium temperature sensor 73a to a seventh heat medium temperature sensor 73g.
  • the first heat medium temperature sensor 73a is arranged at the outlet portion of the heat medium passage 18b in the first chiller 18, and detects the temperature of the heat medium flowing out of the first chiller 18.
  • the second heat medium temperature sensor 73b is arranged at the outlet portion of the heat medium passage 19b in the second chiller 19, and detects the temperature of the heat medium flowing out of the second chiller 19. As shown in FIG.
  • the third heat medium temperature sensor 73 c is arranged at the inlet portion of the cooler core 31 and detects the temperature of the heat medium passing through the cooler core 31 .
  • the fourth heat medium temperature sensor 73d is arranged at the inlet portion of the heat medium passage in the battery heat exchange section 32 and detects the temperature of the heat medium passing through the battery heat exchange section 32 .
  • the fifth heat medium temperature sensor 73e is arranged at the inlet portion of the heat medium passage of the equipment heat exchange section 33, and detects the temperature of the heat medium passing through the heat medium passage 33a of the equipment heat exchange section 33. To detect.
  • the sixth heat medium temperature sensor 73f is arranged at the inlet portion of the heat medium passage of the outside air heat exchanger 34 and detects the temperature of the heat medium passing through the outside air heat exchanger 34 .
  • the seventh heat medium temperature sensor 73g is arranged at the heat medium inlet portion of the heater core 35 and detects the temperature of the heat medium passing through the heater core 35 .
  • the refrigeration cycle device 1 controls the refrigeration cycle 10 and the heat medium circuit 30 by referring to the detection results of the first heat medium temperature sensor 73a to the seventh heat medium temperature sensor 73g.
  • control device 70 is connected to an operation panel 71 arranged near the instrument panel in the front part of the passenger compartment. Operation signals from various operation switches provided on the operation panel 71 are input to the control device 70 .
  • operation switches provided on the operation panel 71 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, and the like.
  • the auto switch is an operation switch for setting or canceling automatic control operation of the refrigeration cycle 10 .
  • the air conditioner switch is an operation switch that requests that the cooler core 31 cool the blown air.
  • the air volume setting switch is an operation switch that is operated when manually setting the air volume of the blower 62 .
  • the temperature setting switch is an operation switch for setting a target temperature Tset in the passenger compartment.
  • the control device 70 of the first embodiment is integrally configured with a control section that controls various control target devices connected to the output side thereof. Therefore, the configuration (that is, hardware and software) that controls the operation of each controlled device constitutes a control unit that controls the operation of each controlled device.
  • the configuration that controls the refrigerant discharge capacity (for example, the number of revolutions) of the compressor 11 in the refrigeration cycle 10 corresponds to the compressor control section 70a.
  • the amount of pressure reduction (that is, throttle opening) in the high-stage expansion valve 14, the first expansion valve 17a, the second expansion valve 17b, and the bypass-side flow control valve 22 of the refrigeration cycle 10 is controlled.
  • the configuration corresponds to the pressure reduction control section 70b.
  • the high-stage expansion valve 14 the first expansion valve 17a, the second expansion valve 17b, and the bypass-side flow control valve 22 are controlled to configure a circuit configuration in which the refrigerant circulates in the refrigeration cycle 10.
  • the configuration for switching corresponds to the refrigerant circuit switching control section 70c.
  • the first pump 37 to the fourth pump 40, the first five-way valve 41, the second five-way valve 42, the third five-way valve 43, and the four-way valve 44 are controlled to open the heat medium circuit.
  • the configuration for switching the circulation circuit of the heat medium in 30 corresponds to the heat medium circuit switching control section 70d.
  • the operation mode of the refrigeration cycle device 1 is determined by a combination of the operation mode (circuit configuration) of the refrigeration cycle 10 and the operation mode (circuit configuration) of the heat medium circuit 30 .
  • the first chiller 18 absorbs heat from the heat medium to the refrigerant, and the heat medium-refrigerant heat exchanger 13 heats the heat.
  • An operation mode in which heat is radiated by the medium-refrigerant heat exchanger 13 is included.
  • the operation mode of the refrigeration cycle 10 includes an operation mode in which heat is absorbed from the heat medium to the refrigerant in each of the first chiller 18 and the second chiller 19 and heat is released in the heat medium-refrigerant heat exchanger 13. .
  • the accumulator 20 is arranged between the outlet side of the refrigerant passage 18a of the first chiller 18 and the refrigerant junction 16b. Therefore, the refrigerating cycle 10 can ensure the cooling performance of the first chiller 18 .
  • the outlet side of the first chiller 18 is provided with an accumulator 20 that forms a gas-liquid interface of the saturated refrigerant. :1 is maintained near the saturated gas.
  • outlet side refrigerant of the second chiller 19 is merged at the inlet side of the accumulator 20, when the outlet refrigerant of the second chiller 19 is a superheated refrigerant gas, the outlet refrigerant of the first chiller 18 is this superheated refrigerant gas. It balances in the state of wet steam with a dryness that contains enough liquid refrigerant to cancel out the temperature.
  • the balance state of the refrigerant at the outlet of the first chiller 18 shifts to the side of wet steam with a predetermined dryness, and the refrigerant heat absorption amount in the first chiller 18, that is, It is assumed that the cooling performance will deteriorate.
  • the accumulator 20 is arranged between the outlet of the refrigerant passage 18a of the first chiller 18 and the refrigerant junction 16b.
  • a decrease in performance can be suppressed. If the superheated refrigerant gas on the outlet side of the second chiller 19 joins the refrigerant flow on the outlet side of the accumulator 20, the balanced state of the refrigerant on the outlet side of the first chiller 18 will always be in the state of near saturated gas with a dryness of 1. This is because it can be maintained.
  • a hot gas heating mode is included as an operation mode of the refrigeration cycle 10 according to the first embodiment.
  • the hot gas heating mode is an operation mode for effectively using the heat generated by the work of the compressor 11 to heat the heat medium.
  • An example of the hot gas heating mode will be described.
  • the control device 70 puts the high-stage expansion valve 14, the first expansion valve 17a, and the bypass-side flow control valve 22 into throttled states, and puts the second expansion valve 17b into a fully closed state. .
  • the refrigerant includes the compressor 11, the first three-way joint 12a, the heat medium refrigerant heat exchanger 13, the high-stage expansion valve 14, the gas-liquid separator 15, the first expansion valve 17a, the first The chiller 18, the second three-way joint 12b, the accumulator 20, and the compressor 11 are circulated in this order.
  • the refrigerant circulates through the compressor 11, the first three-way joint 12a, the heat medium refrigerant heat exchanger 13, the high stage expansion valve 14, the gas-liquid separator 15, the intermediate pressure refrigerant passage 23, and the compressor 11 in this order.
  • the refrigerant circulates through the compressor 11, the first three-way joint 12a, the bypass side flow control valve 22, the second three-way joint 12b, the accumulator 20, and the compressor 11 in this order. That is, in the hot gas heating mode refrigeration cycle, the three refrigerant circulation circuits are switched so that they coexist.
  • the state change of the refrigerant in the hot gas heating mode will be explained.
  • the flow of discharged refrigerant discharged from the compressor 11 is first branched at the first three-way joint 12a.
  • One of the refrigerants branched at the first three-way joint 12a flows into the heat medium refrigerant heat exchanger 13 and is radiated by the heat medium flowing through the heat medium passage 13b. The heat medium is thereby heated.
  • the refrigerant that has flowed out of the heat medium refrigerant heat exchanger 13 is isoenthalpically decompressed and expanded until it becomes an intermediate pressure refrigerant by the high-stage expansion valve 14 in the throttled state.
  • the intermediate-pressure refrigerant decompressed by the high stage expansion valve 14 is separated into gas and liquid by the gas-liquid separator 15 .
  • the gas-phase refrigerant separated by the gas-liquid separator 15 flows through the intermediate-pressure refrigerant passage 23 into the intermediate-pressure port 11b of the compressor 11, and joins the refrigerant discharged from the low-stage compression mechanism of the compressor 11. Then, it is sucked into the high stage side compression mechanism.
  • the liquid-phase refrigerant separated by the gas-liquid separator 15 passes through the first It flows into the expansion valve 17a.
  • the refrigerant that has flowed into the first expansion valve 17a is isoenthalpically decompressed.
  • the relatively low enthalpy refrigerant flowing out of the first expansion valve 17 a flows into the first chiller 18 .
  • the heating medium passage 13b of the first chiller 18 is controlled so that the heating medium does not flow. Therefore, the refrigerant that has flowed into the first chiller 18 flows into the other inlet of the second three-way joint 12b without exchanging heat with the heat medium when flowing through the refrigerant passage.
  • the other refrigerant branched at the first three-way joint 12 a flows into the bypass passage 21 .
  • the flow rate of the refrigerant that has flowed into the bypass passage 21 is adjusted by the bypass side flow control valve 22 and the pressure is reduced.
  • the refrigerant with a relatively high enthalpy decompressed by the bypass-side flow control valve 22 flows into one inlet of the second three-way joint 12b.
  • the refrigerant flowing out of the bypass side flow control valve 22 and the refrigerant flowing out of the first chiller 18 are mixed at the second three-way joint 12b.
  • the refrigerant that has flowed out of the second three-way joint 12 b flows into the accumulator 20 .
  • the gas-phase refrigerant separated by the accumulator 20 is sucked into the compressor 11 and compressed again.
  • the heat generated by the work of the compressor 11 can be effectively used to heat the heat medium without radiating the heat of the high-pressure refrigerant to the outside air.
  • a plurality of evaporators that is, the first chiller 18 and the second chiller 19 are used to blow air, the battery B, and the vehicle-mounted equipment through the heat medium circulating in the heat medium circuit 30.
  • an operation mode in which heat is absorbed from a cooling target such as outside air multiple chiller cooling mode, multiple chiller battery cooling mode, multiple chiller waste heat recovery mode, multiple chiller outside air heat absorption mode, cooling & battery cooling mode, dehumidification heating & waste Includes heat recovery mode, dehumidification heating & outside air heat absorption mode.
  • the operation mode of the refrigeration cycle 10 is such that heat is absorbed from the heat medium to the refrigerant in each of the first chiller 18 and the second chiller 19, and heat is This is an operation mode in which heat is radiated by the medium-refrigerant heat exchanger 13 .
  • the refrigerant in the refrigeration cycle 10 includes the compressor 11, the heat medium refrigerant heat exchanger 13, the high-stage expansion valve 14, the gas-liquid separator 15, the throttled first expansion valve 17a, the first chiller 18, and the accumulator. 20 and the compressor 11 in order to circulate.
  • the refrigerant flows through the compressor 11, the heat medium refrigerant heat exchanger 13, the high-stage expansion valve 14, the gas-liquid separator 15, the throttled second expansion valve 17b, the second chiller 19, and the compressor 11 in this order. circulating.
  • the multi-chiller cooling mode which is one of the operation modes in which heat is absorbed from an object to be cooled using a plurality of evaporators, will be described with reference to FIG.
  • the multiple chiller cooling mode is an operation mode for cooling the passenger compartment with higher performance by utilizing the cooling performance of the first chiller 18 and the second chiller 19 to absorb heat from the air to be cooled. be.
  • control device 70 controls the first pump 37 to the fourth pump 40 to exert their respective pumping capabilities. In addition, the control device 70 controls the operation of the first five-way valve 41 to the third five-way valve 43 and the four-way valve 44, and regulates the flow of the heat medium so that the circuit configuration is suitable for the multiple chiller cooling mode. Control.
  • the control device 70 controls such that the heat medium flowing in from the first inlet/outlet 41a flows out from the fourth inlet/outlet 41d. At this time, the control device 70 fully closes the second inlet/outlet 41b, the third inlet/outlet 41c, and the fifth inlet/outlet 41e so that the heat medium does not flow into or out of the first five-way valve 41 .
  • the control device 70 controls the heat medium flowing in from the third inlet/outlet 42c to flow out from the first inlet/outlet 42a. At this time, the control device 70 fully closes the second inlet/outlet 42b, the fourth inlet/outlet 42d, and the fifth inlet/outlet 42e so that the heat medium does not flow into or out of the second five-way valve 42 .
  • the control device 70 controls such that the heat medium flowing in from the fifth inlet/outlet 43e flows out from the second inlet/outlet 43b. At this time, the controller 70 fully closes the first inflow/outlet 43a, the third inflow/outlet 43c, and the fourth inflow/outlet 43d so that the heat medium does not flow into or out of the third five-way valve 43 .
  • the control device 70 controls such that the heat medium flowing in from the third inlet/outlet 44c flows out from the first inlet/outlet 44a and the fourth inlet/outlet 44d.
  • the flow rate ratio of the heat medium flowing out from the first inlet/outlet 44a and the heat medium flowing out from the fourth inlet/outlet 44d is determined according to the cooling capacities of the first chiller 18 and the second chiller 19. For example, the refrigeration cycle 10 It is determined so as to maximize the cooling capacity as a whole. Then, the control device 70 fully closes the second inlet/outlet 44 b so that the heat medium does not flow into or out of the four-way valve 44 .
  • the heat medium is the first pump 37, the first chiller 18, the second connection portion 45b, the first connection portion 45a, the cooler core 31, the four-way valve 44, the first pump It flows and circulates in the order of 37.
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • a heat medium circulation circuit is configured in which the first chiller 18 and the second chiller 19 are connected in parallel to the cooler core 31 . Therefore, in the multiple chiller cooling mode, the blown air can be cooled with a higher cooling capacity than when either the first chiller 18 or the second chiller 19 is used, and the comfort of the passenger compartment can be quickly improved by cooling. can be enhanced.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection portion 45h, the ninth connection portion 45i, It flows in the order of the third five-way valve 43 . Then, when the heat medium flows out from the third five-way valve 43, the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, the second five-way valve 42, the seventh connection portion 45g, the fourth pump It flows in order of 40.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the equipment heat exchange unit 33 circulates through the outside air heat exchanger 34. be. Therefore, according to the multi-chiller cooling mode, the heat pumped up by the refrigerating cycle 10 and the waste heat generated in the in-vehicle equipment can be transported via the heat medium and radiated to the outside air.
  • the multiple chiller battery cooling mode utilizes the cooling performance of the first chiller 18 and the second chiller 19 to absorb heat from the battery B to be cooled, thereby cooling the battery B with higher performance.
  • the multiple chiller battery cooling mode is effective, for example, when the amount of heat generated by the battery B increases due to rapid charging of the battery B, and the cooling capacity of the first chiller 18 or the second chiller 19 alone is insufficient. .
  • control device 70 controls the first pump 37 to the fourth pump 40 to exert their respective pumping capabilities. In addition, the control device 70 controls the operation of the first five-way valve 41 to the third five-way valve 43 and the four-way valve 44 so that the circuit configuration is suitable for the multiple chiller battery cooling mode. to control.
  • the control device 70 controls such that the heat medium flowing in from the first inlet/outlet 41a flows out from the fourth inlet/outlet 41d and flows in from the third inlet/outlet 41c.
  • the heat medium is controlled to flow out from the second inlet/outlet 41b.
  • the control device 70 fully closes the fifth inlet/outlet 41 e so that the heat medium does not flow into or out of the first five-way valve 41 .
  • the control device 70 controls the heat medium flowing in from the third inlet/outlet 42c to flow out from the first inlet/outlet 42a, and controls the heat medium flowing in from the fifth inlet/outlet 42e.
  • the medium is controlled to flow out from the second inlet/outlet 42b.
  • the controller 70 fully closes the fourth inlet/outlet 42d so that the heat medium does not flow into or out of the second five-way valve 42 .
  • the control device 70 controls such that the heat medium flowing in from the fifth inlet/outlet 43e flows out from the second inlet/outlet 43b. At this time, the controller 70 fully closes the first inflow/outlet 43a, the third inflow/outlet 43c, and the fourth inflow/outlet 43d so that the heat medium does not flow into or out of the third five-way valve 43 .
  • the control device 70 controls such that the heat medium flowing in from the second inlet/outlet 44b flows out from the first inlet/outlet 44a and the fourth inlet/outlet 44d.
  • the flow rate ratio of the heat medium flowing out from the first inlet/outlet 44a and the heat medium flowing out from the fourth inlet/outlet 44d is determined according to the cooling capacity of the first chiller 18 and the second chiller 19, for example. Then, the control device 70 fully closes the third inlet/outlet 44 c so that the heat medium does not flow into or out of the four-way valve 44 .
  • the heat medium is the first pump 37, the first chiller 18, the second connection portion 45b, the first five-way valve 41, the third connection portion 45c, the battery heat exchange portion 32, the second fifth The flow circulates through the one-way valve 42, the sixth connection portion 45f, the four-way valve 44, and the first pump 37 in this order.
  • the heat medium flows through the second pump 38, the second chiller 19, the first connection portion 45a, the second connection portion 45b, the first five-way valve 41, the third connection portion 45c, the battery heat exchange portion 32, the second It flows and circulates through the five-way valve 42, the sixth connection portion 45f, the four-way valve 44, and the second pump 38 in this order.
  • a heat medium circulation circuit is configured in which the first chiller 18 and the second chiller 19 are connected in parallel to the battery heat exchange section 32 . Therefore, in the multiple chiller battery cooling mode, the battery B can be cooled with a higher cooling capacity than when either the first chiller 18 or the second chiller 19 is used, and the amount of heat generated increases due to rapid charging and the like. Battery B can be cooled quickly even in such a case.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the outside air heat exchanger 34, the eighth connecting portion 45h, the ninth connecting portion 45i. , the third five-way valve 43 . Then, when the heat medium flows out from the third five-way valve 43, the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, the second five-way valve 42, the seventh connection portion 45g, the fourth pump It flows in order of 40.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the equipment heat exchange unit 33 circulates through the outside air heat exchanger 34. be done. Therefore, according to the multiple chiller battery cooling mode, the heat pumped up by the refrigerating cycle 10 and the waste heat generated in the vehicle-mounted equipment can be transported via the heat medium and released to the outside air.
  • the multiple chiller waste heat recovery mode utilizes the cooling performance of the first chiller 18 and the second chiller 19 to absorb heat from the onboard equipment to be cooled, thereby recovering the waste heat of the onboard equipment with higher performance. is the operating mode of
  • control device 70 controls the first pump 37 to the fourth pump 40 to exhibit the pumping capacity determined for each.
  • control device 70 controls the operation of the first five-way valve 41 to the third five-way valve 43 and the four-way valve 44 so that the circuit configuration is suitable for the multiple chiller waste heat recovery mode. control the flow.
  • the control device 70 controls the heat medium flowing in from the first inlet/outlet 41a to flow out from the fifth inlet/outlet 41e, and the heat medium from the third inlet/outlet 41c.
  • the heat medium is controlled to flow out from the second inlet/outlet 41b.
  • the controller 70 fully closes the fourth inlet/outlet 41 d so that the heat medium does not flow into or out of the first five-way valve 41 .
  • the control device 70 controls the heat medium flowing in from the third inlet/outlet 42c to flow out from the first inlet/outlet 42a. At this time, the control device 70 fully closes the first inlet/outlet 42a, the fourth inlet/outlet 42d, and the fifth inlet/outlet 42e so that the heat medium does not flow into or out of the second five-way valve 42 .
  • the control device 70 controls such that the heat medium flowing in from the fifth inflow/outlet 43e flows out from the fourth inflow/outlet 43d, and the heat medium flowing in from the third inflow/outlet 43c flows out from the fourth inflow/outlet 43d. It is controlled to flow out from the second inflow/outlet 43b. At this time, the control device 70 fully closes the first inlet/outlet 43 a so that the heat medium does not flow into or out of the third five-way valve 43 .
  • the control device 70 controls such that the heat medium flowing in from the second inlet/outlet 44b flows out from the first inlet/outlet 44a and the fourth inlet/outlet 44d.
  • the flow rate ratio of the heat medium flowing out from the first inlet/outlet 44a and the heat medium flowing out from the fourth inlet/outlet 44d is determined according to the cooling capacity of the first chiller 18 and the second chiller 19, for example. Then, the control device 70 fully closes the third inlet/outlet 44 c so that the heat medium does not flow into or out of the four-way valve 44 .
  • the heat medium is the first pump 37, the first chiller 18, the second connection 45b, the first five-way valve 41, the third connection 45c, the third five-way valve 43, the fifth It flows through the connecting portion 45e and the third pump 39 in this order. Then, when the heat medium flows out from the third pump 39, it flows through the equipment heat exchange portion 33, the second five-way valve 42, the sixth connection portion 45f, the four-way valve 44, and the first pump 37 in this order and circulates.
  • the heat medium flows through the second pump 38, the second chiller 19, the first connection portion 45a, the second connection portion 45b, the first five-way valve 41, the third connection portion 45c, the third five-way valve 43, the fifth It flows through the connecting portion 45e and the third pump 39 in this order.
  • the heat medium flows out from the third pump 39, the heat medium flows through the equipment heat exchange portion 33, the second five-way valve 42, the sixth connection portion 45f, the four-way valve 44, and the second pump 38 in this order and circulates.
  • a heat medium circulation circuit is configured in which the first chiller 18 and the second chiller 19 are connected in parallel to the equipment heat exchange section 33 . Therefore, in the multi-chiller waste heat recovery mode, the waste heat of the vehicle-mounted equipment can be recovered with a higher cooling capacity than when either the first chiller 18 or the second chiller 19 is used.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connecting portion 45i, the third fifth The flow circulates through the direction valve 43, the seventh connecting portion 45g, and the fourth pump 40 in this order.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the electric heater 36 circulates through the heater core 35 . Therefore, according to the multiple chiller waste heat recovery mode, the heat pumped up by the refrigeration cycle 10 and the heat applied by the electric heater 36 can be used to heat the blast air. In this case, since the heat pumped up by the refrigeration cycle 10 also includes the waste heat of the on-vehicle equipment recovered by the equipment heat exchange unit 33, the waste heat of the on-vehicle equipment is used to heat the vehicle interior. It can be performed.
  • the multiple chiller outside air heat absorption mode utilizes the cooling performance of the first chiller 18 and the second chiller 19 to absorb heat from the outside air, which is the object of cooling, so that the heat absorbed from the outside air is effectively used with higher performance. is the operating mode of
  • the control device 70 controls the first pump 37, the second pump 38, and the fourth pump 40 to exert their predetermined pumping capabilities. Note that the control device 70 stops the third pump 39 . In addition, the control device 70 controls the operation of the first five-way valve 41, the third five-way valve 43, and the four-way valve 44 so that the circuit configuration is suitable for the multiple chiller outside air heat absorption mode. to control.
  • the control device 70 controls the heat medium flowing in from the first inlet/outlet 41a to flow out from the fifth inlet/outlet 41e, and the heat medium from the third inlet/outlet 41c.
  • the heat medium is controlled to flow out from the fourth inlet/outlet 41d.
  • the control device 70 fully closes the second inlet/outlet 41 b so that the heat medium does not flow into or out of the first five-way valve 41 .
  • the control device 70 controls the heat medium flowing in from the fifth inlet/outlet 43e to flow out from the fourth inlet/outlet 43d. At this time, the control device 70 fully closes the first inlet/outlet 43a, the second inlet/outlet 43b, and the third inlet/outlet 43c so that the heat medium does not flow into or out of the third five-way valve 43 .
  • the control device 70 controls the heat medium flowing in from the second inlet/outlet 44b to flow out from the first inlet/outlet 44a and the fourth inlet/outlet 44d.
  • the flow rate ratio of the heat medium flowing out from the first inlet/outlet 44a and the heat medium flowing out from the fourth inlet/outlet 44d is determined according to the cooling capacity of the first chiller 18 and the second chiller 19, for example. Then, the control device 70 fully closes the third inlet/outlet 44 c so that the heat medium does not flow into or out of the four-way valve 44 .
  • the heat medium is the first pump 37, the first chiller 18, the second connection part 45b, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection part 45h, and the sixth connection part. 45f, the four-way valve 44, and the first pump 37 in order to circulate.
  • the heat medium flows through the second pump 38, the second chiller 19, the first connection portion 45a, the second connection portion 45b, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection portion 45h, the sixth connection It flows and circulates through the portion 45f, the four-way valve 44, and the second pump 38 in this order.
  • a heat medium circulation circuit is configured in which the first chiller 18 and the second chiller 19 are connected in parallel to the outside air heat exchanger 34 . Therefore, in the multi-chiller outside air heat absorption mode, the outside air heat exchanger 34 performs heat exchange between the heat medium cooled with a higher cooling capacity than when either the first chiller 18 or the second chiller 19 is used, and the outside air. Since it is performed at , the outside air can be effectively used as a heat source.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connecting portion 45i, the third fifth The flow circulates through the direction valve 43, the seventh connecting portion 45g, and the fourth pump 40 in this order.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the electric heater 36 circulates through the heater core 35 . Therefore, according to the multiple chiller outside air heat absorption mode, the heat pumped up by the refrigeration cycle 10 and the heat applied by the electric heater 36 can be used to heat the blast air.
  • the heat pumped up by the refrigerating cycle 10 includes the heat absorbed from the outside air by the outside air heat exchanger 34, so that the inside of the vehicle can be heated using the outside air as a heat source.
  • the multiple chiller cooling mode, the multiple chiller battery cooling mode, the multiple chiller waste heat recovery mode, and the multiple chiller outside air heat absorption mode correspond to examples of the first cooling mode and the second cooling mode in the present disclosure.
  • the multiple chiller cooling mode is the first cooling mode
  • the multiple chiller battery cooling mode, the multiple chiller waste heat recovery mode, and the multiple chiller outside air heat absorption mode correspond to the second cooling mode.
  • the blowing air, the battery B, the vehicle-mounted equipment, and the outside air which are the cooling targets in the multiple chiller cooling mode, the multiple chiller battery cooling mode, the multiple chiller waste heat recovery mode, and the multiple chiller outside air heat absorption mode, are the first cooling targets in the present disclosure, It corresponds to an example of the second object to be cooled. That is, if one of the blown air, the battery B, the vehicle-mounted device, and the outside air is taken as the first object to be cooled, any one of the remaining objects to be cooled corresponds to the second object to be cooled.
  • the cooling performance of the plurality of evaporators is combined into one object to be cooled, such as the multiple chiller cooling mode described above.
  • Other operation modes are included in addition to the concentrated operation mode.
  • an operation mode for absorbing heat from a cooling object using multiple evaporators there is an operation mode for cooling by allocating the cooling performance of multiple evaporators to multiple cooling objects.
  • An operation mode in which the cooling performance of a plurality of evaporators is allocated to a plurality of objects to be cooled, respectively, will be described below with reference to the drawings.
  • the cooling & battery cooling mode will be described with reference to FIG.
  • the cooling performance of the first chiller 18 and the second chiller 19 is allocated to the battery B and the air to be cooled, respectively, and the cooling of the passenger compartment and the cooling of the battery B are performed in parallel. mode.
  • control device 70 controls the first to fourth pumps 37 to 40 to exert their respective pumping capabilities. In addition, the control device 70 controls the operation of the first five-way valve 41 to the third five-way valve 43 and the four-way valve 44 so that the circuit configuration is suitable for the cooling & battery cooling mode. to control.
  • the control device 70 controls such that the heat medium flowing in from the first inlet/outlet 41a flows out from the fourth inlet/outlet 41d and flows in from the third inlet/outlet 41c.
  • the heat medium is controlled to flow out from the second inlet/outlet 41b.
  • the control device 70 fully closes the fifth inlet/outlet 41 e so that the heat medium does not flow into or out of the first five-way valve 41 .
  • the control device 70 controls the heat medium flowing in from the third inlet/outlet 42c to flow out from the first inlet/outlet 42a, and controls the heat medium flowing in from the fifth inlet/outlet 42e.
  • the medium is controlled to flow out from the second inlet/outlet 42b.
  • the controller 70 fully closes the fourth inlet/outlet 42d so that the heat medium does not flow into or out of the second five-way valve 42 .
  • the control device 70 controls the heat medium flowing in from the fifth inlet/outlet 43e to flow out from the second inlet/outlet 43b. At this time, the controller 70 fully closes the first inflow/outlet 43a, the third inflow/outlet 43c, and the fourth inflow/outlet 43d so that the heat medium does not flow into or out of the third five-way valve 43 .
  • control device 70 controls the heat medium flowing in from the second inflow/outlet 44b to flow out from the first inflow/outlet 44a, and controls the heat medium flowing in from the third inflow/outlet 44c to flow out from the third inflow/outlet 44c. 4 Control to flow out from the inflow/outlet 44d.
  • the heat medium is the first pump 37, the first chiller 18, the second connection part 45b, the first five-way valve 41, the third connection part 45c, the battery heat exchange part 32, the fourth connection 45d, the second five-way valve 42, the sixth connection portion 45f, the four-way valve 44, and the first pump 37 in this order.
  • the heat medium cooled by the first chiller 18 circulates through the battery heat exchange section 32 , so the batteries B can be cooled by the cooling performance of the first chiller 18 .
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • the heat medium cooled by the second chiller 19 circulates through the cooler core 31, so that the cooling performance of the second chiller 19 cools the blown air to cool the passenger compartment. can.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection portion 45h, and the ninth connection portion 45i. , the third five-way valve 43 . Then, when the heat medium flows out from the third five-way valve 43, the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, the second five-way valve 42, the seventh connection portion 45g, the fourth pump 40 flows and circulates.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the equipment heat exchange unit 33 circulates through the outside air heat exchanger 34. be done. Therefore, in the cooling & battery cooling mode, the heat pumped up by the refrigerating cycle 10 and the waste heat generated in the in-vehicle equipment can be transported through the heat medium and radiated to the outside air.
  • the dehumidification heating & waste heat recovery mode will be described with reference to FIG.
  • the cooling performance of the first chiller 18 and the second chiller 19 is assigned to the on-vehicle equipment to be cooled and the blowing air, respectively, to dehumidify the vehicle interior and recover waste heat from the on-board equipment. This is a parallel operation mode.
  • the control device 70 controls the first pump 37 to the fourth pump 40 to exert their predetermined pumping capabilities. In addition, the control device 70 controls the operation of the first five-way valve 41 to the third five-way valve 43 and the four-way valve 44 so that the circuit configuration is suitable for the dehumidification heating & waste heat recovery mode. to control the flow of
  • the control device 70 controls the heat medium flowing in from the first inlet/outlet 41a to flow out from the fifth inlet/outlet 41e, and the heat medium from the third inlet/outlet 41c.
  • the heat medium is controlled to flow out from the second inlet/outlet 41b.
  • the controller 70 fully closes the fourth inlet/outlet 41 d so that the heat medium does not flow into or out of the first five-way valve 41 .
  • the control device 70 controls the heat medium flowing in from the third inlet/outlet 42c to flow out from the second inlet/outlet 42b. At this time, the control device 70 fully closes the first inlet/outlet 42a, the fourth inlet/outlet 42d, and the fifth inlet/outlet 42e so that the heat medium does not flow into or out of the second five-way valve 42 .
  • the control device 70 controls the heat medium flowing in from the fifth inlet/outlet 43e to flow out from the fourth inlet/outlet 43d, and the heat medium flowing in from the third inlet/outlet 43c. It is controlled to flow out from the second inflow/outlet 43b. At this time, the control device 70 fully closes the first inlet/outlet 43 a so that the heat medium does not flow into or out of the third five-way valve 43 .
  • control device 70 controls the heat medium flowing in from the second inflow/outlet 44b to flow out from the first inflow/outlet 44a, and controls the heat medium flowing in from the third inflow/outlet 44c to flow out from the third inflow/outlet 44c. 4 Control to flow out from the inflow/outlet 44d.
  • the heat medium is the first pump 37, the first chiller 18, the second connection portion 45b, the first five-way valve 41, the third connection portion 45c, the third five-way valve 43, the third 5 connecting portion 45e and the third pump 39 in this order. Then, when the heat medium flows out from the third pump 39, it flows through the equipment heat exchange portion 33, the second five-way valve 42, the sixth connection portion 45f, the four-way valve 44, and the first pump 37 in this order and circulates.
  • the heat medium cooled by the first chiller 18 circulates through the equipment heat exchange section 33, so that the cooling performance of the first chiller 18 cools the onboard equipment and The waste heat generated in can be recovered.
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • the heat medium cooled by the second chiller 19 circulates through the cooler core 31, so that the cooling performance of the second chiller 19 can dehumidify the blown air.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connection part 45i, the third It flows and circulates through the five-way valve 43, the seventh connecting portion 45g, and the fourth pump 40 in this order.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the electric heater 36 circulates through the heater core 35 . Therefore, according to the dehumidification heating & waste heat recovery mode, the heat pumped up by the refrigeration cycle 10 and the heat applied by the electric heater 36 can be used to heat the blast air dehumidified by the cooler core 31 . In this case, since the heat pumped up by the refrigerating cycle 10 also includes the waste heat of the vehicle-mounted equipment recovered by the equipment heat exchange section 33, the waste heat of the vehicle-mounted equipment is used to dehumidify the vehicle interior. Heating can be done.
  • the dehumidification heating & outdoor air heat absorption mode will be described with reference to FIG.
  • the cooling performance of the first chiller 18 and the second chiller 19 is allocated to the outside air and blowing air that are the cooling objects, respectively, and the operation in which the dehumidification of the passenger compartment and the heat absorption from the outside air are performed in parallel. mode.
  • the control device 70 controls the first pump 37, the second pump 38, and the fourth pump 40 to exhibit their predetermined pumping capabilities. Note that the control device 70 stops the third pump 39 . In addition, the control device 70 controls the operation of the first five-way valve 41, the third five-way valve 43, and the four-way valve 44 so that the circuit configuration is suitable for the dehumidification heating & waste heat recovery mode. to control the flow of
  • the control device 70 controls the heat medium flowing in from the first inlet/outlet 41a to flow out from the fifth inlet/outlet 41e, and the heat medium from the third inlet/outlet 41c.
  • the heat medium is controlled to flow out from the fourth inlet/outlet 41d.
  • the control device 70 fully closes the second inlet/outlet 41 b so that the heat medium does not flow into or out of the first five-way valve 41 .
  • the control device 70 controls the heat medium flowing in from the fifth inlet/outlet 43e to flow out from the fourth inlet/outlet 43d. At this time, the control device 70 fully closes the first inlet/outlet 43a, the second inlet/outlet 43b, and the third inlet/outlet 43c so that the heat medium does not flow into or out of the third five-way valve 43 .
  • control device 70 controls the heat medium flowing in from the second inflow/outlet 44b to flow out from the first inflow/outlet 44a, and controls the heat medium flowing in from the third inflow/outlet 44c to flow out from the third inflow/outlet 44c. 4 Control to flow out from the inflow/outlet 44d.
  • the heat medium is the first pump 37, the first chiller 18, the second connection part 45b, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection part 45h, the sixth connection It flows and circulates through the portion 45f, the four-way valve 44, and the first pump 37 in this order.
  • the heat medium cooled by the first chiller 18 circulates through the outside air heat exchanger 34 , so that the first chiller 18 can absorb heat from the outside air due to the cooling performance of the first chiller 18 .
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • the heat medium cooled by the second chiller 19 circulates through the cooler core 31, so that the cooling performance of the second chiller 19 can dehumidify the blown air.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connection part 45i, the third fifth
  • the flow circulates through the direction valve 43, the seventh connecting portion 45g, and the fourth pump 40 in this order.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the electric heater 36 circulates through the heater core 35 . Therefore, according to the dehumidifying heating & outside air heat absorbing mode, the heat pumped up by the refrigerating cycle 10 and the heat applied by the electric heater 36 can be used to heat the blast air dehumidified by the cooler core 31 . In this case, since the heat pumped up by the refrigerating cycle 10 also includes the heat absorbed from the outside air by the outside air heat exchanger 34, the inside of the vehicle can be dehumidified and heated using the outside air as a heat source.
  • the first chiller 18 cools one object to be cooled
  • the second chiller 19 cools another object. is cooling the object to be cooled. That is, the cooling & battery cooling mode, the dehumidifying heating & waste heat recovery mode, and the dehumidifying heating & outside air heat absorption mode each correspond to an example of the combined mode.
  • the refrigeration cycle device 1 there are multiple chiller cooling modes, cooling & battery cooling modes, and the like as operation modes for cooling the blown air blown into the vehicle interior.
  • the cooling performance of the first chiller 18 and the second chiller 19 is used to cool the blown air
  • the cooling & battery cooling mode either the first chiller 18 or the second chiller 19
  • the cooling performance of is used to cool the blast air.
  • the cooling performance used for cooling the blast air which is the object to be cooled, can be adjusted to the evaporator. It can be adjusted in units.
  • switching to the multiple chiller cooling mode allows the required It is possible to ensure a cooling performance that is suitable for the vehicle, and to improve the comfort of the vehicle interior.
  • the refrigeration cycle device 1 as operation modes for cooling the battery B, it has a multiple chiller battery cooling mode, a cooling & battery cooling mode, and the like.
  • the multiple chiller battery cooling mode the battery B is cooled using the cooling performance of the first chiller 18 and the second chiller 19, and in the cooling & battery cooling mode, either the first chiller 18 or the second chiller 19 Cooling of the battery B is performed by utilizing one of the cooling performances.
  • the cooling performance used for cooling the battery B to be cooled can be adjusted for each evaporator by selectively using the multiple chiller battery cooling mode, the cooling & battery cooling mode, and the like. .
  • the cooling performance of a single evaporator for example, the second chiller 19
  • the required cooling performance can be secured. For example, even if the amount of heat generated by the battery B increases due to rapid charging or the like, the refrigeration cycle device 1 can cool the battery B and adjust it to an appropriate temperature range by switching to the multiple chiller battery cooling mode.
  • the refrigeration cycle device 1 there are multiple chiller waste heat recovery mode and dehumidification heating & waste heat recovery mode as operation modes for cooling the in-vehicle equipment.
  • the cooling performance of the first chiller 18 and the second chiller 19 is used to recover waste heat from onboard equipment.
  • the cooling performance of either the first chiller 18 or the second chiller 19 is used to recover waste heat from the vehicle-mounted equipment.
  • the cooling performance used for recovering waste heat from the in-vehicle equipment to be cooled can be adjusted for each evaporator. can be adjusted.
  • the cooling performance of a single evaporator for example, the first chiller 18
  • the required capacity can be secured.
  • the refrigeration cycle device 1 there are a multiple chiller outside air heat absorption mode and a dehumidification heating & outside air heat absorption mode as operation modes for cooling the outside air.
  • the cooling performance of the first chiller 18 and the second chiller 19 is used to absorb the heat of the outdoor air.
  • the cooling performance of either the first chiller 18 or the second chiller 19 is used to absorb the heat of the outside air.
  • the cooling performance used for absorbing heat from the outside air, which is the object to be cooled can be adjusted for each evaporator.
  • the refrigerating cycle device 1 has the refrigerating cycle 10 and the heat medium circuit 30, and can cool a plurality of objects to be cooled, such as the blown air, the battery B, the in-vehicle equipment, and the outside air. It is configured.
  • the refrigerating cycle 10 has a compressor 11 , a heat medium refrigerant heat exchanger 13 , a first expansion valve 17 a , a second expansion valve 17 b , a first chiller 18 and a second chiller 19 .
  • the heat medium circuit 30 includes a cooler core 31 as a cooling part for cooling the blown air, a battery heat exchange part 32 as a cooling part for cooling the battery B, and a cooling part for recovering waste heat from the vehicle equipment. It has an equipment heat exchange section 33 as a heat exchanger and an outside air heat exchanger 34 for absorbing heat from the outside air.
  • the heat medium circuit 30 heats the heat medium cooled by at least one of the plurality of chillers (the first chiller 18 and the second chiller 19) to a plurality of It is configured to be able to supply to at least one of the cooling units.
  • the refrigeration cycle apparatus 1 according to the first embodiment, as shown in FIGS. can be supplied to one of the departments. Therefore, the refrigeration cycle device 1 can cool any one of the blown air, the battery B, the in-vehicle equipment, and the outside air using a plurality of evaporators (the first chiller 18 and the second chiller 19). It is possible to improve the cooling performance for a specific object to be cooled.
  • the heat medium circuit 30 includes a cooler core 31, a battery heat exchange section 32, an equipment heat exchange section 33, an outside air heat exchanger 34, and a heat medium flow in the heat medium circuit 30. It has a first five-way valve 41 to a third five-way valve 43 and a four-way valve 44 for switching between.
  • the refrigeration cycle device 1 by controlling the operations of the first five-way valve 41 to the third five-way valve 43 and the four-way valve 44, a plurality of operation modes as shown in FIGS. 4 to 10 are realized. can do. That is, the refrigeration cycle device 1 can supply the heat medium cooled by at least one of the plurality of chillers to at least one of the plurality of cooling units.
  • the refrigeration cycle apparatus 1 can supply the heat medium cooled by the first chiller 18 and the second chiller 19 to the cooler core 31 by switching to the multiple chiller cooling mode. Thereby, the refrigerating cycle apparatus 1 can cool the air in the passenger compartment by using the cooling performance of the first chiller 18 and the second chiller 19 .
  • the refrigerating cycle apparatus 1 is switched to the multiple chiller battery cooling mode to supply the heat medium cooled by the first chiller 18 and the second chiller 19 to the battery heat exchange section 32. can do.
  • the refrigerating cycle device 1 can cool the battery B using the cooling performance of the first chiller 18 and the second chiller 19. For example, when the heat generation amount of the battery B increases during rapid charging, However, cooling performance can be ensured.
  • the refrigerating cycle apparatus 1 switches to the multi-chiller waste heat recovery mode to transfer the heat medium cooled by the first chiller 18 and the second chiller 19 to the equipment heat exchange section 33. can supply.
  • the refrigeration cycle apparatus 1 can utilize the cooling performance of the first chiller 18 and the second chiller 19 to cool the vehicle-mounted equipment and recover the waste heat generated in the vehicle-mounted equipment.
  • the refrigeration cycle apparatus 1 switches to the multiple chiller outside air heat absorption mode to supply the heat medium cooled by the first chiller 18 and the second chiller 19 to the outside air heat exchanger 34. be able to.
  • the refrigeration cycle apparatus 1 can utilize the cooling performance of the first chiller 18 and the second chiller 19 to absorb heat from the outside air and use the absorbed heat as a heat source.
  • the refrigerating cycle device 1 controls the operation of the first five-way valve 41 to the third five-way valve 43 and the four-way valve 44 to perform cooling & battery cooling mode, dehumidification It can be switched to heating & waste heat recovery mode, dehumidification heating & outside air heat absorption mode.
  • the refrigerating cycle apparatus 1 switches to the cooling and battery cooling mode to supply the heat medium that has flowed through the first chiller 18 to the battery heat exchange section 32 and to flow the heat medium through the second chiller 19 .
  • the heated heat medium can be supplied to the cooler core 31 .
  • the refrigeration cycle device 1 can cool the battery B with the cooling performance of the first chiller 18, and at the same time, cool the blown air with the cooling performance of the second chiller 19 to cool the passenger compartment. .
  • the refrigerating cycle device 1 is switched to the dehumidification heating & waste heat recovery mode, thereby supplying the heat medium that has flowed through the first chiller 18 to the equipment heat exchange unit 33 and the second The heat medium that has flowed through the chiller 19 can be supplied to the cooler core 31 .
  • the refrigerating cycle apparatus 1 can use the cooling performance of the first chiller 18 to recover waste heat from the onboard equipment, and use the cooling performance of the second chiller 19 to dehumidify the blown air. can.
  • the refrigerating cycle device 1 switches to the dehumidification heating & outside air heat absorption mode, thereby supplying the heat medium that has flowed through the first chiller 18 to the outside air heat exchanger 34 and the second chiller 19 can be supplied to the cooler core 31.
  • the refrigerating cycle apparatus 1 can use the cooling performance of the first chiller 18 to absorb heat from the outside air, and at the same time can use the cooling performance of the second chiller 19 to dehumidify the blown air.
  • the refrigeration cycle device 1 of the refrigeration cycle 10 has a suction port 11a, an intermediate pressure port 11b and a discharge port 11c. Furthermore, the refrigeration cycle 10 has a gas-liquid separator 15, and the gas-liquid separator 15 separates the gas-liquid refrigerant flowing out of the heat medium-refrigerant heat exchanger 13 into the separated gas-phase refrigerant. It flows out to the intermediate pressure port 11b. That is, the refrigerating cycle 10 can constitute a gas injection cycle.
  • the refrigeration cycle device 1 can improve the compression efficiency of the high-stage compression mechanism by causing the high-stage compression mechanism of the compressor 11 to suck the low-temperature mixed refrigerant. Furthermore, the refrigeration cycle device 1 reduces the pressure difference between the suction refrigerant pressure and the discharge refrigerant pressure of both the low-stage compression mechanism and the high-stage compression mechanism of the compressor 11, thereby increasing the compression efficiency of both compression mechanisms. can be improved. As a result, the COP of the refrigeration cycle 10 as a whole can be improved.
  • the refrigeration cycle apparatus 1 can adjust the cooling performance of the 1st chiller 18 and the cooling performance of the 2nd chiller 19 by simple processing content.
  • the accumulator 20 is arranged between the outlet of the refrigerant passage 18a of the first chiller 18 and the refrigerant junction 16b.
  • the refrigerating cycle device 1 can always maintain the balanced state of the refrigerant at the outlet of the first chiller 18 in the vicinity of the saturated gas with dryness: 1, thereby suppressing the deterioration of the cooling performance of the first chiller 18. can be done.
  • FIG. 11 to 27 The refrigerating cycle device 1 according to the second embodiment differs in configuration from the refrigerating cycle 10 according to the first embodiment, and is configured to enable various operation modes including the operation of the refrigerating cycle 10 .
  • Other configurations of the heat medium circuit 30, the indoor air conditioning unit 60, the control system, and the like in the refrigeration cycle apparatus 1 are the same as those of the above-described embodiment, and thus the description thereof will be omitted.
  • the refrigeration cycle 10 includes a compressor 11, a heat medium refrigerant heat exchanger 13, a high-stage expansion valve 14, a gas-liquid separator 15, a first expansion valve 17a, It has a second expansion valve 17 b , a first chiller 18 , a second chiller 19 and an accumulator 20 .
  • the refrigeration cycle 10 according to the second embodiment has a refrigerant bypass passage 25 and a refrigerant switching valve 26 in addition to the same components as in the first embodiment. Further, in the refrigerating cycle 10 according to the second embodiment, a first refrigerant connection portion 24a and a second refrigerant connection portion 24b are adopted instead of the first three-way joint 12a and the second three-way joint 12b according to the first embodiment. ing.
  • the first refrigerant connection portion 24a has three inlets and outlets communicating with each other, similar to the first three-way joint 12a. One of the three inlets and outlets in the first coolant connection portion 24a is used as an inlet, and the remaining two are used as outlets.
  • the discharge port 11c of the compressor 11 is connected to the inlet of the first refrigerant connection portion 24a.
  • a refrigerant inlet side of the heat medium refrigerant heat exchanger 13 is connected to one outflow port of the first refrigerant connection portion 24a.
  • the bypass passage 21 is connected to the other outflow port of the first refrigerant connection portion 24a.
  • a second refrigerant connection portion 24b is arranged on the outlet side of the refrigerant passage 18a in the first chiller 18 instead of the second three-way joint 12b.
  • the second refrigerant connection portion 24b is formed in the shape of a four-way joint having four inlets and outlets communicating with each other.
  • the outlet side of the refrigerant passage 18a in the first chiller 18 is connected to one of the inlet and outlet ports of the second refrigerant connection portion 24b.
  • the other end of the bypass passage 21 is connected to the other inlet/outlet of the second coolant connection portion 24b.
  • the refrigerant inlet of the accumulator 20 is connected to another inlet/outlet of the second refrigerant connection portion 24b.
  • one end side of the refrigerant bypass passage 25 is connected to yet another inlet/outlet of the second refrigerant connection portion 24b.
  • the other end side of the refrigerant bypass passage 25 is connected to the third refrigerant connection portion 24c.
  • the third refrigerant connection portion 24c is formed in the shape of a three-way joint having three inlets and outlets communicating with each other, similar to the first refrigerant connection portion 24a.
  • One of the inlets and outlets of the third refrigerant connection portion 24c is connected to the other end side of the refrigerant bypass passage 25 as described above.
  • a refrigerant outlet side of the second chiller 19 is connected to another inlet/outlet of the third refrigerant connection portion 24c.
  • the other side of the refrigerant inlet of the refrigerant merging portion 16b is connected to the other inlet/outlet of the third refrigerant connection portion 24c.
  • a refrigerant switching valve 26 is arranged in the refrigerant pipe that connects the third refrigerant connection portion 24c and the refrigerant junction portion 16b.
  • the refrigerant switching valve 26 is an on-off valve that switches whether or not the refrigerant flows in the refrigerant pipe that connects the third refrigerant connection portion 24c and the refrigerant junction portion 16b.
  • the refrigerant bypass passage 25 corresponds to an example of a refrigerant bypass passage
  • the refrigerant switching valve 26 corresponds to an example of a refrigerant switching portion.
  • the circuit configuration of the refrigeration cycle 10 includes a multiple chiller circulation mode in which the refrigerant absorbs heat in the first chiller 18 and the second chiller 19, a first chiller circulation mode in which the refrigerant absorbs heat in the first chiller 18 alone, and a second chiller 19 alone.
  • a second chiller circulation mode is included that allows the refrigerant to absorb heat.
  • the circuit configuration of the refrigeration cycle 10 according to the second embodiment will be described below with reference to the drawings.
  • the process by which the refrigerant discharged from the compressor 11 reaches the refrigerant branching portion 16a is the same as in the above-described first embodiment, so the explanation thereof will be omitted. That is, the multiple chiller circulation mode, the first chiller circulation mode, and the second chiller circulation mode are different in the process until the refrigerant flowing out from the refrigerant branch portion 16a reaches the suction port 11a of the compressor 11. .
  • the refrigerant is made to absorb heat from the heat medium in the first chiller 18 and the second chiller 19 .
  • the control device 70 brings the first expansion valve 17a and the second expansion valve 17b into a predetermined throttle state. Further, the control device 70 opens the refrigerant switching valve 26 .
  • the refrigerant that has flowed out of one of the outlets of the refrigerant branch portion 16a is decompressed by the first expansion valve 17a, absorbs heat from the heat medium flowing through the heat medium passage 18b in the first chiller 18, and 2 to the refrigerant connecting portion 24b.
  • the refrigerant flowing out from the other outlet of the refrigerant branch portion 16a absorbs heat from the heat medium flowing through the heat medium passage 19b in the second chiller 19.
  • the refrigerant flowing out of the second chiller 19 branches into a flow on the side of the refrigerant bypass passage 25 and a flow on the side of the refrigerant switching valve 26 at the third refrigerant connection portion 24c.
  • the refrigerant that has flowed through the refrigerant bypass passage 25 joins with the refrigerant that has flowed out of the first chiller 18 at the second refrigerant connection portion 24b and flows into the accumulator 20 .
  • the refrigerant separated into gas and liquid in the accumulator 20 flows out to the refrigerant junction 16b.
  • part of the refrigerant branched at the third refrigerant connection portion 24c passes through the refrigerant switching valve 26, bypasses the accumulator 20, and flows into the refrigerant merging portion. 16b.
  • the refrigerant merged at the refrigerant junction 16 b is sucked into the suction port 11 a of the compressor 11 .
  • part of the refrigerant that has flowed into the third refrigerant connection portion 24c can be flowed and circulated so as to bypass the accumulator 20.
  • the cooling capacity in the 1st chiller 18 and the 2nd chiller 19 can be improved rather than the 2nd aspect of multiple chiller circulation mode mentioned later.
  • the control device 70 brings the first expansion valve 17a and the second expansion valve 17b into a predetermined throttle state. In addition, the control device 70 closes the refrigerant switching valve 26 .
  • the refrigerant that has flowed out from one of the outlets of the refrigerant branch portion 16a flows through the first expansion valve 17a, the first chiller 18, and the second refrigerant connection portion 24b in this order.
  • Refrigerant flowing out of the other outlet of the refrigerant branch portion 16a flows through the second expansion valve 17b, the second chiller 19, the third refrigerant connection portion 24c, the refrigerant bypass passage 25, and the second refrigerant connection portion 24b in this order. Since the refrigerant switching valve 26 is closed, all the refrigerant that has passed through the third refrigerant connection portion 24 c passes through the refrigerant bypass passage 25 and reaches the accumulator 20 .
  • the refrigerant flowing out of the first chiller 18 and the refrigerant flowing out of the second chiller 19 join at the second refrigerant connection portion 24 b and flow into the accumulator 20 .
  • the refrigerant separated into gas and liquid in the accumulator 20 flows out to the refrigerant junction 16b.
  • the multiple chiller circulation mode which gave priority to the stability of the refrigerating cycle 10 rather than the cooling capacity in the 1st chiller 18 and the 2nd chiller 19 is realizable.
  • the first chiller 18 allows the refrigerant to absorb heat from the heat medium.
  • the control device 70 brings the first expansion valve 17a into a predetermined throttle state and brings the second expansion valve 17b into a fully closed state. Further, the control device 70 opens the refrigerant switching valve 26 .
  • the refrigerant flowing out from the refrigerant branch portion 16a flows through the first expansion valve 17a, the first chiller 18, and the second refrigerant connection portion 24b in this order.
  • a part of the refrigerant branched at the second refrigerant connection portion 24b flows through the accumulator 20 and the refrigerant junction portion 16b in this order.
  • the remaining portion of the refrigerant branched at the second refrigerant connection portion 24b flows through the refrigerant bypass passage 25, the third refrigerant connection portion 24c, the refrigerant switching valve 26, and the refrigerant junction portion 16b in this order.
  • part of the refrigerant branched at the second refrigerant connection portion 24b passes through the refrigerant switching valve 26, bypasses the accumulator 20, and flows into the refrigerant merging portion. 16b.
  • part of the refrigerant that has flowed into the second refrigerant connection portion 24b can be flowed and circulated so as to bypass the accumulator 20.
  • the cooling capacity of the 1st chiller 18 can be improved compared with the 2nd aspect of 1st chiller circulation mode mentioned later.
  • the first chiller 18 allows the refrigerant to absorb heat from the heat medium.
  • the control device 70 brings the first expansion valve 17a into a predetermined throttle state and brings the second expansion valve 17b into a fully closed state.
  • the control device 70 closes the refrigerant switching valve 26 .
  • the refrigerant flowing out of the refrigerant branch portion 16a flows through the first expansion valve 17a, the first chiller 18, the second refrigerant connection portion 24b, the accumulator 20, and the refrigerant junction portion 16b in this order.
  • the refrigerant switching valve 26 since the refrigerant switching valve 26 is in the closed state, the refrigerant does not branch to the refrigerant bypass passage 25 side at the second refrigerant connection portion 24b, and the entire amount of refrigerant flows from the second refrigerant connection portion 24b to the accumulator 20 side. flow out to
  • the second chiller circulation mode in the refrigeration cycle 10 according to the second embodiment will be described with reference to FIG.
  • the second chiller 19 allows the refrigerant to absorb heat from the heat medium.
  • the control device 70 brings the second expansion valve 17b into a predetermined throttle state and brings the first expansion valve 17a into a fully closed state. Further, the control device 70 opens the refrigerant switching valve 26 .
  • the accumulator 20 is not included in the circulation path of the refrigerant. If the refrigerating cycle 10 continues to operate in this state, the liquid refrigerant in the accumulator 20 will evaporate and the high pressure of the cycle will increase, which may cause the cycle to collapse.
  • the refrigerant flowing out from the refrigerant branching portion 16a flows through the second expansion valve 17b, the second chiller 19, the third refrigerant connection portion 24c, the refrigerant bypass passage 25, the second The refrigerant flows in the order of the refrigerant connection portion 24b, the accumulator 20, and the refrigerant junction portion 16b.
  • a plurality of evaporators can be used to realize an operation mode in which heat is absorbed from one object to be cooled.
  • the cooling capacity of the first chiller 18 and the second chiller 19 in the operation mode of absorbing heat from one object to be cooled using a plurality of evaporators can be changed. can be done.
  • a multiple chiller cooling mode will be taken to explain how to properly use the circuit configuration of the refrigeration cycle 10 .
  • the flow of heat medium in the heat medium circuit 30 is the same as in the first embodiment.
  • the heat medium flows and circulates through the first pump 37, the first chiller 18, the second connecting portion 45b, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the first pump 37 in this order. do.
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • a heat medium circulation circuit is configured in which the first chiller 18 and the second chiller 19 are connected in parallel to the cooler core 31 .
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection portion 45h, the ninth connection portion 45i, It flows in the order of the third five-way valve 43 . Then, when the heat medium flows out from the third five-way valve 43, the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, the second five-way valve 42, the seventh connection portion 45g, the fourth pump It flows in order of 40.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the equipment heat exchange unit 33 circulates through the outside air heat exchanger 34. be. Therefore, according to the multi-chiller cooling mode, the heat pumped up by the refrigerating cycle 10 and the waste heat generated in the in-vehicle equipment can be transported via the heat medium and radiated to the outside air.
  • the refrigeration cycle apparatus 1 switches the circuit configuration of the refrigeration cycle 10 between the first mode and the second mode of the multiple chiller circulation mode. It is possible to realize the cooling capacity according to the situation.
  • the refrigerating cycle device 1 uses the multiple-chiller circulation mode shown in FIG.
  • the first aspect is adopted. This causes a flow in which part of the refrigerant bypasses the accumulator 20, so that the cooling capacity of the first chiller 18 and the second chiller 19 can be improved.
  • the refrigerating cycle device 1 adopts the second aspect of the multiple-chiller circulation mode shown in FIG. to adopt. As a result, all of the refrigerant flowing out of the first chiller 18 and the second chiller 19 passes through the accumulator 20, so that the required cooling capacity can be achieved and the stability of the cycle can be ensured.
  • the cooling capacity is realized according to the situation such as the multiple-chiller cooling mode. be able to.
  • the multiple chiller cooling mode has been described as an example of the operation mode in which heat is absorbed from one object to be cooled using multiple evaporators, the present invention is not limited to this mode. Any operation mode that absorbs heat from one object to be cooled using a plurality of evaporators may be used. Differential use of the aspect and the second aspect may be applied.
  • the refrigeration cycle apparatus 1 as in the first embodiment, it is possible to realize an operation mode in which heat is absorbed from a plurality of objects to be cooled using a plurality of evaporators.
  • the cooling & battery cooling mode will be used to explain how to properly use the circuit configuration of the refrigeration cycle 10 .
  • the flow of the heat medium in the heat medium circuit 30 is the same as in the first embodiment. That is, in the cooling & battery cooling mode, the heat medium is the first pump 37, the first chiller 18, the second connection portion 45b, the first five-way valve 41, the third connection portion 45c, the battery heat exchange portion 32, the second 4 connection portion 45d, second five-way valve 42, sixth connection portion 45f, four-way valve 44, and first pump 37 in this order.
  • the heat medium cooled by the first chiller 18 circulates through the battery heat exchange section 32 , so the batteries B can be cooled by the cooling performance of the first chiller 18 .
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • the heat medium cooled by the second chiller 19 circulates through the cooler core 31, so that the cooling performance of the second chiller 19 cools the blown air to cool the passenger compartment. can.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection portion 45h, and the ninth connection portion 45i. , the third five-way valve 43 . Then, when the heat medium flows out from the third five-way valve 43, the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, the second five-way valve 42, the seventh connection portion 45g, the fourth pump 40 flows and circulates.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the equipment heat exchange unit 33 circulates through the outside air heat exchanger 34. be done. Therefore, in the cooling & battery cooling mode, the heat pumped up by the refrigerating cycle 10 and the waste heat generated in the in-vehicle equipment can be transported through the heat medium and radiated to the outside air.
  • the refrigeration cycle apparatus 1 switches the circuit configuration of the refrigeration cycle 10 between the first mode and the second mode of the multiple chiller circulation mode. It is possible to realize the cooling capacity according to the situation.
  • the refrigeration cycle apparatus 1 switches the circuit configuration of the refrigeration cycle 10 between the first mode and the second mode of the multiple chiller circulation mode. It is possible to realize the cooling capacity according to the situation.
  • the refrigeration cycle device 1 adopts the first aspect of the multiple chiller circulation mode shown in FIG. 12 as the circuit configuration of the refrigeration cycle 10 . This causes a flow in which part of the refrigerant bypasses the accumulator 20, so that the cooling capacity of the first chiller 18 and the second chiller 19 can be improved.
  • the refrigeration cycle device 1 adopts the second aspect of the multiple chiller circulation mode shown in FIG. 13 as the circuit configuration of the refrigeration cycle 10 .
  • the refrigeration cycle device 1 adopts the second aspect of the multiple chiller circulation mode shown in FIG. 13 as the circuit configuration of the refrigeration cycle 10 .
  • the cooling capacity is realized according to the situation such as the cooling & battery cooling mode. can do.
  • the cooling & battery cooling mode has been described as an example of an operation mode in which heat is absorbed from a plurality of objects to be cooled using a plurality of evaporators, the present invention is not limited to this mode. It may be an operation mode that absorbs heat from a plurality of objects to be cooled using a plurality of evaporators, and for the dehumidification heating & waste heat recovery mode and the dehumidification heating & outside air heat absorption mode, the first mode and the second mode of the multiple chiller circulation mode Different modes may be used.
  • the refrigerating cycle device 1 according to the second embodiment is operated in an operation mode in which heat is absorbed from a plurality of objects to be cooled using a plurality of evaporators, depending on environmental conditions surrounding the refrigerating cycle device 1, , it is assumed that any one of the plurality of evaporators does not need to absorb heat.
  • one of a plurality of evaporators is used from an operation mode in which heat is absorbed from a plurality of objects to be cooled using a plurality of evaporators. can shift to an operation mode in which heat is absorbed from one object to be cooled. Further, when one evaporator absorbs heat from one object to be cooled, at least part of the refrigerant that has flowed out of the evaporator is sucked into the compressor 11 by bypassing the accumulator 20. Cooling capacity can be improved.
  • cooling & battery cooling mode an example of an operation mode in which heat is absorbed from a plurality of objects to be cooled using a plurality of evaporators.
  • Two chiller use cooling modes are mentioned and demonstrated.
  • the cooling mode using the second chiller is an operation mode in which the cooling capacity of the second chiller 19 is utilized to cool the vehicle interior. is executed when is no longer needed.
  • the refrigeration cycle 10 operates in the first mode or second mode of the multiple chiller circulation mode. Further, in the cooling & battery cooling mode according to the second embodiment, as described above, the circulation circuit of the heat medium passing through the first chiller 18 and the battery heat exchange unit 32, the second chiller 19 and the cooler core 31 A heat medium circulation circuit is formed. Also, in the heat medium circuit 30, a heat medium circulation circuit passing through the heat medium refrigerant heat exchanger 13, the equipment heat exchange section 33, and the outside air heat exchanger 34 is formed.
  • the refrigeration cycle device 1 switches to the cooling mode using the second chiller. Specifically, the control device 70 fully closes the first expansion valve 17a, closes the refrigerant switching valve 26, and switches the operation of the refrigeration cycle 10 to the second chiller circulation mode shown in FIG. switch.
  • the control device 70 stops the operation of at least the first pump 37 .
  • circulation of the heat medium via the first chiller 18 and the battery heat exchange section 32 is stopped.
  • the refrigeration cycle apparatus 1 has a dehumidification heating mode using the second chiller as an operation mode similar to the cooling mode using the second chiller.
  • the dehumidification heating mode using the second chiller shifts from the operation mode in which the air cooled by one evaporator is heated by the heater core 35, and the heat is absorbed from another object to be cooled by another evaporator. .
  • the dehumidifying heating & outside air heat absorption mode can be mentioned as one of the operation modes that shifts to the dehumidifying heating mode using the second chiller.
  • the dehumidification/heating & outside air heat absorption mode according to the second embodiment will be described with reference to FIG. 20 .
  • the flow of the heat medium in the heat medium circuit 30 is the same as in the first embodiment.
  • the heat medium is the first pump 37, the first chiller 18, the second connection part 45b, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection part 45h, the second 6 connection part 45f, the four-way valve 44, and the first pump 37, in this order, to circulate.
  • the heat medium cooled by the first chiller 18 circulates through the outside air heat exchanger 34 , so that the first chiller 18 can absorb heat from the outside air due to the cooling performance of the first chiller 18 .
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • the heat medium cooled by the second chiller 19 circulates through the cooler core 31, so that the cooling performance of the second chiller 19 can dehumidify the blown air.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connection part 45i, the third fifth
  • the flow circulates through the direction valve 43, the seventh connecting portion 45g, and the fourth pump 40 in this order.
  • a heat medium circulation circuit is configured in which the heat medium that has passed through the heat medium refrigerant heat exchanger 13 and the electric heater 36 circulates through the heater core 35 .
  • the heat absorbed from the outside air by the first chiller 18 can be used to heat the blown air dehumidified by the cooling performance of the second chiller 19, and the dehumidifying heating operation can be realized.
  • the dehumidifying and heating mode using the second chiller is an operation mode that performs dehumidifying and heating in the passenger compartment by utilizing the cooling capacity of the second chiller 19. Executed when the endothermic from is no longer needed.
  • the refrigeration cycle 10 operates in the first mode or second mode of the multiple chiller circulation mode.
  • the heat medium circulation circuit via the first chiller 18 and the outside air heat exchanger 34, the second chiller 19 and the cooler core 31 A heat medium circulation circuit is formed.
  • a heat medium circulation circuit passing through the heat medium refrigerant heat exchanger 13 and the heater core 35 is formed.
  • the refrigeration cycle device 1 switches to the second chiller use dehumidification heating mode. Specifically, the control device 70 fully closes the first expansion valve 17a, closes the refrigerant switching valve 26, and switches the operation of the refrigeration cycle 10 to the second chiller circulation mode shown in FIG. switch.
  • the control device 70 stops the operation of at least the first pump 37 .
  • circulation of the heat medium via the first chiller 18 and the outside air heat exchanger 34 is stopped.
  • the second chiller 19 and the heat medium circulation circuit via the cooler core 31, the heat medium refrigerant heat exchanger 13, the electric heater 36, and the heater core 35 A heat medium circulation circuit is formed.
  • the dehumidification and heating of the passenger compartment using the cooling capacity of the second chiller 19 can be achieved.
  • the dehumidification heating mode using the second chiller since the second chiller circulation mode via the accumulator 20 using the refrigerant bypass passage 25 can be realized, the dehumidification heating mode using the second chiller, which could not be realized in the first embodiment, is realized. be able to.
  • the refrigeration cycle apparatus 1 has a dehumidifying heating & waste heat recovery mode as an operation mode that can shift to the second chiller use dehumidifying heating mode.
  • the dehumidification heating & waste heat recovery mode according to the second embodiment will be described with reference to FIG. 22 .
  • the flow of the heat medium in the heat medium circuit 30 is the same as in the first embodiment.
  • the heat medium is the first pump 37, the first chiller 18, the second connection part 45b, the first five-way valve 41, the third connection part 45c, the third five-way valve 43 , the fifth connecting portion 45e, and the third pump 39 in this order. Then, when the heat medium flows out from the third pump 39, it flows through the equipment heat exchange portion 33, the second five-way valve 42, the sixth connection portion 45f, the four-way valve 44, and the first pump 37 in this order and circulates.
  • the heat medium cooled by the first chiller 18 circulates through the equipment heat exchange section 33, so that the cooling performance of the first chiller 18 cools the onboard equipment and The waste heat generated in can be recovered.
  • the heat medium flows and circulates through the second pump 38, the second chiller 19, the first connecting portion 45a, the cooler core 31, the four-way valve 44, and the second pump 38 in this order.
  • the blowing air can be dehumidified by the cooling performance of the second chiller 19 .
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connection part 45i, the third It flows and circulates through the five-way valve 43, the seventh connecting portion 45g, and the fourth pump 40 in this order.
  • the heat pumped up by the refrigeration cycle 10 and the heat applied by the electric heater 36 can be used to heat the blast air dehumidified by the cooler core 31. can.
  • the heat pumped up by the refrigerating cycle 10 also includes the waste heat of the vehicle-mounted equipment recovered by the equipment heat exchange section 33, the waste heat of the vehicle-mounted equipment is used to dehumidify the vehicle interior. Heating can be done.
  • the second chiller use dehumidifying heating mode is executed.
  • the refrigeration cycle 10 operates in the first mode or second mode of the multiple chiller circulation mode.
  • the heat medium circulation circuit via the first chiller 18 and the equipment heat exchange unit 33, the second chiller 19 and the cooler core 31 A heat medium circulation circuit is formed.
  • a heat medium circulation circuit passing through the heat medium refrigerant heat exchanger 13 and the heater core 35 is formed.
  • the control device 70 When shifting from the dehumidification heating and waste heat recovery mode to the dehumidification heating mode using the second chiller, the control device 70 fully closes the first expansion valve 17a, closes the refrigerant switching valve 26, and closes the refrigeration cycle. 10 is switched to the second chiller circulation mode shown in FIG. As for the heat medium circuit 30 , the control device 70 stops the operation of at least the first pump 37 . As a result, in the heat medium circuit 30, circulation of the heat medium via the first chiller 18 and the equipment heat exchange section 33 is stopped.
  • the refrigeration cycle apparatus 1 when executing the operation mode in which heat is absorbed from one object to be cooled by the cooling performance of one evaporator, by switching the operation of the refrigeration cycle 10, evaporation You can adjust the cooling capacity of the vessel. That is, the refrigeration cycle apparatus 1 can adjust the cooling capacity of the first chiller 18 by switching the first chiller circulation mode between the first mode and the second mode.
  • the first chiller use cooling mode can be mentioned as one of the operation modes in which heat is absorbed from one object to be cooled by the cooling performance of the first chiller 18 .
  • a cooling mode using the first chiller according to the second embodiment will be described with reference to FIG. 23 .
  • the heat medium includes the first pump 37, the first chiller 18, the second connection portion 45b, the first connection portion 45a, the cooler core 31, the four-way valve 44, the first It flows in order of the pump 37 and circulates.
  • the cooling performance of the first chiller 18 allows the cooler core 31 to cool the blown air, thereby realizing cooling of the passenger compartment.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection portion 45h, the ninth connection portion 45i, and the third five-way valve 43.
  • flow to The heat medium that has flowed out from the third five-way valve 43 passes through the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, the second five-way valve 42, the seventh connection portion 45g, and the fourth pump 40 in this order. flow and circulate.
  • waste heat from the in-vehicle equipment can be recovered in the equipment heat exchange section 33 and radiated to the outside air in the outside air heat exchanger 34 .
  • the refrigeration cycle 10 is set to the first mode of the first chiller circulation mode shown in FIG. 14, so that part of the refrigerant flowing out of the first chiller 18 bypasses the accumulator 20 can be done.
  • the cooling performance of the first chiller 18 can be improved compared to when the second mode of the first chiller circulation mode is adopted, and the cooling operation using the improved cooling performance can be realized.
  • the first chiller use battery cooling mode which is an operation mode in which heat is absorbed from one object to be cooled by the cooling performance of the first chiller 18, will be described with reference to FIG.
  • the heat medium flows through the first pump 37, the first chiller 18, the second connecting portion 45b, and the first five-way valve 41 in this order in the first chiller used battery cooling mode.
  • the heat medium that has flowed out of the first five-way valve 41 passes through the third connection portion 45c, the battery heat exchange portion 32, the fourth connection portion 45d, the second five-way valve 42, the sixth connection portion 45f, the four-way valve 44, the 1 pump 37 in order to circulate.
  • the battery B can be cooled by absorbing heat from the battery B in the battery heat exchange section 32 due to the cooling performance of the first chiller 18 .
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the outside air heat exchanger 34, the eighth connection portion 45h, the ninth connection portion 45i, and the third five-way valve 43.
  • flow to The heat medium that has flowed out from the third five-way valve 43 passes through the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, the second five-way valve 42, the seventh connection portion 45g, and the fourth pump 40 in this order. flow and circulate.
  • waste heat from the in-vehicle equipment can be recovered in the equipment heat exchange section 33 and radiated to the outside air in the outside air heat exchanger 34 .
  • the refrigeration cycle 10 is set to the first aspect of the first chiller circulation mode shown in FIG. be able to.
  • the cooling performance of the first chiller 18 can be improved compared to when the second mode of the first chiller circulation mode is adopted, and the battery B can be cooled using the improved cooling performance. can.
  • the first chiller use waste heat recovery mode which is an operation mode in which heat is absorbed from one object to be cooled by the cooling performance of the first chiller 18, will be described with reference to FIG.
  • the heat medium flows through the first pump 37, the first chiller 18, the second connecting portion 45b, and the first five-way valve 41 in this order.
  • the heat medium that has flowed out of the first five-way valve 41 flows through the third connection portion 45c, the third five-way valve 43, the fifth connection portion 45e, the third pump 39, the equipment heat exchange portion 33, and the second five-way valve 42. , the sixth connection portion 45f, the four-way valve 44, and the first pump 37 in this order.
  • the waste heat of the in-vehicle equipment can be recovered in the equipment heat exchange section 33 by the cooling performance of the first chiller 18 .
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connection portion 45i, the third five-way valve 43, the seventh connection portion. 45g and the fourth pump 40 in order to circulate.
  • the heat applied to the heat medium by the heat medium-refrigerant heat exchanger 13 and the electric heater 36 can be used to heat the blown air.
  • the refrigeration cycle 10 is set to the first aspect of the first chiller circulation mode shown in FIG. can be made As a result, the cooling performance of the first chiller 18 can be improved compared to the case where the second mode of the first chiller circulation mode is adopted, and waste heat recovery from on-vehicle equipment using the improved cooling performance is realized. can do.
  • the first chiller use outside air heat absorption mode which is an operation mode in which heat is absorbed from one object to be cooled by the cooling performance of the first chiller 18, will be described with reference to FIG.
  • the heat medium flows through the first pump 37, the first chiller 18, the second connecting portion 45b, and the first five-way valve 41 in this order.
  • the heat medium that has flowed out of the first five-way valve 41 flows through the outside air heat exchanger 34, the eighth connection portion 45h, the sixth connection portion 45f, the four-way valve 44, and the first pump 37 in this order and circulates.
  • the cooling performance of the first chiller 18 allows the outside air heat exchanger 34 to absorb heat from the outside air to the heat medium.
  • the heat medium is the fourth pump 40, the heat medium refrigerant heat exchanger 13, the first five-way valve 41, the electric heater 36, the heater core 35, the ninth connection portion 45i, the third five-way valve 43, the seventh connection portion. 45g and the fourth pump 40 in order to circulate.
  • the heat applied to the heat medium by the heat medium-refrigerant heat exchanger 13 and the electric heater 36 can be used to heat the blown air.
  • the refrigeration cycle 10 is set to the first mode of the first chiller circulation mode shown in FIG. be able to.
  • the cooling performance of the first chiller 18 can be improved compared to when the second mode of the first chiller circulation mode is adopted, and heat absorption from the outside air can be realized using the improved cooling performance. can.
  • the first chiller use dehumidification heating mode which is an operation mode in which heat is absorbed from one object to be cooled by the cooling performance of the first chiller 18, will be described with reference to FIG.
  • the heat medium includes the first pump 37, the first chiller 18, the second connection portion 45b, the first connection portion 45a, the cooler core 31, the four-way valve 44, the first 1 pump 37 in order to circulate.
  • the cooling performance of the first chiller 18 allows the cooler core 31 to dehumidify the blown air.
  • the heat medium flows through the fourth pump 40, the heat medium refrigerant heat exchanger 13, and the first five-way valve 41 in this order. branch into a side stream.
  • One of the flows of the heat medium that has flowed out from the first five-way valve 41 flows through the outside air heat exchanger 34, the eighth connection portion 45h, and the ninth connection portion 45i in this order.
  • the other part of the heat medium flowing out of the first five-way valve 41 flows through the electric heater 36, the heater core 35, and the ninth connecting portion 45i in this order.
  • the heat medium flowing out of the outside air heat exchanger 34 and the heat medium flowing out of the heater core 35 join at the ninth connection portion 45i, flow through the seventh connection portion 45g and the fourth pump 40 in this order, and circulate.
  • the heater core 35 can heat the blown air using the heat of the heat medium as a heat source.
  • surplus heat can be radiated to the outside air by the outside air heat exchanger 34 .
  • the cooling performance of the first chiller 18 can be improved compared to the case where the second mode of the first chiller circulation mode is adopted, and the dehumidifying heating operation using the improved cooling performance can be realized.
  • the refrigerating cycle 10 according to the second embodiment has the refrigerant bypass passage 25 and the refrigerant switching valve 26, part of the refrigerant flowing out from at least one of the first chiller 18 and the second chiller 19 is Accumulator 20 can be bypassed.
  • the cooling performance of the first chiller 18 and the second chiller 19 can be improved, and various operation modes using a plurality of evaporators can be performed. can be operated effectively.
  • the refrigeration cycle apparatus 1 according to the second embodiment by using the refrigerant bypass passage 25 and the refrigerant switching valve 26, as shown in FIG. can be circulated with As a result, the refrigeration cycle apparatus 1 according to the second embodiment operates in operation modes using the second chiller 19 alone, such as the cooling mode using the second chiller shown in FIG. 19 and the dehumidification heating mode using the second chiller shown in FIG. can be realized.
  • FIG. 1 In the refrigerating cycle device 1 according to the third embodiment, the arrangement of the accumulator 20 and the refrigerant switching valve 26 in the refrigerating cycle 10 is different from that of the second embodiment.
  • Other configurations of the heat medium circuit 30, the indoor air conditioning unit 60, the control system, and the like in the refrigeration cycle apparatus 1 are the same as those of the above-described embodiment, and thus the description thereof will be omitted.
  • the refrigeration cycle 10 includes a compressor 11, a heat medium refrigerant heat exchanger 13, a high-stage expansion valve 14, a gas-liquid separator 15, a first expansion valve 17a, It has a second expansion valve 17 b , a first chiller 18 , a second chiller 19 and an accumulator 20 .
  • the refrigeration cycle 10 according to the third embodiment has a refrigerant bypass passage 25 and a refrigerant switching valve 26, like the second embodiment.
  • the refrigerant bypass passage 25 connects the second refrigerant connection portion 24b and the third refrigerant connection portion 24c.
  • the second refrigerant connection portion 24b is a four-way joint connected to the outlet side of the refrigerant passage 18a in the first chiller 18.
  • the third refrigerant connection portion 24 c is a three-way joint connected to the outlet side of the second chiller 19 in the second chiller 19 .
  • the third coolant connection portion 24c corresponds to an example of a coolant connection portion. Therefore, the refrigerant bypass passage 25 corresponds to an example of a refrigerant bypass passage, and the refrigerant switching valve 26 corresponds to an example of a refrigerant switching portion.
  • the accumulator 20 is arranged on one side of the outlet of the third refrigerant connection portion 24c.
  • the accumulator 20 is arranged between the third refrigerant connection portion 24c and the refrigerant junction portion 16b, unlike the embodiment described above.
  • the refrigerant switching valve 26 is arranged between the second refrigerant connection portion 24b and the refrigerant junction portion 16b.
  • the refrigerant switching valve 26 has the same configuration as that of the second embodiment described above, and corresponds to an example of a refrigerant switching unit.
  • the refrigerating cycle 10 according to the third embodiment corresponds to a configuration in which the positions of the accumulator 20 and the refrigerant switching valve 26 in the refrigerating cycle 10 according to the second embodiment are exchanged.
  • the circuit configuration of the refrigeration cycle 10 according to the third embodiment will be described below with reference to the drawings.
  • the process by which the refrigerant discharged from the compressor 11 reaches the refrigerant branching portion 16a is the same as in the above-described embodiments, so the explanation thereof will be omitted. That is, the multiple chiller circulation mode, the first chiller circulation mode, and the second chiller circulation mode are different in the process until the refrigerant flowing out from the refrigerant branch portion 16a reaches the suction port 11a of the compressor 11. .
  • the circuit configuration of the refrigeration cycle 10 includes a multiple chiller circulation mode in which the refrigerant absorbs heat in the first chiller 18 and the second chiller 19, a first chiller circulation mode in which the refrigerant absorbs heat in the first chiller 18 alone, and a second chiller 19 alone.
  • a second chiller circulation mode is included that allows the refrigerant to absorb heat.
  • the control device 70 puts the first expansion valve 17a and the second expansion valve 17b into a predetermined throttle state. Further, the control device 70 opens the refrigerant switching valve 26 .
  • the refrigerant that has flowed out of one of the outlets of the refrigerant branch portion 16a is decompressed by the first expansion valve 17a, absorbs heat from the heat medium flowing through the heat medium passage 18b in the first chiller 18, and 2 to the refrigerant connecting portion 24b.
  • the refrigerant flowing out from the other outlet of the refrigerant branch portion 16a absorbs heat from the heat medium flowing through the heat medium passage 19b in the second chiller 19.
  • the refrigerant flowing out of the second chiller 19 branches into a flow on the side of the refrigerant bypass passage 25 and a flow on the side of the accumulator 20 at the third refrigerant connection portion 24c.
  • the refrigerant that has flowed through the refrigerant bypass passage 25 joins the refrigerant flowing out of the first chiller 18 at the second refrigerant connection portion 24b and flows into the refrigerant switching valve 26. .
  • the refrigerant that has passed through the refrigerant switching valve 26 flows out to the refrigerant junction portion 16b. That is, the refrigerant that has passed through the refrigerant switching valve 26 bypasses the accumulator 20 and reaches the refrigerant junction portion 16b.
  • part of the refrigerant branched at the third refrigerant connection portion 24c flows into the accumulator 20 and is separated into gas and liquid.
  • the gas-liquid separated refrigerant flows out to the refrigerant junction 16b.
  • the refrigerant merged at the refrigerant junction 16 b is sucked into the suction port 11 a of the compressor 11 .
  • part of the refrigerant that has flowed into the third refrigerant connection portion 24c can be flowed and circulated so as to bypass the accumulator 20, as in FIG.
  • the cooling capacity in the 1st chiller 18 and the 2nd chiller 19 can be improved.
  • the first chiller circulation mode shown in FIG. 30 causes the refrigerant to absorb heat from the heat medium in the first chiller 18 without using the cooling performance of the second chiller 19 .
  • the control device 70 brings the first expansion valve 17a into a predetermined throttle state and brings the second expansion valve 17b into a fully closed state. In addition, the control device 70 closes the refrigerant switching valve 26 .
  • the refrigerant that flows out from the refrigerant branching portion 16a flows through the first expansion valve 17a, the first chiller 18, the second refrigerant connection portion 24b, the refrigerant bypass passage 25, and the third refrigerant connection portion. 24c, the accumulator 20, and the refrigerant junction 16b.
  • the first chiller circulation mode shown in FIG. 30 all of the refrigerant that has passed through the first chiller 18 can be circulated through the accumulator 20.
  • the stability of the refrigeration cycle 10 can be ensured, and the cooling performance of the first chiller 18 can be exhibited.
  • the circuit configuration of the refrigeration cycle 10 and the heat medium circuit is switched, and one of the plurality of evaporators is used from the operation mode in which heat is absorbed from a plurality of objects to be cooled using a plurality of evaporators. can shift to an operation mode that absorbs heat from one object to be cooled.
  • a plurality of operation modes, which are such operation modes, will be described with reference to the drawings.
  • the first chiller use battery cooling mode shifts to the cooling & battery cooling mode when the need for cooling operation in the passenger compartment decreases.
  • the circulation circuit of the heat medium passing through the first chiller 18 and the battery heat exchange unit 32, the second chiller 19 and the cooler core 31 A heat medium circulation circuit is formed through the Also, in the heat medium circuit 30, a heat medium circulation circuit passing through the heat medium refrigerant heat exchanger 13, the equipment heat exchange section 33, and the outside air heat exchanger 34 is formed.
  • the refrigeration cycle 10 at this time is operating in a multiple chiller circulation mode as shown in FIG.
  • the control device 70 when switching from the cooling & battery cooling mode to the battery cooling mode using the first chiller, switches from the multiple chiller circulation mode shown in FIG. Switch to the first chiller circulation mode shown in .
  • the control device 70 stops the operation of at least the second pump 38 .
  • circulation of the heat medium via the second chiller 19 and the cooler core 31 is stopped.
  • the circulation circuit of the heat medium via the first chiller 18 and the battery heat exchange unit 32, the heat medium refrigerant heat exchanger 13, the equipment heat exchange unit 33, a circulation circuit of the heat medium via the outside air heat exchanger 34 is formed. Thereby, the cooling of the battery B using the cooling capacity of the second chiller 19 can be realized.
  • the first chiller use outside air heat absorption mode according to the third embodiment is shifted to, for example, when the need to dehumidify the blown air decreases in the state of operation in the dehumidification heating & outside air heat absorption mode.
  • the circulation circuit of the heat medium passing through the first chiller 18 and the outside air heat exchanger 34, the second chiller 19 and the cooler core 31 A heat medium circulation circuit is formed through the Also, in the heat medium circuit 30, a heat medium circulation circuit passing through the heat medium refrigerant heat exchanger 13 and the heater core 35 is formed.
  • the refrigeration cycle 10 at this time is operating in a multiple chiller circulation mode as shown in FIG.
  • the control device 70 when switching from the dehumidification heating & outside air heat absorption mode to the first chiller use outside air heat absorption mode, changes from the multiple chiller circulation mode shown in FIG. Switch to the first chiller circulation mode shown at 30 .
  • control device 70 stops the operation of at least the second pump 38 .
  • circulation of the heat medium via the second chiller 19 and the cooler core 31 is stopped.
  • the first chiller use waste heat recovery mode according to the third embodiment is shifted to, for example, when the need to dehumidify the blown air is reduced in the state of operation in the dehumidification heating & waste heat recovery mode.
  • the circulation circuit of the heat medium via the first chiller 18 and the equipment heat exchange unit 33, the second chiller 19 and A heat medium circulation circuit passing through the cooler core 31 is formed. Also, in the heat medium circuit 30, a heat medium circulation circuit passing through the heat medium refrigerant heat exchanger 13 and the heater core 35 is formed.
  • the refrigeration cycle 10 at this time is operating in a multiple chiller circulation mode as shown in FIG.
  • the control device 70 when switching from the dehumidification heating & waste heat recovery mode to the first chiller use waste heat recovery mode, the control device 70, for example, switches from the multiple chiller circulation mode shown in FIG. , to the first chiller circulation mode shown in FIG.
  • control device 70 stops the operation of at least the second pump 38 .
  • circulation of the heat medium via the second chiller 19 and the cooler core 31 is stopped.
  • the refrigeration cycle apparatus 1 by using the refrigerant bypass passage 25 and the refrigerant switching valve 26, part of the refrigerant flowing out of the first chiller 18 and the second chiller 19 is transferred to the accumulator 20 can be bypassed and circulated. Thereby, in the refrigerating cycle apparatus 1 according to the third embodiment, the cooling performance of the first chiller 18 and the second chiller 19 can be improved.
  • the first chiller use battery cooling mode, the first chiller use outside air heat absorption mode, the first chiller A use waste heat recovery mode can be realized.
  • a refrigeration cycle 10 includes a compressor 11, a heat medium refrigerant heat exchanger 13, a high-stage expansion valve 14, a gas-liquid separator 15, a first expansion valve 17a, a It has two expansion valves 17 b , a first chiller 18 and a second chiller 19 .
  • the configuration from the compressor 11 to the refrigerant branch portion 16a and the configuration from the refrigerant junction portion 16b to the compressor 11 are the same as those in the above-described embodiment, so the description will be repeated. omitted.
  • a first expansion valve 17a and a first chiller 18 are connected to one outlet of the refrigerant branch portion 16a.
  • a four-way joint-like second refrigerant connection portion 24 b is connected to the outlet side of the refrigerant passage 18 a in the first chiller 18 .
  • the bypass passage 21 is connected to another inlet/outlet of the second refrigerant connection portion 24b, and the first refrigerant switching valve 26a is connected to another inlet/outlet of the second refrigerant connection portion 24b. , the refrigerant junction 16b is connected.
  • the first refrigerant switching valve 26a is composed of an on-off valve similar to the refrigerant switching valve 26 of the above-described embodiment.
  • a first refrigerant bypass passage 25a is connected to the remaining inlet/outlet of the second refrigerant connection portion 24b.
  • the other end side of the first refrigerant bypass passage 25a is connected to a fourth refrigerant connection portion 24d in the shape of a three-way joint.
  • a second expansion valve 17b and a second chiller 19 are connected to the other outlet of the refrigerant branch portion 16a.
  • the outlet side of the refrigerant passage 19a in the second chiller 19 is connected to a three-way joint-shaped third refrigerant connection portion 24c.
  • the refrigerant merging portion 16b is connected to the other inlet/outlet of the third refrigerant connection portion 24c via a second refrigerant switching valve 26b and a three-way joint-shaped fifth refrigerant connection portion 24e.
  • a second coolant bypass passage 25b is connected to another inlet/outlet of the third coolant connection portion 24c.
  • One of the inlets and outlets of the fourth refrigerant connection portion 24d is connected to the other end of the second refrigerant bypass passage 25b.
  • the refrigerant inlet side of the accumulator 20 is connected to the remaining inlet/outlet of the fourth refrigerant connection portion 24d.
  • One of the inlets and outlets of the fifth refrigerant connecting portion 24 e is connected to the refrigerant outlet of the accumulator 20 .
  • the fifth refrigerant connection portion 24e may function as a confluence portion where the refrigerant flowing out of the accumulator 20 and the refrigerant that has passed through the second refrigerant switching valve 26b join together.
  • the refrigerant merging portion 16b may function as a merging portion that merges the refrigerant flowing out of the accumulator 20 or the second refrigerant switching valve 26b and the refrigerant flowing out of the first refrigerant switching valve 26a.
  • the refrigerant junction portion 16 b guides the refrigerant that has passed through the refrigerant junction portion 16 b to the suction port 11 a of the compressor 11 .
  • the refrigerating cycle 10 according to the fourth embodiment configured in this manner can realize a configuration similar to that of the refrigerating cycle 10 according to the second embodiment by closing the first refrigerant switching valve 26a. . Therefore, the refrigerating cycle apparatus 1 according to the fourth embodiment controls the second refrigerant switching valve 26b and the like while the first refrigerant switching valve 26a is closed, thereby achieving the same effect as in the second embodiment. can be demonstrated.
  • the second refrigerant bypass passage 25b corresponds to an example of a refrigerant bypass passage
  • the second refrigerant switching valve 26b corresponds to an example of a refrigerant switching portion.
  • the refrigerating cycle 10 according to the fourth embodiment can realize a configuration similar to that of the refrigerating cycle 10 according to the third embodiment by closing the second refrigerant switching valve 26b. Therefore, the refrigeration cycle apparatus 1 according to the fourth embodiment controls the first refrigerant switching valve 26a and the like while the second refrigerant switching valve 26b is closed, thereby achieving the same effect as in the third embodiment. can be demonstrated.
  • the first refrigerant bypass passage 25a corresponds to an example of a refrigerant bypass passage
  • the first refrigerant switching valve 26a corresponds to an example of a refrigerant switching portion.
  • the refrigeration cycle device 1 As described above, according to the refrigeration cycle device 1 according to the fourth embodiment, even when the refrigeration cycle 10 includes the first refrigerant switching valve 26a and the second refrigerant switching valve 26b shown in FIG. It is possible to obtain operational effects from the configuration and operation common to the form.
  • the present invention is limited to this aspect. isn't it.
  • the number of evaporators in the refrigeration cycle 10 may be plural, and may be three or more.
  • the first chiller 18 and the second chiller 19, which are a plurality of evaporators, are connected in parallel with each other, but the present invention is not limited to this aspect. . That is, as the configuration of the refrigeration cycle 10, it is also possible to employ a configuration in which a plurality of evaporators are connected in series.
  • the refrigerating cycle 10 has a compressor 11 having an intermediate pressure port 11b, a high stage expansion valve 14, a gas-liquid separator 15, and an intermediate pressure refrigerant passage 23. , is configured as a gas injection cycle.
  • the present disclosure does not limit the refrigeration cycle 10 to a gas injection cycle, and various aspects can be employed.
  • the refrigerating cycle 10 of the refrigerating cycle device 1 has an accumulator 20 that separates the gas-liquid refrigerant that has flowed out of the evaporator and causes the gas-phase refrigerant to flow out to the suction port side of the compressor 11.
  • the configuration of the refrigeration cycle 10 of the present disclosure is not limited to the accumulator cycle.
  • the gas-liquid refrigerant flowing out of the condenser is separated on the refrigerant outlet side of the condenser (for example, the heat medium refrigerant heat exchanger 13), and the separated liquid-phase refrigerant It is also possible to employ a receiver cycle with the receiver storing . Further, as the configuration of the refrigeration cycle 10 of the present disclosure, a configuration may be adopted in which the refrigerant flowing out from the evaporator is guided to the suction port of the compressor without using the accumulator.
  • an internal heat exchanger that exchanges heat between the high-pressure refrigerant flowing out of the heat medium refrigerant heat exchanger 13 and the refrigerant decompressed by the high-stage expansion valve 14 is provided.
  • An economizer cycle may be employed.
  • the heat medium circuit 30 having the heat medium refrigerant heat exchanger 13 and the heater core 35 is used as a configuration for heating the blown air with the heat of the high-pressure refrigerant.
  • the heat medium circuit 30 having the heat medium refrigerant heat exchanger 13 and the heater core 35 is used as a configuration for heating the blown air with the heat of the high-pressure refrigerant.
  • the heat medium circuit 30 having the heat medium refrigerant heat exchanger 13 and the heater core 35 is used as a configuration for heating the blown air with the heat of the high-pressure refrigerant.
  • an indoor condenser that condenses the refrigerant may be employed to heat the blown air.
  • the plurality of objects to be cooled include the air blown into the vehicle interior, the battery B mounted on the vehicle, the in-vehicle equipment that generates heat during operation, and the outside air outside the vehicle. , is not limited to this embodiment.
  • the object to be cooled may be different among a plurality of objects to be cooled, and various objects can be adopted.
  • a refrigeration cycle device having a refrigeration cycle (10) and a heat medium circuit (30) and cooling a plurality of objects to be cooled
  • the refrigeration cycle includes a compressor (11) for compressing and discharging refrigerant, a condenser (13) for condensing the high-pressure refrigerant discharged from the compressor, and a decompressor for decompressing the refrigerant discharged from the condenser.
  • the heat medium circuit has a plurality of cooling units (31, 32, 33, 34) that cool a plurality of objects to be cooled by heat exchange with the heat medium,
  • the refrigeration cycle apparatus wherein the heat medium circuit is configured to supply the heat medium cooled by at least one of the plurality of evaporators to at least one of the plurality of cooling units.
  • the heat medium circuit is a first cooling unit (31) included in the plurality of cooling units and configured to cool a first cooling target among the plurality of cooling targets by heat exchange with the heat medium; Second cooling units (32, 33, 34) and The refrigeration cycle apparatus according to item 1, further comprising switching units (41, 42, 43, 44) that switch the flow of the heat medium in the heat medium circuit.
  • the heat medium circuit is switched to a first cooling mode in which the heat medium that has flowed through the plurality of evaporators (18, 19) circulates through the first cooling section (31) by the operation of the switching section.
  • the refrigeration cycle device according to item 2.
  • the heat medium circuit is a second cooling unit in which the heat medium that has flowed through the plurality of evaporators (18, 19) circulates through the second cooling units (32, 33, 34) by the operation of the switching unit. 4.
  • the refrigeration cycle device according to item 2 or 3, which can be switched between modes. (Item 5) In the heat medium circuit, the heat medium that has flowed through some of the evaporators (19) of the plurality of evaporators circulates through the first cooling section (31) and the Any one of items 2 to 4, in which the heat medium circulating through the other evaporator (18) of the plurality of evaporators is switched to a combined mode in which the heat medium circulates through the second cooling units (32, 33, 34).
  • the refrigeration cycle device according to .
  • the compressor compresses the low-pressure refrigerant sucked from the suction port (11a) until it becomes a high-pressure refrigerant and discharges it from the discharge port (11c). has an intermediate pressure port (11b) for merging, 6. Any one of items 1 to 5, wherein the refrigerating cycle has a gas-liquid separation section (15) that separates the gas-liquid of the refrigerant that has flowed out of the condenser and causes the separated gas-phase refrigerant to flow out to the intermediate pressure port.
  • Refrigerating cycle apparatus according to claim 1.
  • the refrigerating cycle apparatus according to any one of items 1 to 6, wherein in the refrigerating cycle, the plurality of evaporators are connected in parallel with each other.
  • the refrigeration cycle includes a refrigerant junction (16b) that joins the refrigerants flowing out of the plurality of evaporators connected in parallel and guides them to the compressor; an accumulator (20) that separates the gas-liquid refrigerant that has flowed out of the plurality of evaporators and causes the separated gas-phase refrigerant to flow out to the compressor; 8.
  • the accumulator is arranged between an outlet of one evaporator (18) of the plurality of evaporators and the refrigerant junction.

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  • Air-Conditioning For Vehicles (AREA)

Abstract

Un dispositif à cycle de réfrigération présente un cycle de réfrigération (10) et un circuit de milieu thermique (30), et refroidit une pluralité de sujets à refroidir. Le cycle de réfrigération comporte un compresseur (11), un condenseur (13), une unité de décompression (17a, 17b) et une pluralité d'évaporateurs (18, 19). Le compresseur comprime et évacue un fluide frigorigène. Le condenseur condense le fluide frigorigène à haute pression qui est évacué du compresseur. L'unité de décompression décomprime le fluide frigorigène qui s'est écoulé du condenseur. La pluralité d'évaporateurs vaporisent le fluide frigorigène qui a été décomprimé par l'unité de décompression et refroidit un milieu thermique circulant dans le circuit de milieu thermique. Le circuit de milieu thermique présente une pluralité d'unités de refroidissement (31, 32, 33, 34) destinées à refroidir une pluralité de sujets à refroidir par échange de chaleur avec le milieu thermique. Le circuit de milieu thermique est conçu pour pouvoir fournir le milieu thermique qui a été refroidi par l'intermédiaire d'au moins l'un de la pluralité d'évaporateurs à au moins l'une de la pluralité d'unités de refroidissement.
PCT/JP2022/045448 2022-01-12 2022-12-09 Dispositif à cycle de réfrigération WO2023136002A1 (fr)

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JP2022-002832 2022-01-12
JP2022002832 2022-01-12
JP2022-090286 2022-06-02
JP2022090286 2022-06-02

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WO2023136002A1 true WO2023136002A1 (fr) 2023-07-20

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006177632A (ja) * 2004-12-24 2006-07-06 Denso Corp 冷凍サイクル
JP2007155230A (ja) * 2005-12-06 2007-06-21 Hitachi Appliances Inc 空気調和機
WO2014016865A1 (fr) * 2012-07-24 2014-01-30 三菱電機株式会社 Dispositif de climatisation
JP2022501252A (ja) * 2018-09-26 2022-01-06 ヴァレオ システム テルミク 車両用の冷媒回路

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006177632A (ja) * 2004-12-24 2006-07-06 Denso Corp 冷凍サイクル
JP2007155230A (ja) * 2005-12-06 2007-06-21 Hitachi Appliances Inc 空気調和機
WO2014016865A1 (fr) * 2012-07-24 2014-01-30 三菱電機株式会社 Dispositif de climatisation
JP2022501252A (ja) * 2018-09-26 2022-01-06 ヴァレオ システム テルミク 車両用の冷媒回路

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