WO2023199912A1 - Dispositif à cycle de pompe à chaleur - Google Patents

Dispositif à cycle de pompe à chaleur Download PDF

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Publication number
WO2023199912A1
WO2023199912A1 PCT/JP2023/014692 JP2023014692W WO2023199912A1 WO 2023199912 A1 WO2023199912 A1 WO 2023199912A1 JP 2023014692 W JP2023014692 W JP 2023014692W WO 2023199912 A1 WO2023199912 A1 WO 2023199912A1
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Prior art keywords
refrigerant
heat
operation mode
section
outside air
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PCT/JP2023/014692
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English (en)
Japanese (ja)
Inventor
淳 稲葉
祐一 加見
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株式会社デンソー
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Publication of WO2023199912A1 publication Critical patent/WO2023199912A1/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

Definitions

  • the present disclosure relates to a heat pump cycle device that includes an accumulator and is configured to be able to switch operation modes.
  • Patent Document 1 discloses a heat pump cycle device that includes an accumulator and is configured to be able to switch operation modes.
  • the accumulator separates the gas-liquid refrigerant, allows the separated gas-phase refrigerant to flow out to the suction side of the compressor, and stores the separated liquid-phase refrigerant as surplus refrigerant in the cycle. It is a separator.
  • the heat pump cycle device of Patent Document 1 is applied to a vehicle air conditioner, and is configured to be able to switch between operating modes such as hot gas heating mode and outside air heat absorption heating mode.
  • the refrigerant circuit is switched to allow a part of the refrigerant discharged from the compressor to flow into the heating section.
  • the heating unit uses the discharged refrigerant as a heat source to heat the air blown into the vehicle interior. Further, the refrigerant flowing out from the heating section and the remaining refrigerant discharged from the compressor are switched to a refrigerant circuit in which the pressure is reduced and the refrigerant is combined and flows into the accumulator.
  • the refrigerant circuit is switched to allow all of the discharged refrigerant to flow into the heating section. Furthermore, the refrigerant circuit is switched to a refrigerant circuit in which the pressure of the refrigerant flowing out from the heating section is reduced, and the reduced pressure refrigerant absorbs outside heat of the outside air and flows into the accumulator.
  • an object of the present disclosure is to provide a heat pump cycle device that includes an accumulator and is configured to be able to switch operation modes, and that can appropriately protect the compressor. do.
  • a heat pump cycle device includes an accumulator, a compressor, and an operation mode switching section.
  • the accumulator separates the gas and liquid of the refrigerant and stores the separated liquid phase refrigerant.
  • the compressor sucks and compresses the gas phase refrigerant separated by the accumulator.
  • the driving mode switching unit switches the driving mode.
  • the operation modes to which the operation mode switching section can switch include a first operation mode and a second operation mode in which the suction side refrigerant pressure, which is the refrigerant pressure in the accumulator, is lower than in the first operation mode. .
  • a recovery flow path through which refrigerant can flow is formed in the refrigerant flow path through which refrigerant does not flow when the operation mode switching unit switches to the first operation mode.
  • liquid amount reduction control is performed to reduce the amount of liquid phase refrigerant in the accumulator by causing the refrigerant to flow into the recovery channel. conduct.
  • FIG. 1 is a schematic overall configuration diagram of a vehicle air conditioner according to a first embodiment.
  • FIG. 2 is a block diagram showing an electric control section of the vehicle air conditioner according to the first embodiment.
  • FIG. 2 is a schematic overall configuration diagram showing the flow of refrigerant, etc. in the independent dehumidification/heating mode of the heat pump cycle of the first embodiment.
  • FIG. 2 is a schematic overall configuration diagram showing the flow of refrigerant, etc. in the independent outside air heat absorption heating mode of the heat pump cycle of the first embodiment.
  • FIG. 2 is a schematic overall configuration diagram showing the flow of refrigerant and the like during the waste heat recovery heating mode of the heat pump cycle of the first embodiment.
  • FIG. 2 is a schematic overall configuration diagram showing the flow of refrigerant and the like in the hot gas heating mode of the heat pump cycle of the first embodiment. It is a time chart of liquid volume reduction control when the hot gas heating mode of the first embodiment is defined as the first operation mode. It is a time chart of liquid amount reduction control when the waste heat recovery heating mode of 1st Embodiment is defined as the 1st operation mode.
  • FIG. 2 is a schematic overall configuration diagram of a vehicle air conditioner according to a second embodiment.
  • FIG. 3 is a schematic overall configuration diagram of a vehicle air conditioner according to a third embodiment.
  • FIG. 3 is a schematic overall configuration diagram of a vehicle air conditioner according to a fourth embodiment.
  • FIG. 7 is a schematic overall configuration diagram showing the flow of refrigerant, etc. in the independent outside air heat absorption heating mode of the heat pump cycle of the fourth embodiment.
  • FIG. 12 is a schematic overall configuration diagram showing the flow of refrigerant, etc. in the waste heat recovery heating mode of the heat pump cycle of the fourth embodiment.
  • It is a typical whole block diagram showing the flow of a refrigerant, etc. in hot gas heating mode of a heat pump cycle of a 4th embodiment.
  • It is a time chart of liquid volume reduction control when the hot gas heating mode of 4th Embodiment is defined as the 1st operation mode.
  • It is a time chart of liquid amount reduction control when the waste heat recovery heating mode of 4th Embodiment is defined as the 1st operation mode.
  • It is a typical overall block diagram of the vehicle air conditioner of a 5th embodiment.
  • a heat pump cycle device is applied to a vehicle air conditioner 1 installed in an electric vehicle.
  • An electric vehicle is a vehicle that obtains driving force for driving from an electric motor.
  • the vehicle air conditioner 1 air-conditions the interior of a vehicle, which is a space to be air-conditioned, and also adjusts the temperature of on-vehicle equipment. Therefore, the vehicle air conditioner 1 can be called an air conditioner with a vehicle-mounted equipment temperature adjustment function, or a vehicle-mounted equipment temperature adjustment device with an air-conditioning function.
  • the vehicle air conditioner 1 specifically adjusts the temperature of the battery 70 as an in-vehicle device.
  • the battery 70 is a secondary battery that stores power to be supplied to a plurality of on-vehicle devices that operate using electricity.
  • the battery 70 is an assembled battery formed by electrically connecting a plurality of stacked battery cells in series or parallel.
  • the battery cell of this embodiment is a lithium ion battery.
  • the battery 70 is a heat-generating device that generates heat during operation (that is, during charging and discharging).
  • the output of the battery 70 tends to decrease when the temperature becomes low, and the battery 70 tends to deteriorate when the temperature becomes high. Therefore, the temperature of the battery 70 needs to be maintained within an appropriate temperature range (in this embodiment, 15° C. or higher and 55° C. or lower). Therefore, in the electric vehicle of this embodiment, the temperature of the battery 70 is adjusted using the vehicle air conditioner 1.
  • the on-vehicle equipment whose temperature is adjusted by the vehicle air conditioner 1 is not limited to the battery 70.
  • the vehicle air conditioner 1 is configured to be able to switch between various operating modes in order to air condition the vehicle interior and adjust the temperature of the battery 70.
  • the vehicle air conditioner 1 includes a heat pump cycle 10, a high temperature side heat medium circuit 30, a low temperature side heat medium circuit 40, an indoor air conditioning unit 50, a control device 60, and the like.
  • the heat pump cycle 10 is a vapor compression type that adjusts the temperature of the air blown into the vehicle interior, the high temperature heat medium circulating in the high temperature heat medium circuit 30, and the low temperature heat medium circulating in the low temperature heat medium circuit 40. This is the refrigeration cycle.
  • the heat pump cycle 10 is configured to be able to switch the circuit configuration of the refrigerant circuit depending on the operating mode of the vehicle air conditioner 1.
  • the heat pump cycle 10 uses an HFO-based refrigerant (specifically, R1234yf) as the refrigerant.
  • the heat pump cycle 10 constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure side refrigerant does not exceed the critical pressure of the refrigerant.
  • Refrigerating machine oil for lubricating the compressor 11 is mixed in the refrigerant.
  • Refrigerating machine oil is PAG oil that is compatible with liquid phase refrigerant. A portion of the refrigerating machine oil circulates through the heat pump cycle 10 together with the refrigerant.
  • the compressor 11 sucks in refrigerant, compresses it, and discharges it.
  • the compressor 11 is an electric compressor that uses an electric motor to rotationally drive a fixed capacity type compression mechanism having a fixed discharge capacity.
  • the rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60, which will be described later.
  • the compressor 11 is arranged in a drive device compartment formed on the front side of the vehicle compartment.
  • the drive device room forms a space in which at least a portion of equipment (for example, an electric motor for driving) used for generating and adjusting driving force for driving the vehicle is arranged.
  • the inlet side of the first three-way joint 12a is connected to the discharge port of the compressor 11.
  • the first three-way joint 12a has three inlets and outlets that communicate with each other.
  • a joint formed by joining a plurality of pipes or a joint formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.
  • the heat pump cycle 10 includes a second three-way joint 12b to a sixth three-way joint 12f, as described later.
  • the basic configuration of the second three-way joint 12b to the sixth three-way joint 12f is the same as that of the first three-way joint 12a.
  • the basic configuration of the three-way joint described in the embodiment described later is also the same as that of the first three-way joint 12a.
  • the first three-way joint 12a serves as a discharge side branching portion that branches the flow of the discharged refrigerant discharged from the compressor 11.
  • the inlet side of the refrigerant passage of the water-refrigerant heat exchanger 13 is connected to one outlet of the first three-way joint 12a.
  • One inlet side of the sixth three-way joint 12f is connected to the other outlet of the first three-way joint 12a.
  • a refrigerant passage leading from the other outlet of the first three-way joint 12a to one inlet of the sixth three-way joint 12f is a bypass passage 21a.
  • a bypass side flow rate adjustment valve 14d is arranged in the bypass passage 21a.
  • the bypass side flow rate adjustment valve 14d controls the refrigerant flowing out from the other outlet of the first three-way joint 12a (that is, the other refrigerant branched at the first three-way joint 12a) during the hot gas heating mode described later. This is a pressure reducing part on the side of the bypass passage where the pressure is reduced.
  • the bypass side flow rate adjustment valve 14d is a bypass side flow rate adjustment section that adjusts the flow rate (mass flow rate) of the refrigerant flowing through the bypass passage 21a.
  • the bypass side flow rate adjustment valve 14d is an electric variable throttle mechanism that has a valve body that changes the throttle opening and an electric actuator that displaces the valve body.
  • a stepping motor or a brushless motor can be used as the electric actuator.
  • the operation of the bypass side flow rate adjustment valve 14d is controlled by a control signal output from the control device 60.
  • the bypass-side flow rate adjustment valve 14d has a full-open function in which it functions as a mere refrigerant passage without exhibiting much of the refrigerant pressure reduction effect and flow rate adjustment effect by fully opening the valve opening.
  • the bypass side flow rate adjustment valve 14d has a fully closing function of closing the refrigerant passage by fully closing the valve opening.
  • the heat pump cycle 10 includes a heating expansion valve 14a, a cooling expansion valve 14b, and a cooling expansion valve 14c, as described later.
  • the basic configuration of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c is the same as that of the bypass side flow rate adjustment valve 14d.
  • the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the bypass side flow rate adjustment valve 14d can switch the refrigerant circuit by exhibiting the above-described fully closing function. Therefore, the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the bypass side flow rate adjustment valve 14d are operation mode switching units that switch the operation mode by switching the refrigerant circuit.
  • the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the bypass side flow rate adjustment valve 14d are replaced by a variable throttle mechanism that does not have a full closing function and an on-off valve that opens and closes the throttle passage. They may be formed in combination. In this case, each on-off valve becomes an operation mode switching section.
  • the water-refrigerant heat exchanger 13 circulates the discharged refrigerant flowing out from one outlet of the first three-way joint 12a (that is, one refrigerant branched at the first three-way joint 12a) through the high-temperature side heat medium circuit 30. This is a heat exchange part that exchanges heat with the high temperature side heat medium. In the water-refrigerant heat exchanger 13, the heat of the discharged refrigerant is radiated to the high-temperature side heat medium to heat the high-temperature side heat medium.
  • the inlet side of the second three-way joint 12b is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 13.
  • the inlet side of the heating expansion valve 14a is connected to one outlet of the second three-way joint 12b.
  • One inlet side of the four-way joint 12x is connected to the other outlet of the second three-way joint 12b.
  • the refrigerant passage leading from the other outlet of the second three-way joint 12b to one inlet of the four-way joint 12x is a dehumidification passage 21b.
  • a dehumidifying on-off valve 22a is arranged in the dehumidifying passage 21b.
  • the dehumidification on-off valve 22a is an on-off valve that opens and closes the dehumidification passage 21b.
  • the dehumidifying on-off valve 22a is an electromagnetic valve whose opening/closing operation is controlled by a control voltage output from the control device 60.
  • the dehumidification on-off valve 22a can switch the refrigerant circuit by opening and closing the dehumidification passage 21b. Therefore, the dehumidifying on-off valve 22a is an operation mode switching section that switches the operation mode by switching the refrigerant circuit.
  • the four-way joint 12x is a joint portion that has four inlets and outlets that communicate with each other.
  • a joint portion formed similarly to the three-way joint described above can be employed.
  • the four-way joint 12x may be formed by combining two three-way joints.
  • the heating expansion valve 14a is an outside air pressure reducing part that reduces the pressure of the refrigerant flowing into the outdoor heat exchanger 15 during an independent outside air heat absorption heating mode, which will be described later. Furthermore, the heating expansion valve 14a is an outside air flow rate adjustment section that adjusts the flow rate (mass flow rate) of the refrigerant flowing into the outdoor heat exchanger 15.
  • the refrigerant inlet side of the outdoor heat exchanger 15 is connected to the outlet of the heating expansion valve 14a.
  • the outdoor heat exchanger 15 is an outdoor heat exchange unit that exchanges heat between the refrigerant flowing out from the heating expansion valve 14a and the outside air blown by an outside air fan (not shown).
  • the outdoor heat exchanger 15 is arranged on the front side of the drive device chamber. Therefore, when the vehicle is running, the outdoor heat exchanger 15 can be exposed to the running wind that has flowed into the drive device chamber through the grille.
  • the outdoor heat exchanger 15 serves as an outside air heat radiating section that radiates the heat of the refrigerant to the outside air during an independent cooling mode, which will be described later.
  • the outdoor heat exchanger 15 serves as an outside air heat absorption section that causes the refrigerant to absorb outside air side heat of the outside air during an independent outside air heat absorption heating mode, which will be described later.
  • the refrigerant outlet of the outdoor heat exchanger 15 is connected to the inlet side of the third three-way joint 12c.
  • One outlet of the third three-way joint 12c is connected to another inlet of the four-way joint 12x via a first check valve 16a.
  • One inlet side of the fourth three-way joint 12d is connected to the other outlet of the third three-way joint 12c.
  • a refrigerant passage from the other outlet of the third three-way joint 12c to one inlet of the fourth three-way joint 12d is a heating passage 21c.
  • a heating on-off valve 22b is arranged in the heating passage 21c.
  • the heating on-off valve 22b is an on-off valve that opens and closes the heating passage 21c.
  • the basic configuration of the heating on-off valve 22b is the same as that of the dehumidification on-off valve 22a.
  • the heating on-off valve 22b can switch the refrigerant circuit by opening and closing the heating passage 21c. Therefore, the heating on-off valve 22b is an operation mode switching section that switches the operation mode by switching the refrigerant circuit.
  • the heating on-off valve 22b closes the heating passage 21c, the refrigerant cannot flow through the heating passage 21c in either the forward or reverse direction.
  • the heating on-off valve 22b closes the heating passage 21c, the refrigerant flows through the heating passage 21c from the other outlet side of the third three-way joint 12c to one inlet of the fourth three-way joint 12d. It cannot flow to the side. Further, when the heating on-off valve 22b closes the heating passage 21c, the refrigerant flows through the heating passage 21c from one inlet of the fourth three-way joint 12d to the other outlet of the third three-way joint 12c. I can't even move to the side. This also applies to the dehumidifying on-off valve 22a.
  • the first check valve 16a allows the refrigerant to flow from the third three-way joint 12c side to the four-way joint 12x side, and prohibits the refrigerant from flowing from the four-way joint 12x side to the third three-way joint 12c side.
  • the refrigerant inlet side of the indoor evaporator 18 is connected to one outlet of the four-way joint 12x via the cooling expansion valve 14b.
  • the cooling expansion valve 14b is an evaporator pressure reducing part that reduces the pressure of the refrigerant flowing out from one outlet of the four-way joint 12x during an individual cooling mode, which will be described later. Furthermore, the cooling expansion valve 14b is an evaporator flow rate adjustment section that adjusts the flow rate (mass flow rate) of the refrigerant flowing into the indoor evaporator 18.
  • the indoor evaporator 18 is arranged within an air conditioning case 51 of an indoor air conditioning unit 50, which will be described later.
  • the indoor evaporator 18 is a cooling evaporator that exchanges heat between the low-pressure refrigerant whose pressure has been reduced by the cooling expansion valve 14b and the air blown into the vehicle interior from the indoor blower 52.
  • the indoor evaporator 18 cools the blown air by evaporating the low-pressure refrigerant and exhibiting an endothermic action.
  • One inlet side of the fifth three-way joint 12e is connected to the refrigerant outlet of the indoor evaporator 18 via the second check valve 16b.
  • the second check valve 16b allows the refrigerant to flow from the refrigerant outlet side of the indoor evaporator 18 to the fifth three-way joint 12e side, and allows the refrigerant to flow from the fifth three-way joint 12e side to the refrigerant outlet side of the indoor evaporator 18. Forbidden to flow.
  • the other inlet side of the sixth three-way joint 12f is connected to another outlet of the four-way joint 12x via a cooling expansion valve 14c.
  • the inlet side of the refrigerant passage of the chiller 20 is connected to the outlet of the sixth three-way joint 12f.
  • the cooling expansion valve 14c is an equipment pressure reducing part that reduces the pressure of the refrigerant flowing into the chiller 20 during a cooling cooling mode or a hot gas heating mode, which will be described later. Furthermore, the cooling expansion valve 14c is an equipment flow rate adjustment section that adjusts the flow rate (mass flow rate) of the refrigerant flowing into the chiller 20.
  • the chiller 20 exchanges heat between the low-pressure refrigerant whose pressure has been reduced by the cooling expansion valve 14c and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40, and evaporates the low-pressure refrigerant.
  • the chiller 20 cools the low-temperature heat medium by evaporating the low-pressure refrigerant and exerting an endothermic action.
  • the other inlet side of the fourth three-way joint 12d is connected to the outlet of the refrigerant passage of the chiller 20.
  • the other inlet side of the fifth three-way joint 12e is connected to the outlet of the fourth three-way joint 12d.
  • the inlet side of the accumulator 23 is connected to the outlet of the fifth three-way joint 12e.
  • the accumulator 23 separates the gas and liquid of the refrigerant that has flowed into the accumulator 23, causes the separated gas-phase refrigerant to flow out to the suction port side of the compressor 11, and stores the separated liquid-phase refrigerant as surplus refrigerant of the cycle.
  • This is a gas-liquid separator located on the low pressure side. Therefore, the gas phase refrigerant outlet of the accumulator 23 is connected to the suction port side of the compressor 11.
  • the high temperature side heat medium circuit 30 is a heat medium circulation circuit that circulates a high temperature side heat medium.
  • an ethylene glycol aqueous solution is used as the high temperature side heat medium.
  • the high temperature side heat medium circuit 30 includes a heat medium passage of the water/refrigerant heat exchanger 13, a high temperature side pump 31, a heater core 32, and the like.
  • the high temperature side pump 31 is a high temperature side heat medium pumping section that pumps the high temperature side heat medium flowing out from the heat medium passage of the water-refrigerant heat exchanger 13 to the heat medium inlet side of the heater core 32.
  • the high temperature side pump 31 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 60.
  • the heater core 32 is a heating heat exchanger that heats the blown air by exchanging heat between the high temperature side heat medium heated by the water-refrigerant heat exchanger 13 and the blown air that has passed through the indoor evaporator 18.
  • the heater core 32 is arranged inside the air conditioning case 51 of the indoor air conditioning unit 50.
  • the heating medium outlet of the heater core 32 is connected to the inlet side of the heating medium passage of the water/refrigerant heat exchanger 13 .
  • each of the components arranged in the water-refrigerant heat exchanger 13 and the high-temperature side heat medium circuit 30 of this embodiment uses one of the discharged refrigerants branched at the first three-way joint 12a as a heat source, and uses the refrigerant to be heated as a heat source.
  • This is a heating section that heats some blown air.
  • the low temperature side heat medium circuit 40 is a heat medium circuit that circulates a low temperature side heat medium.
  • the same type of fluid as the high temperature side heat medium is used as the low temperature side heat medium.
  • the low temperature side heat medium circuit 40 is connected to a low temperature side pump 41, a cooling water passage 70a of the battery 70, a heat medium passage of the chiller 20, and the like.
  • the low temperature side pump 41 is a low temperature side heat medium pumping section that pumps the low temperature side heat medium flowing out of the cooling water passage 70a of the battery 70 to the inlet side of the heat medium passage of the chiller 20.
  • the basic configuration of the low temperature side pump 41 is the same as that of the high temperature side pump 31.
  • the outlet side of the heat medium passage of the chiller 20 is connected to the inlet side of the cooling water passage 70a of the battery 70.
  • the cooling water passage 70a of the battery 70 is a cooling water passage formed to cool the battery 70 by circulating the low temperature side heat medium cooled by the chiller 20.
  • the cooling water passage 70a is formed inside a dedicated battery case that accommodates a plurality of stacked battery cells.
  • the cooling water passage 70a has a passage configuration in which a plurality of passages are connected in parallel inside the battery-dedicated case. Thereby, all the battery cells can be equally cooled in the cooling water passage 70a.
  • the inlet side of the low temperature side pump 41 is connected to the outlet of the cooling water passage 70a.
  • the chiller 20 of the present embodiment becomes a heat absorption part for a device that causes a refrigerant to absorb heat from the device side generated by the battery 70 via a low-temperature side heat medium during the waste heat recovery heating mode described later.
  • the indoor air conditioning unit 50 is a unit that integrates a plurality of components in order to blow air adjusted to an appropriate temperature for air conditioning the vehicle interior to appropriate locations within the vehicle interior.
  • the indoor air conditioning unit 50 is arranged inside an instrument panel at the forefront of the vehicle interior.
  • the indoor air conditioning unit 50 is formed by accommodating an indoor blower 52, an indoor evaporator 18, a heater core 32, etc. in an air conditioning case 51 that forms an air passage for blown air.
  • the air conditioning case 51 is made of a resin (for example, polypropylene) that has a certain degree of elasticity and excellent strength.
  • An inside/outside air switching device 53 is disposed at the most upstream side of the air conditioning case 51 in terms of the air flow.
  • the inside/outside air switching device 53 selectively introduces inside air (ie, vehicle interior air) and outside air (ie, vehicle exterior air) into the air conditioning case 51 .
  • the operation of the inside/outside air switching device 53 is controlled by a control signal output from the control device 60.
  • An indoor blower 52 is arranged downstream of the inside/outside air switching device 53 in the flow of air.
  • the indoor blower 52 is a blower unit that blows air sucked in via the inside/outside air switching device 53 into the vehicle interior.
  • the rotation speed (that is, the blowing capacity) of the indoor blower 52 is controlled by a control voltage output from the control device 60.
  • the indoor evaporator 18 and the heater core 32 are arranged downstream of the indoor blower 52 in the flow of air.
  • the indoor evaporator 18 is arranged upstream of the heater core 32 in the flow of blown air.
  • a cold air bypass passage 55 is formed in the air conditioning case 51 to allow the air that has passed through the indoor evaporator 18 to bypass the heater core 32.
  • An air mix door 54 is arranged downstream of the indoor evaporator 18 in the air conditioning case 51 and upstream of the heater core 32 and the cold air bypass passage 55.
  • the air mix door 54 adjusts the ratio of the volume of the blown air that passes through the heater core 32 side and the volume of blown air that passes through the cold air bypass passage 55 out of the blown air that has passed through the indoor evaporator 18 .
  • the operation of the actuator for driving the air mix door 54 is controlled by a control signal output from the control device 60.
  • a mixing space 56 is arranged on the downstream side of the heater core 32 and the cold air bypass passage 55 in the flow of air.
  • the mixing space 56 is a space in which the blown air heated by the heater core 32 and the blown air that has not been heated after passing through the cold air bypass passage 55 are mixed.
  • the temperature of the blown air (i.e., conditioned air) that is mixed in the mixing space 56 and blown into the vehicle interior can be adjusted by adjusting the opening degree of the air mix door 54.
  • the air mix door 54 of this embodiment is a flow rate adjustment section that adjusts the flow rate of the blown air that is heat exchanged in the heater core 32.
  • a plurality of opening holes are formed at the most downstream part of the air conditioning case 51 in the airflow direction to blow out the conditioned air to various locations within the vehicle interior.
  • a blowout mode door (not shown) is arranged in each of the plurality of openings to open and close each opening. The operation of the actuator for driving the blowout mode door is controlled by a control signal output from the control device 60.
  • the indoor air conditioning unit 50 by switching the opening hole through which the blowout mode door opens and closes, it is possible to blow out conditioned air adjusted to an appropriate temperature to an appropriate location in the vehicle interior.
  • the control device 60 includes a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits.
  • the control device 60 performs various calculations and processes based on a control program stored in the ROM. Then, the control device 60 controls the operation of various controlled devices connected to the output side based on the calculation and processing results.
  • the input side of the control device 60 includes an inside temperature sensor 61a, an outside temperature sensor 61b, a solar radiation sensor 61c, a discharge refrigerant temperature and pressure sensor 62a, a high pressure side refrigerant temperature and pressure sensor 62b, an outdoor unit side refrigerant temperature and pressure sensor 62c, and an evaporator side refrigerant temperature and pressure sensor 62b.
  • the refrigerant temperature and pressure sensor 62d the chiller side refrigerant temperature and pressure sensor 62e, the suction refrigerant pressure sensor 62f, the high temperature side heat medium temperature sensor 63a, the low temperature side heat medium temperature sensor 63b, the battery temperature sensor 64, the air conditioning air temperature sensor 65, etc.
  • a group of sensors are connected.
  • the inside temperature sensor 61a is an inside temperature detection section that detects the inside temperature (inside temperature) Tr of the vehicle interior.
  • the outside temperature sensor 61b is an outside temperature detection section that detects the outside temperature (outside temperature) Tam of the vehicle interior.
  • the solar radiation sensor 61c is a solar radiation detection unit that detects the solar radiation amount As irradiated into the vehicle interior.
  • the discharge refrigerant temperature and pressure sensor 62a is a discharge refrigerant temperature and pressure detection unit that detects the discharge refrigerant temperature Td and the discharge refrigerant pressure Pd of the discharge refrigerant discharged from the compressor 11.
  • the high-pressure side refrigerant temperature and pressure sensor 62b is a high-pressure side refrigerant temperature and pressure detection unit that detects the high-pressure side refrigerant temperature T1 and high-pressure side refrigerant pressure P1 of the refrigerant flowing out from the water-refrigerant heat exchanger 13.
  • the outdoor unit side refrigerant temperature and pressure sensor 62c is an outdoor unit side refrigerant temperature and pressure detection unit that detects the outdoor unit side refrigerant temperature T2 and the outdoor unit side refrigerant pressure P2 of the refrigerant flowing out from the outdoor heat exchanger 15.
  • the evaporator-side refrigerant temperature and pressure sensor 62d is an evaporator-side refrigerant temperature and pressure detection unit that detects the evaporator-side refrigerant temperature Te and evaporator-side refrigerant pressure Pe of the refrigerant flowing out from the indoor evaporator 18.
  • the chiller-side refrigerant temperature and pressure sensor 62e is a chiller-side refrigerant temperature and pressure detection unit that detects the chiller-side refrigerant temperature Tc and chiller-side refrigerant pressure Pc of the refrigerant flowing out from the refrigerant passage of the chiller 20.
  • a detection section in which a pressure detection section and a temperature detection section are integrated is used as the refrigerant temperature and pressure sensor, but of course, the pressure detection section and the temperature detection section are each configured separately. may be adopted.
  • the suction refrigerant pressure sensor 62f is a suction refrigerant temperature detection section that detects the suction side refrigerant pressure PS, which is the pressure of the refrigerant in the accumulator 23.
  • the high temperature side heat medium temperature sensor 63a is a high temperature side heat medium temperature detection section that detects the high temperature side heat medium temperature TWH, which is the temperature of the high temperature side heat medium flowing into the heater core 32.
  • the low temperature side heat medium temperature sensor 63b is a low temperature side heat medium temperature detection section that detects the low temperature side heat medium temperature TWL, which is the temperature of the low temperature side heat medium flowing into the cooling water passage 70a of the battery 70.
  • the battery temperature sensor 64 is a battery temperature detection section that detects the battery temperature TB, which is the temperature of the battery 70.
  • the battery temperature sensor 64 includes a plurality of temperature sensors and detects the temperature of a plurality of locations on the battery 70. Therefore, the control device 60 can detect the temperature difference and temperature distribution of each battery cell forming the battery 70. Furthermore, as the battery temperature TB, the average value of the detection values of a plurality of temperature sensors is adopted.
  • the conditioned air temperature sensor 65 is a conditioned air temperature detection unit that detects the blown air temperature TAV, which is the temperature of the blown air blown from the mixing space 56 into the vehicle interior.
  • an operation panel 69 is connected to the input side of the control device 60, which is arranged near the instrument panel at the front of the vehicle interior. Operation signals from various operation switches provided on the operation panel 69 are input to the control device 60 .
  • operation switches provided on the operation panel 69 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 automatic control setting unit that sets or cancels automatic control operation of the vehicle air conditioner 1.
  • the air conditioner switch is a cooling requesting unit that requests the indoor evaporator 18 to cool the blown air.
  • the air volume setting switch is an air volume setting section that manually sets the air volume of the indoor blower 52.
  • the temperature setting switch is a temperature setting section that sets a set temperature Tset in the vehicle interior.
  • control device 60 of this embodiment has a control section that controls various controlled devices connected to the output side of the control device 60. Therefore, the configuration (hardware and software) that controls the operation of each device to be controlled constitutes a control unit that controls the operation of each device to be controlled.
  • a component of the control device 60 that controls the rotation speed of the compressor 11 constitutes a discharge capacity control section 60a.
  • the configuration that controls the operation of the driving mode switching section constitutes the driving mode switching control section 60b.
  • the operation of the vehicle air conditioner 1 of this embodiment with the above configuration will be explained.
  • various driving modes are switched in order to air condition the vehicle interior and adjust the temperature of the battery 70. Switching of the driving mode is performed by executing a control program stored in the control device 60 in advance.
  • the control program is executed not only when the start switch (so-called IG switch) of the vehicle system is turned on and the vehicle system is started, but also when the battery 70 is being charged from an external power source.
  • start switch so-called IG switch
  • the control program reads the detection signals of the control sensor group and the operation signal of the operation panel described above. Then, based on the read detection signal and operation signal, a target blowout temperature TAO, which is a target temperature of the air blown into the vehicle interior, is calculated. Further, an operation mode is selected based on the detection signal, the operation signal, the target blowout temperature TAO, etc., and the operation of various controlled devices is controlled according to the selected operation mode.
  • a target blowout temperature TAO which is a target temperature of the air blown into the vehicle interior
  • a control routine such as reading the above-mentioned detection signal and operation signal, calculating the target air outlet temperature TAO, selecting an operation mode, and controlling various controlled devices is performed at each predetermined control cycle until the termination condition of the control program is satisfied. repeat.
  • the target outlet temperature TAO is based on the inside temperature Tr detected by the inside temperature sensor 61a, the outside temperature Tam detected by the outside temperature sensor 61b, the amount of solar radiation As detected by the solar radiation sensor 61c, and the set temperature set by the temperature setting switch. It is calculated using Tset etc. Each operation mode will be explained below.
  • the cooling mode is an operation mode in which the interior of the vehicle is cooled by blowing cooled air into the vehicle interior.
  • the cooling mode is likely to be selected when the outside temperature Tam is relatively high or when the target air temperature TAO is a relatively low value.
  • the cooling mode includes an independent cooling mode in which the interior of the vehicle is cooled without cooling the battery 70, and a cooling mode in which the interior of the vehicle is cooled while cooling the battery 70.
  • an operation mode for cooling the battery 70 is executed when the battery temperature TB detected by the battery temperature sensor 64 becomes equal to or higher than a predetermined reference upper limit temperature KTBH.
  • (a-1) Independent cooling mode In the heat pump cycle 10 in the independent cooling mode, the control device 60 sets the heating expansion valve 14a to a fully open state, the cooling expansion valve 14b to a throttle state that exerts a refrigerant pressure reduction effect, and The expansion valve 14c is brought into a fully closed state, and the bypass side flow rate adjustment valve 14d is brought into a fully closed state. Further, the control device 60 closes the dehumidification on-off valve 22a and closes the heating on-off valve 22b.
  • the refrigerant discharged from the compressor 11 is transferred to the water-refrigerant heat exchanger 13, the heating expansion valve 14a which is in the fully open state, the outdoor heat exchanger 15, and the throttle state.
  • the refrigerant circuit is switched to a refrigerant circuit in which the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11 are circulated in this order.
  • the control device 60 operates the high temperature side pump 31 so as to exhibit a predetermined reference pumping capacity. Therefore, in the high temperature side heat medium circuit 30 in the independent cooling mode, the high temperature side heat medium pumped from the high temperature side pump 31 is transferred to the heater core 32, the heat medium passage of the water/refrigerant heat exchanger 13, and the suction port of the high temperature side pump 31. cycle in this order.
  • control device 60 controls the rotation speed of the indoor blower 52 based on the target outlet temperature TAO and with reference to a control map stored in the control device 60 in advance. .
  • control device 60 adjusts the opening degree of the air mix door 54 so that the blown air temperature TAV detected by the conditioned air temperature sensor 65 approaches the target outlet temperature TAO. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • the water-refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as a condenser that radiates heat and condenses the refrigerant
  • the indoor evaporator 18 functions as an evaporator that evaporates the refrigerant.
  • a vapor compression type refrigeration cycle is constructed to function as
  • the refrigerant evaporation pressure in the indoor evaporator 18 in the independent cooling mode is adjusted so that frost formation on the indoor evaporator 18 can be suppressed. More specifically, in this embodiment, the saturation temperature of the refrigerant in the indoor evaporator 18 is adjusted to be 2° C. or higher. Further, the suction side refrigerant pressure PS in the independent cooling mode is approximately equal to the refrigerant evaporation pressure in the indoor evaporator 18, although it may decrease due to pressure loss.
  • the high temperature side heat medium that has flowed into the heat medium path of the water/refrigerant heat exchanger 13 exchanges heat with the refrigerant discharged from the compressor 11 and is heated.
  • the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 is sucked into the high-temperature side pump 31 and is pumped to the heater core 32 .
  • the high temperature side heat medium that has flowed into the heater core 32 exchanges heat with the blown air. This heats the blown air.
  • the high temperature side heat medium flowing out from the heater core 32 flows into the heat medium passage of the water/refrigerant heat exchanger 13 .
  • the indoor air conditioning unit 50 in the independent cooling mode, when the air blown from the indoor blower 52 passes through the indoor evaporator 18, heat is absorbed by the refrigerant and the air is cooled.
  • the blown air cooled by the indoor evaporator 18 is reheated by exchanging heat with the high temperature side heat medium in the heater core 32 according to the opening degree of the air mix door 54 . Then, the blown air whose temperature is adjusted so as to approach the target blowout temperature TAO is blown into the vehicle interior. This achieves cooling of the vehicle interior.
  • the refrigerant discharged from the compressor 11 circulates in the same way as in the independent cooling mode.
  • the refrigerant discharged from the compressor 11 is transferred to the water-refrigerant heat exchanger 13, the heating expansion valve 14a that is fully open, the outdoor heat exchanger 15, the cooling expansion valve 14c that is throttled, and the chiller. 20, the accumulator 23, and the suction port of the compressor 11 in this order. That is, the indoor evaporator 18 and chiller 20 are switched to a refrigerant circuit connected in parallel to the flow of refrigerant.
  • the high temperature side heat medium pumped from the high temperature side pump 31 circulates, as in the independent cooling mode.
  • the control device 60 operates the low-temperature side pump 41 so as to exhibit a predetermined reference pumping capacity. Therefore, in the low temperature side heat medium circuit 40 in the cooling cooling mode, the low temperature side heat medium pumped from the low temperature side pump 41 is transferred to the heat medium passage of the chiller 20, the cooling water passage 70a of the battery 70, and the suction of the low temperature side pump 41. Circulate in order of mouth.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • the water-refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as a condenser, and the indoor evaporator 18 and the chiller 20 function as an evaporator.
  • a cycle is constructed.
  • the suction side refrigerant pressure PS in the cooling cooling mode is equivalent to that in the independent cooling mode.
  • the high-temperature heat medium heated in the water-refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent cooling mode.
  • the low-temperature side heat medium that has flowed into the heat medium passage of the chiller 20 exchanges heat with the low-pressure side refrigerant whose pressure has been reduced by the cooling expansion valve 14c, and is cooled.
  • the low temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 70a of the battery 70.
  • the low-temperature heat medium that has flowed into the cooling water passage 70a of the battery 70 absorbs equipment-side heat generated by the battery 70. This cools the battery 70.
  • the low-temperature side heat medium flowing out of the cooling water passage 70a of the battery 70 is sucked into the low-temperature side pump 41 and is pumped to the heat medium passage of the chiller 20. Therefore, in the chiller 20 in the cooling cooling mode, the refrigerant absorbs the device-side heat generated by the battery 70 via the low-temperature side heat medium.
  • cooling of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, as in the independent cooling mode.
  • the dehumidifying and heating mode is an operation mode that dehumidifies and heats the vehicle interior by reheating the cooled and dehumidified blown air and blowing it into the vehicle interior.
  • the dehumidifying heating mode is likely to be selected when the outside temperature Tam is in the intermediate temperature range or when the target air temperature TAO is in the intermediate temperature range.
  • the dehumidifying and heating mode includes an independent dehumidifying and heating mode in which the interior of the vehicle is dehumidified and heated without cooling the battery 70, and a cooling, dehumidifying and heating mode in which the battery 70 is cooled and the interior of the vehicle is dehumidified and heated.
  • (b-1) Independent dehumidifying and heating mode
  • the control device 60 fully closes the heating expansion valve 14a, throttles the cooling expansion valve 14b, and controls the cooling expansion valve 14c. is fully closed, and the bypass side flow rate adjustment valve 14d is fully closed. Further, the control device 60 opens the dehumidification on-off valve 22a and closes the heating on-off valve 22b.
  • the refrigerant circuit is switched to a refrigerant circuit in which the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11 are circulated in this order.
  • the high temperature side heat medium pumped from the high temperature side pump 31 circulates as in the independent cooling mode.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser and the indoor evaporator 18 functions as an evaporator.
  • the refrigerant evaporation pressure in the indoor evaporator 18 in the independent dehumidification heating mode is set such that the indoor evaporator 18 can dehumidify the blown air and can suppress frost formation on the indoor evaporator 18.
  • the saturation temperature of the refrigerant in the indoor evaporator 18 is adjusted to be lower than the outside air temperature Tam and 2° C. or higher.
  • the suction side refrigerant pressure PS in the independent dehumidification/heating mode may decrease due to pressure loss, it is approximately equal to the refrigerant evaporation pressure in the indoor evaporator 18.
  • the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent cooling mode.
  • the blown air that has been cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 32. Then, the temperature-adjusted blast air is blown into the vehicle interior, thereby realizing dehumidification and heating of the vehicle interior.
  • the refrigerant discharged from the compressor 11 circulates in the same manner as in the independent dehumidifying and heating mode.
  • the refrigerant discharged from the compressor 11 is sent to the water-refrigerant heat exchanger 13, the dehumidification passage 21b, the cooling expansion valve 14c which is in a throttled state, the chiller 20, the accumulator 23, and the suction port of the compressor 11, in this order.
  • Switched to circulating refrigerant circuit That is, the indoor evaporator 18 and chiller 20 are switched to a refrigerant circuit connected in parallel to the flow of refrigerant.
  • the high temperature side heat medium pumped from the high temperature side pump 31 circulates, as in the independent cooling mode.
  • the low temperature side heat medium pumped from the low temperature side pump 41 circulates, as in the cooling cooling mode.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser, and the indoor evaporator 18 and chiller 20 function as evaporators.
  • the suction side refrigerant pressure PS in the cooling, dehumidifying, and heating mode is equivalent to that in the independent cooling mode.
  • the high temperature side heat medium heated in the water/refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent cooling mode.
  • the low temperature side heat medium circuit 40 in the cooling, dehumidifying and heating mode the low temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 70a of the battery 70, similar to the cooling and cooling mode. This cools the battery 70.
  • dehumidification and heating in the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, similarly to the independent dehumidification and heating mode.
  • Heating Mode is an operation mode in which the interior of the vehicle is heated by blowing heated air into the vehicle interior.
  • the heating mode is likely to be selected when the outside temperature Tam is relatively low or when the target air temperature TAO is relatively high.
  • the heating mode includes an independent outside air heat absorption heating mode that uses the heat absorbed from the outside air as a heat source to heat the interior of the vehicle without cooling the battery 70, and a mode that cools the battery 70 and heats the interior of the vehicle using the heat absorbed from the outside air as a heat source.
  • the independent outside air endothermic heating mode, the cooling outside air endothermic heating mode, and the waste heat recovery heating mode are switched based on the battery temperature TB, the blown air temperature TAV, etc.
  • (c-1) Independent outside air endothermic heating mode
  • the control device 60 puts the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the fully closed state, and expands the cooling.
  • the valve 14c is fully closed, and the bypass side flow rate adjustment valve 14d is fully closed. Further, the control device 60 closes the dehumidification on-off valve 22a and opens the heating on-off valve 22b.
  • the refrigerant circuit is switched to a refrigerant circuit in which refrigerant circulates in the order of the valve 14a, the outdoor heat exchanger 15, the heating passage 21c, the accumulator 23, and the suction port of the compressor 11.
  • the high temperature side heat medium pumped from the high temperature side pump 31 circulates, as in the independent cooling mode, as shown by the broken line arrow in FIG.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser and the outdoor heat exchanger 15 functions as an evaporator.
  • the refrigerant evaporation pressure in the outdoor heat exchanger 15 in the independent outside air heat absorption heating mode is adjusted so that the refrigerant reduced in pressure by the heating expansion valve 14a can absorb heat from the outside air. More specifically, the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is adjusted to be lower than the outside air temperature Tam.
  • the suction side refrigerant pressure PS during the independent outside air endothermic heating mode is approximately equal to the refrigerant evaporation pressure in the indoor evaporator 18, although it may decrease due to pressure loss. Since the heating mode is executed when the outside temperature Tam is relatively low, the suction side refrigerant pressure PS during the independent outside air absorption heating mode is lower than the suction side refrigerant pressure PS during the independent cooling mode. Cheap.
  • the high temperature side heat medium heated in the water/refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent cooling mode.
  • the air blown from the indoor blower 52 passes through the indoor evaporator 18.
  • the blown air that has passed through the indoor evaporator 18 is heated by exchanging heat with the high temperature side heat medium in the heater core 32 according to the opening degree of the air mix door 54 .
  • the blown air whose temperature is adjusted so as to approach the target blowout temperature TAO is blown into the vehicle interior. This achieves heating of the vehicle interior.
  • the refrigerant discharged from the compressor 11 circulates in the same way as in the independent outside air endothermic heating mode.
  • the refrigerant discharged from the compressor 11 is sent to the water-refrigerant heat exchanger 13, the dehumidification passage 21b, the cooling expansion valve 14c which is in a throttled state, the chiller 20, the accumulator 23, and the suction port of the compressor 11, in this order.
  • Switched to circulating refrigerant circuit That is, the outdoor heat exchanger 15 and chiller 20 are switched to a refrigerant circuit connected in parallel to the flow of refrigerant.
  • the high temperature side heat medium pumped from the high temperature side pump 31 circulates, as in the independent cooling mode.
  • the low temperature side heat medium pumped from the low temperature side pump 41 circulates, as in the cooling cooling mode.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser, and the outdoor heat exchanger 15 and chiller 20 function as evaporators. be done.
  • the suction side refrigerant pressure PS in the cooling outside air endothermic heating mode is the same as that in the independent outside air endothermic heating mode.
  • the high temperature side heat medium heated in the water/refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent cooling mode.
  • the low temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 70a of the battery 70, similarly to the cooling cooling mode. This cools the battery 70.
  • heating of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, as in the independent outside air endothermic heating mode.
  • (c-3) Waste heat recovery heating mode In the heat pump cycle 10 in the waste heat recovery heating mode, the control device 60 fully closes the heating expansion valve 14a, fully closes the cooling expansion valve 14b, and The expansion valve 14c is brought into a throttled state, and the bypass side flow rate adjustment valve 14d is brought into a fully closed state. Further, the control device 60 opens the dehumidification on-off valve 22a and closes the heating on-off valve 22b.
  • the refrigerant circuit is switched to a refrigerant circuit in which the cooling expansion valve 14c, the chiller 20, the accumulator 23, and the suction port of the compressor 11 are circulated in this order.
  • the high temperature side heat medium pumped from the high temperature side pump 31 circulates, as in the independent cooling mode, as shown by the broken line arrow in FIG.
  • the low temperature side heat medium pumped from the low temperature side pump 41 circulates, as in the cooling cooling mode, as shown by the broken line arrow in FIG.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser and the chiller 20 functions as an evaporator.
  • the refrigerant evaporation pressure in the chiller 20 during the waste heat recovery heating mode is adjusted so that the battery 70 can be appropriately cooled.
  • the saturation temperature of the refrigerant in the chiller 20 is adjusted to be higher than the outside temperature Tam.
  • the suction side refrigerant pressure PS during the waste heat recovery heating mode may decrease due to pressure loss, it is generally equivalent to the refrigerant evaporation pressure in the chiller 20. Therefore, the refrigerant pressure within the accumulator 23 during the waste heat recovery heating mode tends to be higher than the refrigerant pressure within the accumulator 23 during the independent outside air heat absorption heating mode.
  • the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent cooling mode.
  • the low temperature side heat medium cooled by the chiller 20 flows into the cooling water passage 70a of the battery 70, as in the cooling cooling mode. This cools the battery 70.
  • heating of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, similarly to the independent outside air absorption heating mode.
  • the hot gas heating mode is an operation mode that heats the interior of the vehicle.
  • the hot gas heating mode is selected when the outside temperature Tam is extremely low (in this embodiment, less than -10° C.).
  • the control device 60 In the heat pump cycle 10 in the hot gas heating mode, the control device 60 fully closes the heating expansion valve 14a, fully closes the cooling expansion valve 14b, and throttles the cooling expansion valve 14c, thereby reducing the bypass side flow rate.
  • the regulating valve 14d is brought into a throttled state. Further, the control device 60 opens the dehumidification on-off valve 22a and closes the heating on-off valve 22b.
  • the refrigerant discharged from the compressor 11 flows through the first three-way joint 12a, the bypass side flow adjustment valve 14d arranged in the bypass passage 21a, the sixth three-way joint 12f, the chiller 20, the accumulator 23,
  • the refrigerant circuit is switched to the one in which the refrigerant circulates in the order of the suction port of the compressor 11.
  • the high temperature side heat medium pumped from the high temperature side pump 31 circulates, as in the independent cooling mode, as shown by the broken line arrow in FIG.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • the flow of refrigerant discharged from the compressor 11 is branched at the first three-way joint 12a.
  • One of the refrigerants branched off at the first three-way joint 12a flows into the water-refrigerant heat exchanger 13 and radiates heat to the high temperature side heat medium. Thereby, the high temperature side heat medium is heated.
  • the refrigerant flowing out from the water-refrigerant heat exchanger 13 flows into the cooling expansion valve 14c via the dehumidification passage 21b and is depressurized.
  • the refrigerant having a relatively low enthalpy flowing out from the cooling expansion valve 14c flows into the other inlet of the sixth three-way joint 12f.
  • the other refrigerant branched at the first three-way joint 12a flows into the bypass passage 21a.
  • the flow rate of the refrigerant flowing into the bypass passage 21a is adjusted by the bypass side flow rate adjustment valve 14d, and the pressure is reduced.
  • the relatively high enthalpy refrigerant whose pressure has been reduced by the bypass side flow regulating valve 14d flows into one inlet of the sixth three-way joint 12f.
  • the flow of refrigerant flowing out from the bypass side flow rate adjustment valve 14d and the flow of refrigerant flowing out from the cooling expansion valve 14c are joined and mixed at the sixth three-way joint 12f.
  • the refrigerant flowing out from the sixth three-way joint 12f flows into the chiller 20 and is further mixed homogeneously.
  • the refrigerant flowing out from the refrigerant passage of the chiller 20 flows into the accumulator 23 .
  • the gas phase refrigerant separated in the accumulator 23 is sucked into the compressor 11 and compressed again.
  • the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent cooling mode.
  • heating of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, similarly to the independent outside air endothermic heating mode.
  • the hot gas heating mode is an operation mode selected when the outside temperature Tam is at an extremely low temperature. Therefore, when the refrigerant flowing out from the water-refrigerant heat exchanger 13 is made to flow into the outdoor heat exchanger 15, even if the pressure is reduced by the heating expansion valve 14a, the refrigerant radiates heat to the outside air in the outdoor heat exchanger 15. There is a possibility that it will be stored away.
  • the amount of heat radiated by the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 13 will decrease, so the heating of the blown air in the heating section will be reduced. ability will decrease.
  • the refrigerant circuit of the heat pump cycle 10 is switched to a refrigerant circuit that does not allow the refrigerant flowing out from the water-refrigerant heat exchanger 13 to flow into the outdoor heat exchanger 15. According to this, the heat generated by the work of the compressor 11 can be effectively used to heat the blown air, and it is possible to suppress a decrease in heating capacity in the heating section.
  • the suction side refrigerant pressure PS is higher than in all heating modes (i.e., in the independent outside air endothermic heating mode, in the cooling outside air endothermic heating mode, and in the waste heat recovery heating mode). It will be adjusted so that More specifically, in this embodiment, the saturation temperature of the suction side refrigerant is adjusted to about 20°C.
  • the suction side refrigerant pressure PS is adjusted by controlling the refrigerant discharge capacity of the compressor 11, the throttle opening of the cooling expansion valve 14c, and the throttle opening of the bypass side flow rate adjustment valve 14d.
  • the vehicle air conditioner 1 of this embodiment by switching the driving mode, comfortable air conditioning in the vehicle interior and appropriate temperature adjustment of the battery 70, which is an on-vehicle device, can be performed.
  • the suction side refrigerant pressure PS may change when the operation mode is switched.
  • the refrigerant pressure in the accumulator 23 changes suddenly when the operation mode is switched.
  • liquid amount reduction control is performed to reduce the amount of liquid phase refrigerant in the accumulator 23 when switching the driving mode.
  • the liquid amount reduction control is performed when a predetermined operation mode is defined as a first operation mode, and an operation mode in which the suction side refrigerant pressure PS is lower than the first operation mode is defined as a second operation mode. It is executed when switching from the first operation mode to the second operation mode.
  • the second operation mode is not limited to an operation mode in which the suction side refrigerant pressure PS is always lower than in the first operation mode, but also includes an operation mode in which the suction side refrigerant pressure PS can be lower than in the first operation mode.
  • the amount of liquid phase refrigerant stored in the accumulator 23 is reduced by causing the refrigerant in the heat pump cycle 10 to flow into the recovery channel 24.
  • the recovery flow path 24 is a refrigerant flow path through which refrigerant does not flow during the first operation mode, and is formed to allow refrigerant to flow therethrough.
  • the recovery channel 24 may have a volume equal to or larger than that of the accumulator 23 so that the amount of liquid phase refrigerant stored in the accumulator 23 can be reliably reduced by performing liquid volume reduction control. desirable. Therefore, the recovery channel 24 of this embodiment is formed by a refrigerant channel that includes a component (specifically, a heat exchanger) with a relatively large internal volume.
  • a component specifically, a heat exchanger
  • the recovery flow path 24 of this embodiment is formed so as to be able to connect the region through which the high-pressure side refrigerant flows and the region through which the low-pressure side refrigerant flows during the first operation mode.
  • the operation mode is switched based on the outside temperature Tam and the target air temperature TAO. Therefore, in the vehicle air conditioner 1 of this embodiment, the following combinations are possible as the driving modes corresponding to the first driving mode and the second driving mode.
  • the hot gas heating mode when defined as the first operation mode, the independent outside air endothermic heating mode, the cooling outside air endothermic heating mode, and the waste heat recovery heating mode can be defined as the second operation mode.
  • the recovery channel 24 runs from one outlet of the second three-way joint 12b to the heating expansion valve 14a and the outdoor heat exchanger, as shown in FIG. 15. It is formed by a refrigerant flow path leading to the fourth three-way joint 12d via the heating passage 21c.
  • the independent outside air endothermic heating mode and the cooled outside air endothermic heating mode can be defined as the second operation mode.
  • the recovery channel 24 runs from one outlet of the second three-way joint 12b to the heating expansion valve 14a and the outdoor heat exchanger, as shown in FIG. It is formed by a refrigerant flow path that reaches the fourth three-way joint 12d via the heating passage 21c and the heating passage 21c.
  • the independent dehumidifying heating mode or the cooling dehumidifying heating mode when defined as the first operating mode, the independent outside air endothermic heating mode or the cooling outside air endothermic heating mode can be defined as the second operating mode.
  • the recovery channel 24 connects the heating expansion valve 14a from one outlet to the second three-way joint 12b, as shown in FIG. , the outdoor heat exchanger 15, the heating passage 21c, and the fourth three-way joint 12d, and are formed by a refrigerant flow path leading to the fifth three-way joint 12e.
  • the operation of each component device is controlled as shown in the time charts of FIGS. 7 and 8.
  • the liquid volume reduction control is executed when the control program determines to switch from the first operation mode to the second operation mode.
  • the time chart of FIG. 7 shows an example in which the hot gas heating mode is defined as the first operation mode, and the independent outside air heat absorption heating mode is defined as the second operation mode.
  • the heating expansion valve 14a when it is determined to switch from the first operation mode to the second operation mode, the heating expansion valve 14a is changed from the fully closed state to the throttled state. That is, in the liquid volume reduction control, the heating expansion valve 14a is opened. At this time, the opening degree of the heating expansion valve 14a is set to a minute opening degree that does not affect the high-low pressure balance of the heat pump cycle 10 in the hot gas heating mode.
  • the refrigerant flows into the recovery channel 24. That is, a part of the high-pressure side refrigerant flowing out from the water-refrigerant heat exchanger 13 flows into the outdoor heat exchanger 15 via the heating expansion valve 14a. Since the heating mode is executed when the outside temperature Tam is relatively low, the refrigerant that has flowed into the outdoor heat exchanger 15 is condensed and stored in the outdoor heat exchanger 15. As a result, the amount of liquid phase refrigerant in the accumulator 23 is reduced.
  • the liquid volume reduction control is ended after the predetermined collection time Tmc has elapsed.
  • the mode is switched to the independent outside air heat absorption heating mode.
  • the recovery time Tmc of this embodiment is set to a time interval (specifically, 10 seconds) that allows the amount of liquid phase refrigerant in the accumulator 23 to be appropriately reduced.
  • the same liquid amount reduction control as in FIG. 7 may be performed.
  • the cooling expansion valve 14c may be set to the throttle state, and the dehumidification on-off valve 22a may be opened.
  • the hot gas heating mode is defined as the first operation mode and the waste heat recovery heating mode is defined as the second operation mode
  • the same liquid amount reduction control as in FIG. 7 may be performed.
  • the heating expansion valve 14a is fully closed, and the cooling expansion valve 14c is set to the throttle state. , just open the dehumidifying on-off valve 22a.
  • the time chart in FIG. 8 shows an example in which the waste heat recovery heating mode is defined as the first operation mode, and the independent outside air heat absorption heating mode is defined as the second operation mode.
  • the heating expansion valve 14a when switching from the first operation mode to the second operation mode is determined, the heating expansion valve 14a is changed from the fully closed state to the throttle state. Thereby, the amount of liquid phase refrigerant in the accumulator 23 can be reduced similarly to the liquid amount reduction control shown in FIG.
  • the same liquid volume reduction control as in FIG. 8 may be performed.
  • the cooling expansion valve 14c may be set to the throttle state and the dehumidification on-off valve 22a may be opened.
  • the independent dehumidifying heating mode or the cooling dehumidifying heating mode is defined as the first operating mode
  • the independent outside air heating mode or the cooling outside air endothermic heating mode is defined as the second operating mode
  • similar liquid volume reduction control is performed. do it. That is, in the liquid volume reduction control, the heating expansion valve 14a may be changed from the fully closed state to the throttled state.
  • fluid volume reduction control is performed when switching from the first operation mode to the second operation mode.
  • the amount of liquid phase refrigerant in the accumulator 23 can be reduced. Therefore, even if the suction side refrigerant pressure PS decreases when switching from the first operation mode to the second operation mode, the forming phenomenon is less likely to occur, and liquid compression by the compressor 11 can be suppressed.
  • the compressor 11 can be appropriately protected. Furthermore, in the liquid volume reduction control, the surplus refrigerant in the cycle is simply moved from the inside of the accumulator 23 to the outdoor heat exchanger 15, so the heating capacity of the blown air in the heating section is reduced during the execution of the liquid volume reduction control. Not at all.
  • the recovery channel 24 is formed so as to connect the region through which the high-pressure refrigerant flows and the region through which the low-pressure refrigerant flows during the first operation mode. . According to this, by flowing the refrigerant from the high pressure side during the liquid volume reduction control, the refrigerant can be caused to flow into the recovery flow path 24 in a short time. Therefore, the amount of liquid phase refrigerant in the accumulator 23 can be reduced in a short time.
  • liquid volume reduction control is performed when switching from the hot gas heating mode to the independent outside air endothermic heating mode or the cooled outside air endothermic heating mode. Further, when switching from the waste heat recovery heating mode to the independent outside air endothermic heating mode or the cooled outside air endothermic heating mode, liquid volume reduction control is performed. Further, when switching from the independent dehumidifying heating mode or the cooling dehumidifying heating mode to the independent outside air endothermic heating mode or the cooling outside air endothermic heating mode, liquid amount reduction control is performed.
  • the recovery flow path 24 is formed by the portion through which the refrigerant flows during the second operating mode. Therefore, by switching to the second operation mode, the refrigerant stored in the outdoor heat exchanger 15 can be returned to the accumulator 23 again. As a result, it is possible to avoid a refrigerant shortage in the heat pump cycle 10 after switching to the second operation mode.
  • the heating expansion valve 14a and the outdoor heat exchanger 15 form the recovery flow path 24, so in the liquid volume reduction control, the heating expansion valve 14a is The amount of liquid phase refrigerant in the accumulator 23 can be reduced by simple control of opening.
  • the heat pump cycle 10 includes a first three-way joint 12a, a sixth three-way joint 12f, a bypass passage 21a, and a bypass side flow rate adjustment valve.
  • a bypass side flow rate adjustment valve An example in which 14d is abolished will be explained.
  • the rest of the configuration of the vehicle air conditioner 1 is the same as that of the first embodiment.
  • the vehicle air conditioner 1 of this embodiment can operate in the (a) cooling mode, (b) dehumidification heating mode, and (c) heating mode described in the first embodiment.
  • the waste heat recovery heating mode is defined as the first operation mode
  • the independent outside air endothermic heating mode or the cooling outside air endothermic heating mode is defined as the second operation mode.
  • the independent dehumidifying heating mode or the cooling dehumidifying heating mode is defined as the first operating mode
  • the independent outside air heating mode or the cooling outside air endothermic heating mode is defined as the second operating mode.
  • the compressor 11 can be appropriately protected even if the heat pump cycle device includes the accumulator 23 and is configured to be able to switch the operation mode.
  • the third check valve 16c is arranged in the heating passage 21c.
  • the third check valve 16c allows the refrigerant to flow from the outlet side of the heating on-off valve 22b to one inlet side of the fourth three-way joint 12d, and from the fourth three-way joint 12d side to the heating on-off valve 22b. Prevent refrigerant from flowing to the outlet side.
  • the rest of the configuration of the heat pump cycle 10 is the same as that of the first embodiment.
  • the vehicle air conditioner 1 of this embodiment operates in exactly the same way as the first embodiment. As a result, effects similar to those of the first embodiment can be obtained. That is, even if the heat pump cycle device includes the accumulator 23 and is configured to be able to switch the operation mode, the compressor 11 can be appropriately protected.
  • the heating on-off valve 22b does not need to have sealing performance in the opposite direction. That is, the heating on-off valve 22b does not need to have the function of prohibiting the refrigerant from flowing from one inlet side of the fourth three-way joint 12d to the other outlet side of the third three-way joint 12c. Therefore, the heating on-off valve 22b may be opened during the hot gas heating mode.
  • the vehicle air conditioner 1a is, like the vehicle air conditioner 1 described in the first embodiment, a heat pump cycle device that air-conditions the vehicle interior and adjusts the temperature of vehicle-mounted equipment.
  • the vehicle air conditioner 1a includes a heat pump cycle 10a, a heat medium circuit 30a, an indoor air conditioning unit 50, a control device 60, and the like.
  • the heat pump cycle 10a of the present embodiment is a vapor compression type refrigeration cycle that adjusts the temperature of the air blown into the vehicle interior and the heat medium circulating in the heat medium circuit 30a.
  • the heat pump cycle 10a is configured to be able to switch the circuit configuration of the refrigerant circuit depending on the operating mode of the vehicle air conditioner 1a.
  • the heat pump cycle 10a differs from the heat pump cycle 10 described in the first embodiment in that it includes a second three-way joint 12b, a third three-way joint 12c, a fourth three-way joint 12d, a heating expansion valve 14a, an outdoor heat exchanger 15, and a dehumidifier.
  • the passageway 21b for heating, the passageway 21c for heating, the on-off valve 22a for dehumidification, the on-off valve 22b for heating, etc. are abolished.
  • the inlet side of the seventh three-way joint 12g is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 13 of the heat pump cycle 10a.
  • the inlet side of the cooling expansion valve 14b is connected to one outlet of the seventh three-way joint 12g.
  • the other outlet of the seventh three-way joint 12g is connected to the inlet side of the cooling expansion valve 14c.
  • the other configuration of the heat pump cycle 10a is similar to the heat pump cycle 10 described in the first embodiment.
  • the heat medium circuit 30a is a heat medium circulation circuit that circulates a heat medium.
  • the heat medium circuit 30a is configured to be switchable in circuit configuration depending on the operating mode of the vehicle air conditioner 1a.
  • an ethylene glycol aqueous solution is used as the heat medium.
  • the heat medium circuit 30a includes a heat medium passage of the water/refrigerant heat exchanger 13, a high temperature side pump 31, a heater core 32, a high temperature side three-way valve 33, a radiator 34, a heat medium passage of the chiller 20, a low temperature side pump 41, and a low temperature side three way side valve.
  • a valve 43, a cooling water passage 70a for the battery 70, etc. are arranged.
  • the inlet side of the heat medium passage of the water-refrigerant heat exchanger 13 is connected to the discharge port of the high temperature side pump 31 of the heat medium circuit 30a.
  • the inlet side of the high temperature side three-way valve 33 is connected to the outlet of the heat medium passage of the water-refrigerant heat exchanger 13 .
  • One outflow port of the high temperature side three-way valve 33 is connected to one inflow port side of the first heat medium three-way joint 35a.
  • the other outlet of the high temperature side three-way valve 33 is connected to the heat medium inlet side of the heater core 32 .
  • the high-temperature side three-way valve 33 controls the flow rate of the heat medium flowing out from the heat medium passage of the water-refrigerant heat exchanger 13 into the radiator 34 via the first heat medium three-way joint 35a, and the flow rate of the heat medium flowing into the heater core 32.
  • This is a three-way flow rate adjustment valve that can continuously adjust the flow rate ratio to the heat medium flow rate.
  • the operation of the high temperature side three-way valve 33 is controlled by a control signal output from the control device 60.
  • the high-temperature side three-way valve 33 can allow the entire flow rate of the heat medium flowing out from the heat medium passage of the water-refrigerant heat exchanger 13 to flow into the radiator 34 . Furthermore, the high temperature side three-way valve 33 can allow the entire flow rate of the heat medium flowing out from the heat medium passage of the water-refrigerant heat exchanger 13 to flow into the heater core 32 . Therefore, the high temperature side three-way valve 33 is an operation mode switching unit that switches the operation mode by switching the circuit configuration.
  • the first heat medium three-way joint 35a is a joint portion having three inlets and outlets that communicate with each other, similar to the first three-way joint 12a and the like described in the first embodiment. Furthermore, the heat medium circuit 30a includes a second heat medium three-way joint 35b to a fourth heat medium three-way joint 35d, as described later. The basic configuration of the second heat medium three-way joint 35b to the fourth heat medium three-way joint 35d is the same as that of the first heat medium three-way joint 35a.
  • the heat medium inlet side of the radiator 34 is connected to the outlet of the first three-way heat medium joint 35a.
  • the radiator 34 is a water/outside air heat exchange unit that exchanges heat between the heat medium flowing out from the first heat medium three-way joint 35a and the outside air.
  • the radiator 34 is arranged on the front side of the drive device room together with the outdoor heat exchanger 15 of the heat pump cycle 10a.
  • the radiator 34 When a heat medium having a temperature higher than the outside air temperature Tam flows into the radiator 34, the radiator 34 becomes a heat medium heat radiating part that radiates the heat of the heat medium to the outside air. Further, when a heat medium having a temperature lower than the outside air temperature Tam flows into the radiator 34, the radiator 34 becomes a heat medium heat absorbing part that causes the heat medium to absorb the outside air side heat of the outside air.
  • the inlet side of the second heat medium three-way joint 35b is connected to the heat medium outlet of the radiator 34.
  • One inlet side of the third heat medium three-way joint 35c is connected to one outlet of the second heat medium three-way joint 35b.
  • One inlet side of the fourth three-way heat medium joint 35d is connected to the other outlet of the second three-way heat medium joint 35b.
  • the other inlet side of the third heat medium three-way joint 35c is connected to the heat medium outlet of the heater core 32.
  • the inlet side of the high temperature side pump 31 is connected to the outlet of the third heat medium three-way joint 35c. Therefore, in the heat medium circuit 30a, the high temperature side three-way valve 33 switches the circuit configuration so that the heat medium flowing out from the heat medium passage of the water/refrigerant heat exchanger 13 flows into the heater core 32.
  • a similar heating section can be formed.
  • the inlet side of the heat medium passage of the chiller 20 is connected to the discharge port of the low temperature side pump 41 of the heat medium circuit 30a.
  • the outlet of the heat medium passage of the chiller 20 is connected to the inlet of a low-temperature side three-way valve 43 .
  • One outlet of the low-temperature side three-way valve 43 is connected to the inlet side of the cooling water passage 70a of the battery 70.
  • the other inlet side of the first heat medium three-way joint 35a is connected to the other outlet of the low-temperature side three-way valve 43.
  • the low temperature side three-way valve 43 controls the flow rate of the heat medium flowing into the cooling water passage 70a of the battery 70 and the heat medium flowing out from the heat medium passage of the chiller 20 into the radiator 34 via the first heat medium three-way joint 35a.
  • This is a three-type flow rate adjustment valve that can continuously adjust the flow rate ratio to the heat medium flow rate.
  • the basic configuration of the low-temperature side three-way valve 43 is the same as that of the high-temperature side three-way valve 33.
  • the low-temperature side three-way valve 43 can cause the entire flow rate of the heat medium flowing out of the heat medium passage of the chiller 20 to flow into the cooling water passage 70a of the battery 70. Further, the low temperature side three-way valve 43 can cause the entire flow rate of the heat medium flowing out from the heat medium passage of the chiller 20 to flow into the radiator 34 . Therefore, the low temperature side three-way valve 43 is an operation mode switching section that switches the operation mode by switching the circuit configuration.
  • One inlet side of the fourth heat medium three-way joint 35d is connected to the outlet of the cooling water passage 70a of the battery 70.
  • the inlet side of the low temperature side pump 41 is connected to the outflow port of the fourth three-way heat medium joint 35d.
  • the low temperature side three-way valve 43 causes the heat medium flowing out from the heat medium passage of the chiller 20 to flow into the cooling water passage 70a of the battery 70, so that the battery 70 generates heat in the heat medium. It is possible to absorb heat from the equipment side. Further, the low temperature side three-way valve 43 causes the heat medium flowing out from the heat medium passage of the chiller 20 to flow into the radiator 34, so that the heat medium can absorb the outside air side heat of the outside air.
  • the chiller 20 of this embodiment serves as a shared heat absorption part that causes the refrigerant to absorb at least one of the equipment side heat and the outside air side heat through the heat medium.
  • the cooling expansion valve 14c of this embodiment serves as a shared pressure reducing part that reduces the pressure of the refrigerant flowing into the chiller 20.
  • the low temperature side three-way valve 43 serves as an endothermic ratio adjusting section that adjusts the ratio of outside air side heat to equipment side heat in the heat absorbed by the refrigerant in the chiller 20 .
  • vehicle air conditioner 1a Other configurations of the vehicle air conditioner 1a are similar to the vehicle air conditioner 1 described in the first embodiment.
  • vehicle air conditioner 1a of this embodiment similarly to the vehicle air conditioner 1 described in the first embodiment, various driving modes are switched to air condition the vehicle interior and adjust the temperature of the battery 70. The detailed operation of each operation mode will be explained below.
  • the refrigerant discharged from the compressor 11 is transferred to the water-refrigerant heat exchanger 13, the cooling expansion valve 14b which is in the throttle state, the indoor evaporator 18, the accumulator 23, the compressor
  • the refrigerant circuit is switched to circulate in the order of the suction port of the machine 11.
  • control device 60 operates the high temperature side pump 31 so as to exhibit a predetermined reference pumping capacity. Further, the control device 60 controls the operation of the high temperature side three-way valve 33 so that the high temperature side heat medium temperature TWH detected by the high temperature side heat medium temperature sensor 63a approaches a predetermined reference high temperature side heat medium temperature KTWH. do.
  • the heat medium pumped from the high temperature side pump 31 circulates through the water/refrigerant heat exchanger 13, the heater core 32, and the suction port of the high temperature side pump 31 in this order.
  • the circuit is switched to a circuit in which the low-temperature heat medium pumped from the high-temperature pump 31 is circulated through the water-refrigerant heat exchanger 13, the radiator 34, and the suction port of the high-temperature pump 31 in this order.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the first embodiment. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • the water-refrigerant heat exchanger 13 functions as a condenser that radiates heat and condenses the refrigerant
  • the indoor evaporator 18 functions as an evaporator that evaporates the refrigerant.
  • a refrigeration cycle is constructed.
  • the suction side refrigerant pressure PS in the independent cooling mode is equivalent to that in the independent cooling mode of the first embodiment.
  • the heat medium flowing into the heat medium path of the water-refrigerant heat exchanger 13 exchanges heat with the refrigerant discharged from the compressor 11 and is heated.
  • the heat medium heated in the water-refrigerant heat exchanger 13 flows into the heater core 32 and the radiator 34 in response to the operation of the high temperature side three-way valve 33.
  • the heat medium that has flowed into the heater core 32 radiates heat to the blown air. This heats the blown air.
  • the heat medium flowing into the radiator 34 radiates heat to the outside air and is cooled.
  • the heat medium flowing out from the heater core 32 and the heat medium flowing out from the radiator 34 are sucked into the high temperature side pump 31 and pumped to the heat medium passage of the water/refrigerant heat exchanger 13.
  • cooling of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior.
  • the refrigerant discharged from the compressor 11 circulates in the same way as in the independent cooling mode.
  • the refrigerant discharged from the compressor 11 enters the refrigerant circuit, which circulates in the order of the water-refrigerant heat exchanger 13, the cooling expansion valve 14c in the throttled state, the chiller 20, the accumulator 23, and the suction port of the compressor 11.
  • control device 60 controls the operation of the high temperature side pump 31 and the high temperature side three-way valve 33, similarly to the independent cooling mode. Furthermore, the control device 60 operates the low-temperature side pump 41 so as to exhibit a predetermined reference pumping capacity. Further, the control device 60 controls the operation of the low temperature side three-way valve 43 so that the entire flow rate of the heat medium flowing out from the heat medium passage of the chiller 20 flows into the cooling water passage 70a of the battery 70.
  • the heat medium pumped from the high temperature side pump 31 circulates in the same way as in the independent cooling mode.
  • the circuit is switched so that the heat medium pumped from the low-temperature side pump 41 circulates in the order of the chiller 20, the cooling water passage 70a of the battery 70, and the suction port of the low-temperature side pump 41.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser, and the indoor evaporator 18 and chiller 20 function as evaporators.
  • the suction side refrigerant pressure PS in the cooling cooling mode is equivalent to that in the independent cooling mode.
  • the heat medium heated in the water/refrigerant heat exchanger 13 flows into the heater core 32 and the radiator 34 in accordance with the operation of the high temperature side three-way valve 33, as in the independent cooling mode. do.
  • the heat medium flowing into the heat medium passage of the chiller 20 is cooled by exchanging heat with the low pressure side refrigerant whose pressure has been reduced by the cooling expansion valve 14c.
  • the heat medium cooled by the chiller 20 flows into the cooling water passage 70a of the battery 70 via the low temperature side three-way valve 43.
  • the heat medium that has flowed into the cooling water passage 70a of the battery 70 absorbs equipment-side heat generated by the battery 70. This cools the battery 70.
  • the heat medium flowing out of the cooling water passage 70a of the battery 70 is sucked into the low temperature side pump 41 and is pumped to the heat medium passage of the chiller 20. Therefore, in the chiller 20 in the cooling cooling mode, the refrigerant absorbs the device-side heat generated by the battery 70 via the low-temperature side heat medium.
  • cooling of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, as in the independent cooling mode.
  • (b-1) Independent dehumidification heating mode
  • the control device 60 sets the cooling expansion valve 14b to the throttle state, the cooling expansion valve 14c to the fully closed state, and the bypass side flow rate adjustment valve 14d is fully closed. Therefore, in the heat pump cycle 10a in the independent dehumidifying heating mode, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates, as in the independent cooling mode.
  • control device 60 operates the high temperature side pump 31 so as to exhibit a predetermined reference pumping capacity. Further, the control device 60 controls the operation of the high-temperature side three-way valve 33 so that the entire flow rate of the heat medium flowing out from the water-refrigerant heat exchanger 13 flows into the heater core 32.
  • the heat medium pumped from the high temperature side pump 31 circulates through the water/refrigerant heat exchanger 13, the heater core 32, and the suction port of the high temperature side pump 31 in this order.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser and the indoor evaporator 18 functions as an evaporator.
  • the suction side refrigerant pressure PS in the independent dehumidifying/heating mode is equivalent to that in the independent cooling mode.
  • the heat medium heated in the water/refrigerant heat exchanger 13 is force-fed to the heater core 32.
  • the blown air that has been cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 32. Then, the temperature-adjusted blast air is blown into the vehicle interior, thereby realizing dehumidification and heating of the vehicle interior.
  • the control device 60 controls the operation of the high temperature side pump 31 and the high temperature side three-way valve 33, similarly to the independent dehumidifying heating mode. Furthermore, the control device 60 operates the low-temperature side pump 41 so as to exhibit a predetermined reference pumping capacity. Further, the control device 60 controls the operation of the low temperature side three-way valve 43 so that the entire flow rate of the heat medium flowing out from the heat medium passage of the chiller 20 flows into the cooling water passage 70a of the battery 70.
  • the heat medium pumped from the high temperature side pump 31 circulates in the same manner as in the independent dehumidifying and heating mode. Further, the heat medium pumped from the low temperature side pump 41 circulates through the chiller 20, the cooling water passage 70a of the battery 70, and the suction port of the low temperature side pump 41 in this order.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the first embodiment. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser, and the indoor evaporator 18 and chiller 20 function as evaporators.
  • the suction side refrigerant pressure PS in the cooling, dehumidifying, and heating mode is equivalent to that in the independent cooling mode.
  • the heat medium heated in the water/refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent dehumidifying and heating mode. Further, the heat medium cooled by the chiller 20 flows into the cooling water passage 70a of the battery 70. The heat medium that has flowed into the cooling water passage 70a of the battery 70 absorbs the device-side heat generated by the battery 70, similarly to the cooling cooling mode. This cools the battery 70.
  • dehumidification and heating in the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, similarly to the independent dehumidification and heating mode.
  • the control device 60 controls the operation of the high temperature side pump 31 and the high temperature side three-way valve 33, similarly to the independent dehumidification heating mode. Furthermore, the control device 60 operates the low-temperature side pump 41 so as to exhibit a predetermined reference pumping capacity. Further, the control device 60 controls the operation of the low-temperature side three-way valve 43 so that the entire flow rate of the heat medium flowing out from the heat medium passage of the chiller 20 flows into the radiator 34 .
  • the heat medium pumped from the high temperature side pump 31 circulates in the same manner as in the independent dehumidification heating mode, as shown by the broken line arrow in FIG.
  • the circuit is switched so that the heat medium pumped from the low temperature side pump 41 circulates through the chiller 20, the radiator 34, and the suction port of the low temperature side pump 41 in this order.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 functions as a condenser and the chiller 20 functions as an evaporator.
  • the suction side refrigerant pressure PS in the independent outside air endothermic heating mode is equivalent to that in the independent outside air endothermic heating mode of the first embodiment. Therefore, the refrigerant pressure within the accumulator 23 during the independent outside air heat absorption heating mode tends to be lower than the refrigerant pressure within the accumulator 23 during the independent cooling mode.
  • the heat medium heated in the water-refrigerant heat exchanger 13 is force-fed to the heater core 32, similarly to the independent dehumidification heating mode. Further, the heat medium cooled by the chiller 20 flows into the radiator 34. The heat medium that has flowed into the radiator 34 absorbs heat from the outside air. The heat medium that has absorbed the outside air side heat in the radiator 34 is sucked into the low temperature side pump 41 and is pumped to the heat medium passage of the chiller 20.
  • the air blown from the indoor blower 52 passes through the indoor evaporator 18.
  • the blown air that has passed through the indoor evaporator 18 is heated by exchanging heat with the high temperature side heat medium in the heater core 32 according to the opening degree of the air mix door 54 .
  • the blown air whose temperature is adjusted so as to approach the target blowout temperature TAO is blown into the vehicle interior. This achieves heating of the vehicle interior.
  • the control device 60 sets the cooling expansion valve 14b to the fully closed state, the cooling expansion valve 14c to the throttle state, and controls the bypass side flow rate.
  • the regulating valve 14d is fully closed. Therefore, in the heat pump cycle 10a in the cooling outside air endothermic heating mode, the refrigerant circuit is switched to the same refrigerant circuit as in the independent outside air endothermic heating mode.
  • control device 60 controls the operation of the high temperature side pump 31 and the high temperature side three-way valve 33, similarly to the independent dehumidification heating mode.
  • control device 60 operates the low-temperature side pump 41 so as to exhibit a predetermined reference pumping capacity. Further, the control device 60 controls the operation of the low temperature side three-way valve 43 so that the low temperature side heat medium temperature TWL detected by the low temperature side heat medium temperature sensor 63b approaches a predetermined reference low temperature side heat medium temperature KTWL. do.
  • the heat medium pumped from the high temperature side pump 31 circulates in the same way as in the independent outside air endothermic heating mode. Further, the heat medium pumped from the low temperature side pump 41 circulates through the chiller 20, the cooling water passage 70a of the battery 70, and the suction port of the low temperature side pump 41 in this order. At the same time, the circuit is switched so that the heat medium pumped from the low temperature side pump 41 circulates through the chiller 20, the radiator 34, and the suction port of the low temperature side pump 41 in this order.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is used in which the water/refrigerant heat exchanger 13 functions as a condenser and the chiller 20 functions as an evaporator, as in the independent outside air absorption heating mode. configured.
  • the suction side refrigerant pressure PS in the cooling outside air endothermic heating mode is the same as that in the independent outside air endothermic heating mode.
  • the heat medium heated in the water/coolant heat exchanger 13 is force-fed to the heater core 32, similarly to the cooling dehumidifying heating mode.
  • the heat medium cooled by the chiller 20 flows into the cooling water passage 70a of the battery 70 and the radiator 34 in response to the operation of the low temperature side three-way valve 43.
  • the heat medium flowing into the cooling water passage 70a of the battery 70 absorbs equipment-side heat generated by the battery 70.
  • the heat medium that has flowed into the radiator 34 absorbs heat from the outside air. Therefore, in the chiller 20 in the cooling outside air endothermic heating mode, the refrigerant absorbs equipment side heat and outside air side heat via the low temperature side heat medium in response to the operation of the low temperature side three-way valve 43.
  • heating of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, as in the independent outside air endothermic heating mode.
  • control device 60 controls the operation of the high temperature side pump 31 and the high temperature side three-way valve 33, similarly to the independent dehumidification heating mode. Furthermore, the control device 60 controls the operation of the low-temperature side pump 41 and the low-temperature side three-way valve 43 similarly to the cooling cooling mode.
  • the heat medium pumped from the high temperature side pump 31 circulates as in the independent dehumidification heating mode, as shown by the broken line arrow in FIG. Further, the heat medium pumped from the low-temperature side pump 41 circulates in the same manner as in the cooling cooling mode.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • a vapor compression type refrigeration cycle is used in which the water/refrigerant heat exchanger 13 functions as a condenser and the chiller 20 functions as an evaporator, as in the independent outside air absorption heating mode. configured.
  • the suction side refrigerant pressure PS during the waste heat recovery heating mode is equivalent to the waste heat recovery heating mode of the first embodiment. Therefore, the refrigerant pressure within the accumulator 23 during the waste heat recovery heating mode tends to be higher than the refrigerant pressure within the accumulator 23 during the independent outside air heat absorption heating mode.
  • the heat medium heated in the water-refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent dehumidification heating mode. Further, similarly to the cooling mode, the heat medium cooled by the chiller 20 is force-fed to the cooling water passage 70a of the battery 70.
  • heating of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, similarly to the independent outside air absorption heating mode.
  • the control device 60 controls the operation of the high temperature side pump 31 and the high temperature side three-way valve 33, similarly to the independent dehumidification heating mode. Furthermore, the control device 60 stops the low temperature side pump 41. Therefore, in the heat medium circuit 30a in the hot gas heating mode, the heat medium pumped from the high temperature side pump 31 circulates as in the independent dehumidifying heating mode, as shown by the broken line arrow in FIG.
  • control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mix door 54, etc., as in the independent cooling mode. Furthermore, the control device 60 appropriately controls the operations of other controlled devices.
  • the heat pump cycle 10a in the hot gas heating mode operates similarly to the hot gas heating mode of the first embodiment. Therefore, in the hot gas heating mode, the suction side refrigerant pressure PS is adjusted to be higher than in all heating modes.
  • the high temperature side heat medium heated in the water-refrigerant heat exchanger 13 is force-fed to the heater core 32, as in the independent dehumidification heating mode.
  • heating of the vehicle interior is achieved by blowing temperature-adjusted blast air into the vehicle interior, similarly to the independent outside air endothermic heating mode.
  • the vehicle air conditioner 1a of this embodiment by switching the driving mode, it is possible to comfortably air condition the vehicle interior and appropriately adjust the temperature of the battery 70, which is an on-vehicle device.
  • liquid volume reduction control is performed when switching from the first operation mode to the second operation mode.
  • the hot gas heating mode when defined as the first operation mode, the independent outside air endothermic heating mode, the cooling outside air endothermic heating mode, and the waste heat recovery heating mode can be defined as the second operation mode.
  • the recovery channel 24a runs from one outlet of the seventh three-way joint 12g to the fifth three-way joint via the cooling expansion valve 14b and the indoor evaporator 18. It is formed by a refrigerant flow path leading to the joint 12e.
  • the independent outside air endothermic heating mode and the cooled outside air endothermic heating mode can be defined as the second operation mode.
  • the recovery channel 24a runs from one outlet of the seventh three-way joint 12g to the fifth via the cooling expansion valve 14b and the indoor evaporator 18. It is formed by a refrigerant flow path leading to the three-way joint 12e.
  • the operation of each component device is controlled as shown in the time charts of FIGS. 15 and 16.
  • the time chart of FIG. 15 shows an example in which the hot gas heating mode is defined as the first operation mode, and the independent outside air heat absorption heating mode is defined as the second operation mode.
  • the cooling expansion valve 14b is changed from the fully closed state to the throttle state. That is, in the liquid volume reduction control, the cooling expansion valve 14b is opened. At this time, the opening degree of the cooling expansion valve 14b is set to a minute opening degree that does not affect the high-low pressure balance of the heat pump cycle 10a in the hot gas heating mode.
  • the refrigerant flows into the recovery channel 24a. That is, a part of the high-pressure side refrigerant flowing out from the water-refrigerant heat exchanger 13 flows into the indoor evaporator 18 via the cooling expansion valve 14b. The refrigerant that has flowed into the indoor evaporator 18 is condensed and stored within the indoor evaporator 18 . As a result, the amount of liquid phase refrigerant in the accumulator 23 is reduced.
  • the liquid volume reduction control is ended after the predetermined collection time Tmc has elapsed. After the liquid volume reduction control ends, the mode is switched to the independent outside air heat absorption heating mode.
  • the hot gas heating mode is defined as the first operation mode and the cooled outside air endothermic heating mode is defined as the second operation mode
  • the same liquid volume reduction control as in FIG. 15 may be performed.
  • the independent outside air heat absorption heating mode is defined as the second operation mode
  • the low temperature The operation of the side three-way valve 43 may be controlled.
  • the hot gas heating mode is defined as the first operation mode and the waste heat recovery heating mode is defined as the second operation mode
  • the same liquid volume reduction control as in FIG. 15 may be performed.
  • the total flow rate of the heat medium flowing out from the heat medium passage of the chiller 20 is the cooling water of the battery 70.
  • the operation of the low temperature side three-way valve 43 may be controlled so that the water flows into the passage 70a.
  • the low-temperature side is Although an example in which the operation of the three-way valve 43 is controlled is illustrated, the present invention is not limited to this.
  • the opening degree of the low temperature side three-way valve 43 may be any degree.
  • the time chart in FIG. 16 shows an example in which the waste heat recovery heating mode is defined as the first operation mode, and the independent outside air heat absorption heating mode is defined as the second operation mode. Also in the liquid volume reduction control shown in FIG. 16, the cooling expansion valve 14b is changed from the fully closed state to the throttle state. Thereby, the amount of liquid phase refrigerant in the accumulator 23 can be reduced similarly to the liquid amount reduction control shown in FIG.
  • the same liquid volume reduction control as in FIG. 16 may be performed.
  • the low temperature side heat medium temperature TWL approaches the reference low temperature side heat medium temperature KTWL.
  • the operation of the low temperature side three-way valve 43 may be controlled.
  • the liquid amount reduction control is performed when switching from the first operation mode to the second operation mode, the same effects as in the first embodiment can be obtained. I can do it. That is, even in a heat pump cycle device that includes an accumulator 23 and is configured to be able to switch operation modes, like the vehicle air conditioner 1a of the present embodiment, the compressor 11 can be appropriately protected.
  • the vehicle air conditioner 1 of this embodiment can operate in the (a) cooling mode, (b) dehumidification heating mode, and (c) heating mode described in the first embodiment.
  • the waste heat recovery heating mode is defined as the first operation mode
  • the independent outside air endothermic heating mode or the cooling outside air endothermic heating mode is defined as the second operation mode.
  • the compressor 11 can be appropriately protected even if the heat pump cycle device includes the accumulator 23 and is configured to be able to switch the operation mode.
  • the heat pump cycle device according to the present disclosure was applied to a vehicle air conditioner, but the application target of the heat pump cycle device is not limited to a vehicle air conditioner.
  • the present invention may be applied to an air conditioner that only air-conditions a space to be air-conditioned without adjusting the temperature of a heat-generating device.
  • the present invention may be applied to a water heater that heats household water or the like as an object to be heated.
  • the temperature of the battery 70 is adjusted as an in-vehicle device whose temperature is to be adjusted, but the in-vehicle device is not limited to the battery 70.
  • the temperature of an inverter, PCU, transaxle, ADAS control device, etc. may be adjusted.
  • the temperature of a plurality of in-vehicle devices may be adjusted.
  • the inverter supplies power to the motor generator, etc.
  • the PCU is a power control unit that performs power transformation and power distribution.
  • a transaxle is a power transmission mechanism that integrates a transmission, differential gear, etc.
  • a control device for ADAS is a control device for an advanced driving support system.
  • the configuration of the heat pump cycle device according to the present disclosure is not limited to the configuration disclosed in the above-described embodiments.
  • a heating section is formed by each component of the water-refrigerant heat exchanger 13 and the high-temperature side heat medium circuit 30, or each component of the water-refrigerant heat exchanger 13 and the heat medium circuit 30a.
  • a heating section is formed by each component of the water-refrigerant heat exchanger 13 and the high-temperature side heat medium circuit 30, or each component of the water-refrigerant heat exchanger 13 and the heat medium circuit 30a.
  • it is not limited to this.
  • an indoor condenser may be used as the heating section.
  • the indoor condenser is a heating heat exchange unit that heats the blown air by exchanging heat between one discharged refrigerant branched at the first three-way joint 12a and the blown air that has passed through the indoor evaporator 18. Then, the indoor condenser may be placed in the air passage of the indoor air conditioning unit 50 in the same manner as the heater core 32.
  • the refrigerant flowing out from the bypass side flow rate adjustment valve 14d and the refrigerant flowing out from the refrigerant passage of the chiller 20 are homogeneous when flowing through the refrigerant piping from the accumulator 23 and the sixth three-way joint 12f to the suction side of the compressor 11. mixed with For example, the sixth three-way joint 12f may be abolished and the end of the bypass passage 21a may be directly connected to the accumulator 23.
  • the present invention is not limited to this.
  • the high-temperature side heat medium circuit 30 and the low-temperature side heat medium circuit 40 that are independent of each other may be employed.
  • the high temperature side three-way valve 33 and the high temperature side radiator may be arranged in the high temperature side heat medium circuit 30.
  • the high temperature side radiator is a high temperature side heat medium heat radiator that exchanges heat between the high temperature side heat medium and the outside air discharge.
  • the high temperature side three-way valve 33 may be arranged so as to be able to adjust the flow rate ratio between the flow rate of the high temperature side heat medium flowing into the heater core 32 and the flow rate of the high temperature side heat medium flowing into the high temperature side radiator.
  • the low temperature side three-way valve 43 and the low temperature side radiator may be arranged in the low temperature side heat medium circuit 40.
  • the low temperature side radiator is a high temperature side heat medium heat radiator that exchanges heat between the low temperature side heat medium and the outside air discharge.
  • the low temperature side three-way valve 43 may be arranged to be able to adjust the flow rate ratio between the flow rate of the low temperature side heat medium flowing into the cooling water passage 70a of the battery 70 and the flow rate of the low temperature side heat medium flowing into the low temperature side radiator.
  • the evaporation pressure adjustment valve is a variable throttle mechanism that maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a predetermined temperature (for example, a temperature at which the indoor evaporator 18 can be suppressed) or higher.
  • a variable throttle mechanism configured with a mechanical mechanism that increases the valve opening degree as the pressure of the refrigerant on the refrigerant outlet side of the indoor evaporator 18 increases may be adopted. Further, as the evaporation pressure regulating valve, a variable throttle mechanism configured with an electrical mechanism similar to the heating expansion valve 14a or the like may be employed.
  • R1234yf was adopted as the refrigerant of the heat pump cycles 10 and 10a, but the present invention is not limited to this.
  • R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted.
  • a mixed refrigerant made by mixing a plurality of these refrigerants may be used.
  • a supercritical refrigeration cycle may be constructed in which carbon dioxide is used as the refrigerant, and the refrigerant pressure on the high-pressure side is equal to or higher than the critical pressure of the refrigerant.
  • PAG oil i.e., polyalkylene glycol oil
  • POE polyol ester
  • an aqueous ethylene glycol solution was used as the heat medium, the low-temperature side heat medium, and the high-temperature side heat medium, but the present invention is not limited thereto.
  • a solution containing dimethylpolysiloxane or a nanofluid, an antifreeze solution, an aqueous liquid refrigerant containing alcohol, a liquid medium containing oil, etc. may be used.
  • control sensor group connected to the input side of the control device 60 is not limited to the detection unit disclosed in the above embodiment. Various detection units may be added as necessary.
  • control mode of the heat pump cycle device according to the present disclosure is not limited to the control mode disclosed in the above-described embodiments.
  • vehicle air conditioners 1 and 1a that can execute various operation modes have been described, but the heat pump cycle device according to the present disclosure does not need to be able to execute all of the above-mentioned operation modes. As long as it is possible to execute a combination of driving modes corresponding to at least one set of the first driving mode and the second driving mode, the same effects as in the above-described embodiment can be obtained.
  • the vehicle air conditioners 1 and 1a may be capable of executing other operation modes. For example, it may be possible to execute an equipment cooling mode in which only the battery 70 is cooled without performing air conditioning in the vehicle interior. Specifically, when executing the device cooling mode, the control device 60 switches the refrigerant circuits of the heat pump cycles 10 and 10a in the same way as in the cooling cooling mode, and brings the cooling expansion valve 14b into a fully closed state. Furthermore, the control device 60 may stop the indoor blower 52.
  • the water-refrigerant heat exchanger 13, the outdoor heat exchanger 15, and the indoor evaporator 18 are connected in series to the flow of the refrigerant discharged from the compressor 11. It may also be possible to execute a series dehumidifying and heating mode in which the vehicle interior is dehumidified and heated by being connected to the system. Furthermore, it is possible to execute a parallel dehumidification heating mode in which the outdoor heat exchanger 15 and the indoor evaporator 18 are connected in parallel to the flow of refrigerant flowing out from the water-refrigerant heat exchanger 13 to dehumidify and heat the vehicle interior. It may be.
  • the cooling expansion valve 14c is in the throttled state in the independent dehumidification/heating mode. Then, the low-temperature side pump 41 is operated, and the outside air heat absorption dehumidification/heating mode is executed in which the operation of the low-temperature side three-way valve 43 is controlled so that the entire flow rate of the heat medium flowing out from the heat medium passage of the chiller 20 flows into the radiator 34. It may be possible.
  • the characteristics of the heat pump cycle device disclosed in this specification are shown below.
  • (Item 1) an accumulator (23) that separates the refrigerant into gas and liquid and stores the separated liquid phase refrigerant; a compressor (11) that sucks and compresses the gas phase refrigerant separated in the accumulator;
  • the operation modes to which the operation mode switching unit can switch include a first operation mode and a second operation mode in which the suction side refrigerant pressure (PS), which is the refrigerant pressure in the accumulator, is lower than in the first operation mode.
  • PS suction side refrigerant pressure
  • a recovery flow path (24, 24a) through which the refrigerant can flow is formed in the refrigerant flow path through which the refrigerant does not flow when the operation mode switching unit switches to the first operation mode. Ori, When the operation mode switching unit switches the operation mode from the first operation mode to the second operation mode, the amount of liquid phase refrigerant in the accumulator is reduced by causing the refrigerant to flow into the recovery channel.
  • a heat pump cycle device that controls liquid volume reduction. (Item 2) The heat pump cycle device according to item 1, wherein the recovery flow path is formed to be able to connect a region on the high pressure side through which the refrigerant flows and a region on the low pressure side through which the refrigerant flows during the first operation mode.
  • the heat pump cycle device according to item 1 or 2, wherein the recovery flow path is formed in a region through which the refrigerant flows during the second operation mode.
  • (Item 4) a discharge side branching part (12a) that branches the flow of the refrigerant discharged from the compressor; a heating section (13, 30) that heats an object to be heated using the refrigerant flowing out from one outlet of the discharge side branch section as a heat source; a bypass passage (21a) through which the refrigerant flowing out from the other outlet of the discharge side branch portion flows; an outside air heat absorption part (15) that causes the refrigerant to absorb outside air side heat possessed by outside air;
  • the operation mode switching section includes an outside air pressure reducing section (14a) that reduces the pressure of the refrigerant flowing into the outside air heat absorption section, and a bypass side flow rate adjustment section (14d) that adjusts the flow rate of the refrigerant flowing through the bypass passage.
  • the operation mode switching section includes: In the first operation mode, the refrigerant discharged from the compressor circulates in the order of the discharge side branch section, the heating section, the accumulator, and the suction port of the compressor. switching to a refrigerant circuit that circulates in the order of the bypass passage, the accumulator, and the suction port of the compressor; In the second operation mode, the refrigerant discharged from the compressor is circulated in the order of the heating section, the outside air decompression section, the outside air heat absorption section, the accumulator, and the suction port of the compressor.
  • the heat pump cycle device according to any one of switching items 1 to 3.
  • a heating unit (13, 30) that heats an object to be heated using the refrigerant discharged from the compressor as a heat source; an outside air heat absorption part (15) that causes the refrigerant to absorb outside air side heat possessed by outside air; an equipment heat absorption part (20) that causes the refrigerant to absorb equipment-side heat generated by a heat-generating equipment (70) that generates heat during operation;
  • the operation mode switching section includes an outside air pressure reducing section (14a) that reduces the pressure of the refrigerant flowing into the outside air heat absorption section, and an equipment pressure reducing section (14c) that reduces the pressure of the refrigerant flowing into the equipment heat absorption section.
  • the operation mode switching section includes: During the first operation mode, the refrigerant discharged from the compressor is switched to a refrigerant circuit in which it circulates through the heating section, the device pressure reducing section, the device heat absorption section, the accumulator, and the suction port of the compressor. , During the second operation mode, the refrigerant discharged from the compressor is switched to a refrigerant circuit in which it circulates through the heating section, the outside air pressure reducing section, the outside air heat absorption section, the accumulator, and the suction port of the compressor.
  • the heat pump cycle device according to any one of items 1 to 3.
  • the outside air pressure reducing part and the outside air heat absorption part form the recovery flow path, The heat pump cycle device according to item 4 or 5, in which, in the liquid volume reduction control, the outside air pressure reducing section is opened.
  • (Item 7) a discharge side branching part (12a) that branches the flow of the refrigerant discharged from the compressor; a heating section (13, 30) that heats an object to be heated using the refrigerant flowing out from one outlet of the discharge side branch section as a heat source; a bypass passage (21a) through which the refrigerant flowing out from the other outlet of the discharge side branch portion flows; an equipment heat absorption part (20) that causes the refrigerant to absorb equipment-side heat generated by a heat-generating equipment (70) that generates heat during operation;
  • the operation mode switching section includes an equipment pressure reducing part (14c) that reduces the pressure of the refrigerant flowing into the equipment heat absorption part (20), and a bypass side flow rate adjustment part that adjusts the flow rate of the refrigerant flowing
  • the operation mode switching section includes: In the first operation mode, the refrigerant discharged from the compressor circulates in the order of the discharge side branch section, the heating section, the accumulator, and the suction port of the compressor. switching to a refrigerant circuit that circulates in the order of the bypass passage, the accumulator, and the suction port of the compressor; In the second operation mode, the refrigerant discharged from the compressor is passed through a refrigerant circuit that circulates in the order of the heating section, the device pressure reducing section, the device heat absorption section, the accumulator, and the suction port of the compressor.
  • the heat pump cycle device according to switching item 1 or 2.
  • the operation mode switching unit includes a common pressure reducing unit (14c) that reduces the pressure of the refrigerant flowing into the common heat absorption unit, a bypass side flow rate adjustment unit (14d) that adjusts the flow rate of the refrigerant flowing through the bypass passage, and the It has a heat absorption ratio adjustment part (43) that adjusts the ratio of the outside air side heat and the equipment side heat in the heat
  • a heating unit (13, 30a) that heats an object to be heated using the refrigerant discharged from the compressor as a heat source; a shared heat absorption part (20) that causes the refrigerant to absorb at least one of the outside air-side heat possessed by the outside air and the equipment-side heat generated by the heat-generating equipment (70) that generates heat during operation;
  • the operation mode switching section includes a common pressure reducing section (14c) that reduces the pressure of the refrigerant flowing into the common heat absorption section, and a switch between the outside air side heat and the equipment side heat in the heat absorbed by the refrigerant in the common heat absorption section.
  • the operation mode switching section includes: During the first operation mode, switching to a refrigerant circuit in which the refrigerant discharged from the compressor circulates in the order of the heating section, the common pressure reducing section, the common heat absorption section, the accumulator, and the suction port of the compressor, Further, the common heat absorption section causes the equipment side heat to be absorbed by the refrigerant, During the second operation mode, switching to a refrigerant circuit in which the refrigerant discharged from the compressor circulates in the order of the heating section, the common pressure reducing section, the common heat absorption section, the accumulator, and the suction port of the compressor, Furthermore, the heat pump cycle device according to item 1 or 2, in which the outside air side heat is absorbed by the refrigerant in the shared heat absorption part.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

La présente invention concerne un dispositif à cycle de pompe à chaleur qui comprend un accumulateur (23), un compresseur (11) et une unité de commutation de mode de fonctionnement (14a à 14d, 22a, 22b, 43). L'unité de commutation de mode de fonctionnement permet de commuter entre un premier mode de fonctionnement et un second mode de fonctionnement dans lequel une pression de fluide frigorigène côté aspiration est inférieure à celle dans le premier mode de fonctionnement. Un passage d'écoulement de récupération (24) dans lequel le fluide frigorigène peut s'écouler est formé dans un passage d'écoulement de fluide frigorigène à travers lequel le fluide frigorigène ne s'écoule pas lorsque l'unité de commutation de mode de fonctionnement commute vers le premier mode de fonctionnement. Le dispositif à cycle de pompe à chaleur effectue une commande de réduction de quantité de liquide pour réduire une quantité de fluide frigorigène en phase liquide dans l'accumulateur (23) en permettant au fluide frigorigène de s'écouler dans le passage d'écoulement de récupération (24) lorsque l'unité de commutation de mode de fonctionnement passe du premier mode de fonctionnement au second mode de fonctionnement.
PCT/JP2023/014692 2022-04-15 2023-04-11 Dispositif à cycle de pompe à chaleur WO2023199912A1 (fr)

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JP2022-067683 2022-04-15

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011140291A (ja) * 2010-01-11 2011-07-21 Denso Corp 車両用空調装置
JP2017149365A (ja) * 2016-02-26 2017-08-31 サンデン・オートモーティブクライメイトシステム株式会社 車両用空気調和装置
JP2020050155A (ja) * 2018-09-27 2020-04-02 サンデン・オートモーティブクライメイトシステム株式会社 車両用空気調和装置
JP2021156567A (ja) * 2019-11-22 2021-10-07 株式会社デンソー 冷凍サイクル装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011140291A (ja) * 2010-01-11 2011-07-21 Denso Corp 車両用空調装置
JP2017149365A (ja) * 2016-02-26 2017-08-31 サンデン・オートモーティブクライメイトシステム株式会社 車両用空気調和装置
JP2020050155A (ja) * 2018-09-27 2020-04-02 サンデン・オートモーティブクライメイトシステム株式会社 車両用空気調和装置
JP2021156567A (ja) * 2019-11-22 2021-10-07 株式会社デンソー 冷凍サイクル装置

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