WO2020050040A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2020050040A1
WO2020050040A1 PCT/JP2019/032752 JP2019032752W WO2020050040A1 WO 2020050040 A1 WO2020050040 A1 WO 2020050040A1 JP 2019032752 W JP2019032752 W JP 2019032752W WO 2020050040 A1 WO2020050040 A1 WO 2020050040A1
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WO
WIPO (PCT)
Prior art keywords
temperature
heating
refrigerant
mode
cooling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/032752
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
和弘 多田
賢吾 杉村
寛幸 小林
祐一 加見
伊藤　誠司
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Priority to CN201980057572.4A priority Critical patent/CN112638674B/zh
Priority to DE112019004481.8T priority patent/DE112019004481T5/de
Publication of WO2020050040A1 publication Critical patent/WO2020050040A1/ja
Priority to US17/191,487 priority patent/US12038207B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • 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
    • B60H1/32—Cooling devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/02—Arrangement in connection with cooling of propulsion units with liquid cooling
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries

Definitions

  • the present disclosure relates to a refrigeration cycle device applied to an air conditioner.
  • Patent Document 1 a technology described in Patent Document 1 is known as a refrigeration cycle device applied to an air conditioner.
  • the refrigeration cycle device described in Patent Literature 1 is applied to an air conditioner and is configured to be able to cool a secondary battery as a temperature adjustment target.
  • the refrigeration cycle device of Patent Document 1 includes a heating unit that heats blast air blown into a space to be air-conditioned using a high-pressure refrigerant discharged from a compressor as a heat source, and an indoor evaporator that cools blast air by evaporating a low-pressure refrigerant. And a cooling unit for evaporating the low-pressure refrigerant to cool the battery.
  • the heating unit was connected to a water-refrigerant heat exchanger for exchanging heat between the high-pressure refrigerant and the high-temperature side heat medium, a heater core for exchanging heat between the high-temperature side heat medium and the blast air to heat the blast air, and the like. It is composed of a high-temperature side heat medium circuit.
  • the cooling unit is a chiller for exchanging heat between the low-pressure refrigerant and the battery-side heat medium, and a battery-side heat connected to a heat exchange unit for cooling the secondary battery by exchanging heat between the battery-side heat medium and the secondary battery. It is composed of a medium circuit.
  • a secondary battery as disclosed in Patent Literature 1 has a feature that the output tends to decrease at low temperatures and the deterioration tends to progress at high temperatures. For this reason, the temperature of the secondary battery needs to be maintained within an appropriate temperature range in which the charge / discharge capacity of the secondary battery can be sufficiently utilized.
  • the refrigeration cycle apparatus described in Patent Literature 1 can cool the secondary battery in the cooling unit, but cannot warm up the secondary battery. Therefore, in the refrigeration cycle device of Patent Literature 1, there is a possibility that appropriate temperature adjustment cannot be performed on the secondary battery that is the object of temperature adjustment.
  • the present disclosure has been made in view of these points, and provides a refrigeration cycle device that can achieve both appropriate temperature adjustment of blast air blown into a space to be air-conditioned and appropriate temperature adjustment of a temperature adjustment target.
  • the purpose is to do.
  • the refrigeration cycle device is a compressor, an outdoor heat exchanger, a cooling decompression unit, an evaporator, a branch, a cooling decompression unit, a temperature adjustment unit, and a junction. , A bypass passage, and a first on-off valve.
  • the compressor compresses and discharges the refrigerant.
  • the outdoor heat exchanger exchanges heat between the refrigerant discharged from the compressor and the outside air.
  • the cooling decompression unit decompresses the refrigerant flowing out of the outdoor heat exchanger.
  • the evaporator evaporates the refrigerant flowing out of the cooling decompression unit and absorbs heat from the blast air blown to the air-conditioned space.
  • the branching section is connected so that a part of the flow of the refrigerant flowing out of the outdoor heat exchanger branches off from the flow toward the cooling decompression section.
  • the cooling decompression section decompresses the refrigerant branched at the branch section.
  • the temperature adjustment unit has a temperature adjustment heat exchange unit that exchanges heat with the refrigerant flowing out of the cooling decompression unit, and adjusts the temperature of the temperature adjustment target using the refrigerant passing through the temperature adjustment heat exchange unit as a heat source.
  • the junction joins the flow of the refrigerant flowing out of the evaporator and the flow of the refrigerant flowing out of the temperature adjustment unit, and guides the flow to the suction port side of the compressor.
  • the bypass passage guides the refrigerant discharged from the compressor to the upstream side of the branch portion, bypassing the outdoor heat exchanger.
  • the first on-off valve is disposed in the bypass passage and opens and closes the bypass passage.
  • the outdoor heat exchanger functions as a radiator
  • the evaporator and the temperature control heat exchange unit function as a heat absorber
  • the refrigeration cycle device guides the discharge refrigerant discharged from the compressor to the temperature-regulating heat exchange unit via the bypass passage, and transfers the heat of the discharge refrigerant.
  • the temperature adjustment target is heated.
  • the heat of the discharged refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, and the refrigerant flowing out of the outdoor heat exchanger is branched at the branch portion.
  • One of them is decompressed by the cooling decompression unit, and can absorb heat from the blown air by the evaporator.
  • coolant branched by the branch part can be decompressed by the cooling decompression part, and can be made to absorb heat from a temperature adjustment target object through a temperature adjustment part.
  • the refrigeration cycle apparatus can supply the blast air cooled by the evaporator to the space to be air-conditioned and also cool the temperature adjustment target by the temperature adjustment unit.
  • the refrigerant discharged from the compressor can be guided to the heat exchange unit for temperature control via the bypass passage.
  • the refrigeration cycle apparatus can heat and warm up the temperature adjustment target using the heat of the discharged refrigerant as a heat source.
  • the refrigeration cycle device adjusts the temperature of the air to be blown and heats and cools the object to be temperature-controlled, thereby achieving both air conditioning of the space to be air-conditioned and appropriate temperature adjustment to the object to be temperature-controlled. it can.
  • FIG. 1 is a schematic configuration diagram of a vehicle air conditioner according to one embodiment
  • FIG. 2 is a block diagram showing a control system of the vehicle air conditioner according to one embodiment
  • FIG. 3 is a Mollier diagram showing a change in the state of the refrigerant in the single warm-up mode of the refrigeration cycle device according to one embodiment
  • FIG. 4 is a Mollier chart showing a change in the state of the refrigerant in a heating and warming-up mode of the refrigeration cycle device according to one embodiment
  • FIG. 1 is a schematic configuration diagram of a vehicle air conditioner according to one embodiment
  • FIG. 2 is a block diagram showing a control system of the vehicle air conditioner according to one embodiment
  • FIG. 3 is a Mollier diagram showing a change in the state of the refrigerant in the single warm-up mode of the refrigeration cycle device according to one embodiment
  • FIG. 4 is a Mollier chart showing a change in the state of the refrigerant in a heating and warming-up mode of the refrigeration cycle device according to one embodiment
  • FIG. 5 is a Mollier diagram showing a change in the state of the refrigerant in the cooling priority mode in the first heating / cooling mode of the refrigeration cycle device according to one embodiment
  • FIG. 6 is a Mollier diagram showing a change in the state of the refrigerant in the heating priority mode in the first heating / cooling mode of the refrigeration cycle apparatus according to one embodiment.
  • FIG. 1 is a schematic configuration diagram of a vehicle air conditioner 1 according to the present embodiment.
  • the refrigeration cycle device 10 is applied to the vehicle air conditioner 1 mounted on an electric vehicle that obtains driving power for traveling from an electric motor.
  • the vehicle air conditioner 1 has a function of adjusting the temperature of the battery 80 as well as performing air conditioning of a vehicle interior, which is a space to be air-conditioned. For this reason, the vehicle air conditioner 1 can also be called an air conditioner with a battery temperature adjustment function.
  • the battery 80 is a secondary battery that stores power supplied to on-vehicle devices such as an electric motor.
  • the battery 80 of the present embodiment is a lithium ion battery.
  • the battery 80 is a so-called assembled battery formed by stacking a plurality of battery cells 81 and electrically connecting these battery cells 81 in series or in parallel.
  • the temperature of the battery 80 can be adjusted to an appropriate temperature range by the heat and cold generated by the refrigeration cycle device 10. Therefore, the temperature adjustment target in the refrigeration cycle device 10 according to the present embodiment is the battery 80.
  • the vehicle air conditioner 1 is configured to be capable of performing pre-air conditioning for starting air conditioning in the passenger compartment before the occupant enters the vehicle, in addition to normal air conditioning that is performed when the occupant is in the vehicle. Have been.
  • the vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioning unit 30, a high-temperature-side heat medium circuit 40, a battery-side heat medium circuit 50, and the like.
  • the refrigeration cycle device 10 heats or cools the air blown into the vehicle compartment to perform air conditioning in the vehicle compartment. Further, the refrigeration cycle apparatus 10 heats or cools the battery-side heat medium circulating in the battery-side heat medium circuit 50 in order to adjust the temperature of the battery 80.
  • the refrigeration cycle apparatus 10 is configured to be able to switch refrigerant circuits for various operation modes in order to perform air conditioning in the vehicle interior. For example, it is configured such that a refrigerant circuit in a cooling mode, a refrigerant circuit in a dehumidifying and heating mode, a refrigerant circuit in a heating mode, and the like can be switched.
  • the refrigeration cycle apparatus 10 includes an operation mode for cooling the battery 80, an operation mode for heating the battery 80 to warm it up, and an operation mode for not actively adjusting the temperature of the battery 80 in the operation mode for air conditioning. And can be switched.
  • the refrigeration cycle apparatus 10 employs an HFO-based refrigerant (specifically, R1234yf) as the refrigerant, and is a vapor compression type in which the pressure of the refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Constructs a subcritical refrigeration cycle. Further, a refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. Some of the refrigerating machine oil circulates with the refrigerant in the cycle.
  • HFO-based refrigerant specifically, R1234yf
  • the compressor 11 sucks, compresses, and discharges the refrigerant in the refrigeration cycle device 10.
  • the compressor 11 is disposed in the front of the vehicle compartment and is disposed in a drive device room in which an electric motor and the like are accommodated.
  • the compressor 11 is an electric compressor in which a fixed displacement compression mechanism having a fixed discharge capacity is rotationally driven by an electric motor.
  • the rotation speed (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60 described later.
  • the outlet of the compressor 11 is connected to the inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the water-refrigerant heat exchanger 12 has a refrigerant passage through which the high-pressure refrigerant discharged from the compressor 11 flows, and a water passage through which the high-temperature heat medium circulating in the high-temperature heat medium circuit 40 flows.
  • the water-refrigerant heat exchanger 12 is a heating heat exchanger that heats the high-temperature heat medium by exchanging heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage.
  • the outlet side of the water-refrigerant heat exchanger 12 is connected to the inlet side of a first three-way joint 13a having three inlets and outlets communicating with each other.
  • a three-way joint one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.
  • the refrigeration cycle apparatus 10 includes a second three-way joint 13b to a sixth three-way joint 13f as described later.
  • the basic configuration of the second three-way joint 13b to the sixth three-way joint 13f is the same as that of the first three-way joint 13a.
  • An inlet of the heating expansion valve 14a is connected to one of the outlets of the first three-way joint 13a.
  • One of the inlets of the second three-way joint 13b is connected to the other outlet of the first three-way joint 13a via a bypass passage 22a.
  • An on-off valve 15a for dehumidification is arranged in the bypass passage 22a.
  • the dehumidifying on-off valve 15a is arranged in a bypass passage 22a connecting the other outflow side of the first three-way joint 13a and one inflow side of the second three-way joint 13b.
  • the dehumidifying on-off valve 15a is an electromagnetic valve, and opens and closes the refrigerant passage of the bypass passage 22a.
  • the dehumidifying on-off valve 15a is an example of a first on-off valve.
  • the dehumidifying on-off valve 15a can be replaced by other means as long as the refrigerant passage of the bypass passage 22a can be opened and closed.
  • a function may be substituted by arranging a three-way valve at the position of the first three-way joint 13a.
  • the refrigeration cycle device 10 includes a heating on-off valve 15b, as described later.
  • the basic configuration of the heating on-off valve 15b is the same as that of the dehumidifying on-off valve 15a.
  • the on-off valve 15a for dehumidification and the on-off valve 15b for heating can switch the refrigerant circuit of each operation mode by opening and closing the refrigerant passage.
  • the on-off valve 15a for dehumidification and the on-off valve 15b for heating constitute a refrigerant circuit switching device for switching the refrigerant circuit of the cycle.
  • the operation of the dehumidifying on-off valve 15a and the heating on-off valve 15b is controlled by a control voltage output from the control device 60.
  • the heating expansion valve 14a depressurizes the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 at least in the operation mode for heating the passenger compartment, and also reduces the flow rate (mass flow rate) of the refrigerant flowing downstream. This is a heating decompression unit that adjusts the pressure.
  • the heating expansion valve 14a is an electric variable throttle mechanism that includes a valve body configured to change the opening degree of the throttle and an electric actuator that changes the opening degree of the valve body.
  • the refrigeration cycle apparatus 10 includes a cooling expansion valve 14b and a cooling expansion valve 14c.
  • the basic configuration of the cooling expansion valve 14b and the cooling expansion valve 14c is the same as that of the heating expansion valve 14a.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c have a fully open function and a fully closed function, respectively.
  • the full-open function allows the valve to fully open to function as a mere refrigerant passage with almost no flow rate adjusting function and refrigerant depressurizing function.
  • the fully closed function closes the refrigerant passage by fully closing the valve opening.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c can switch the refrigerant circuit in each operation mode by the fully open function and the fully closed function. Therefore, the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c according to the present embodiment also have a function as a refrigerant circuit switching device.
  • control device 60 The operation of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c is controlled by a control signal (control pulse) output from the control device 60.
  • the refrigerant inlet side of the outdoor heat exchanger 16 is connected to the outlet of the heating expansion valve 14a.
  • the outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out of the heating expansion valve 14a and the outside air blown by a cooling fan (not shown).
  • the outdoor heat exchanger 16 is arranged on the front side in the drive device room. Therefore, when the vehicle is traveling, the traveling wind can be applied to the outdoor heat exchanger 16. In addition, the outdoor heat exchanger 16 exchanges heat between the refrigerant flowing therein and the outside air introduced as traveling wind or the like. Here, with respect to the outside air passing through the outdoor heat exchanger 16, the flow cannot be completely shut off.
  • the refrigerant outlet of the outdoor heat exchanger 16 is connected to the inlet side of the third three-way joint 13c.
  • One of the outlets of the third three-way joint 13c is connected to one of the inlets of the fourth three-way joint 13d via a heating passage 22b.
  • the heating opening / closing valve 15b that opens and closes the refrigerant passage is arranged in the heating passage 22b.
  • the heating on-off valve 15b is configured by an electromagnetic valve.
  • the heating on-off valve 15b is an example of a second on-off valve.
  • heating on-off valve 15b can be replaced by another means as long as the refrigerant passage of the heating passage 22b can be opened and closed.
  • a three-way valve may be arranged at the position of the third three-way joint 13c to replace the function.
  • the other inflow side of the second three-way joint 13b is connected to the other outflow port of the third three-way joint 13c.
  • a check valve 17 is arranged in the refrigerant passage connecting the other outlet side of the third three-way joint 13c and the other inlet side of the second three-way joint 13b. The check valve 17 allows the refrigerant to flow from the third three-way joint 13c to the second three-way joint 13b, and prohibits the refrigerant from flowing from the second three-way joint 13b to the third three-way joint 13c.
  • the outlet of the fifth three-way joint 13e is connected to the outlet of the second three-way joint 13b.
  • One inlet of the fifth three-way joint 13e is connected to the inlet side of the cooling expansion valve 14b.
  • the inlet of the expansion valve for cooling 14c is connected to the other outlet of the fifth three-way joint 13e.
  • the cooling expansion valve 14b is a cooling decompression unit that depressurizes the refrigerant that has passed through the second three-way joint 13b and adjusts the flow rate of the refrigerant that flows out downstream at least in the operation mode in which the air in the passenger compartment is cooled.
  • the refrigerant inlet side of the indoor evaporator 18 is connected to the outlet of the cooling expansion valve 14b.
  • the indoor evaporator 18 is arranged in an air-conditioning case 31 of an indoor air-conditioning unit 30 described later.
  • the indoor evaporator 18 blows air by exchanging heat between the low-pressure refrigerant depressurized by the cooling expansion valve 14b and the blast air blown from the blower 32 to evaporate the low-pressure refrigerant and exert an endothermic effect on the low-pressure refrigerant.
  • This is a cooling heat exchanger that cools air.
  • the indoor evaporator 18 functions as an evaporator.
  • One inlet side of the sixth three-way joint 13f is connected to the refrigerant outlet of the indoor evaporator 18.
  • the cooling expansion valve 14c is a cooling pressure reducing unit that reduces the pressure of the refrigerant that has passed through the second three-way joint 13b and adjusts the flow rate of the refrigerant that flows out downstream at least in the operation mode in which the battery 80 is cooled.
  • the outlet side of the cooling expansion valve 14c is connected to the inlet side of the refrigerant passage of the chiller 19.
  • the chiller 19 has a refrigerant passage through which a low-pressure refrigerant depressurized by the cooling expansion valve 14c flows, and a water passage through which a battery-side heat medium circulating in a battery-side heat medium circuit 50 described later.
  • the chiller 19 is a temperature-adjusting heat exchange unit that exchanges heat between the refrigerant flowing through the refrigerant passage and the battery-side heat medium flowing through the water passage to adjust the temperature of the battery-side heat medium. Therefore, the chiller 19 corresponds to a heat exchange unit for temperature control.
  • the other inlet side of the sixth three-way joint 13f is connected to the outlet of the refrigerant passage of the chiller 19.
  • the inlet of the evaporation pressure regulating valve 20 is connected to the outlet of the sixth three-way joint 13f.
  • the evaporation pressure regulating valve 20 maintains the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined reference pressure in order to suppress frost formation on the indoor evaporator 18.
  • the evaporating pressure adjusting valve 20 is configured by a mechanical variable throttle mechanism that increases the valve opening as the pressure of the refrigerant on the outlet side of the indoor evaporator 18 increases.
  • the evaporation pressure regulating valve 20 maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a temperature equal to or higher than the frost formation suppression temperature (for example, 1 ° C.) at which frost formation on the indoor evaporator 18 can be suppressed. Further, the evaporating pressure regulating valve 20 is disposed downstream of the sixth three-way joint 13f, which is the junction. For this reason, the evaporation pressure regulating valve 20 also maintains the refrigerant evaporation temperature in the chiller 19 at a temperature equal to or higher than the frost formation suppression temperature.
  • the frost formation suppression temperature for example, 1 ° C.
  • the other inlet side of the fourth three-way joint 13d is connected to the outlet of the evaporation pressure regulating valve 20.
  • the inlet side of the accumulator 21 is connected to the outlet of the fourth three-way joint 13d.
  • the accumulator 21 is a gas-liquid separator that separates the gas-liquid of the refrigerant flowing into the inside and stores the surplus liquid-phase refrigerant in the cycle.
  • the suction side of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 21.
  • the fifth three-way joint 13e functions as a branch part that branches the flow of the refrigerant flowing out of the outdoor heat exchanger 16.
  • the sixth three-way joint 13 f functions as a joining portion that joins the flow of the refrigerant flowing out of the indoor evaporator 18 and the flow of the refrigerant flowing out of the chiller 19 and flows out to the suction side of the compressor 11.
  • the indoor evaporator 18 and the chiller 19 are connected in parallel to each other with respect to the refrigerant flow. Further, the heating passage 22b guides the refrigerant flowing out of the outdoor heat exchanger 16 to the suction port side of the compressor 11, bypassing the indoor evaporator 18 and the chiller 19, and functions as a heating passage. I have.
  • the heating on-off valve 15b functions as an on-off valve for opening and closing the refrigerant passage of the heating passage 22b.
  • the high-temperature-side heat medium circuit 40 is a heat medium circulation circuit that circulates the high-temperature-side heat medium.
  • the high-temperature side heat medium ethylene glycol, dimethylpolysiloxane, a solution containing a nanofluid, or the like, an antifreeze, or the like can be used.
  • the high-temperature heat medium circuit 40 includes a water passage of the water-refrigerant heat exchanger 12, a high-temperature heat medium pump 41, a heater core 42, and the like.
  • the high-temperature heat medium pump 41 is a water pump for pumping the high-temperature heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12.
  • the high-temperature-side heat medium pump 41 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 60.
  • the outlet of the water passage of the water-refrigerant heat exchanger 12 is connected to the heat medium inlet side of the heater core 42.
  • the heater core 42 is a heat exchanger that heats the blown air by exchanging heat between the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 18.
  • the heater core 42 is arranged inside the air conditioning case 31 of the indoor air conditioning unit 30.
  • the heat medium outlet of the heater core 42 is connected to the inlet side of the high temperature side three-way valve 43.
  • the high temperature side three-way valve 43 is an electric three-way flow control valve having one inlet and two outlets and capable of continuously adjusting the passage area ratio of the two outlets. The operation of the high-temperature side three-way valve 43 is controlled by a control signal output from the control device 60.
  • the heat medium inlet side of the high-temperature radiator 44 is connected to one outlet of the high-temperature three-way valve 43.
  • the suction port side of the high-temperature side heat medium pump 41 is connected to the other outlet of the high-temperature side three-way valve 43. Accordingly, the high-temperature side three-way valve 43 determines the flow rate of the high-temperature side heat medium flowing out of the heater core 42 to the high-temperature side radiator 44 and the flow rate of the high-temperature side heat medium pump 41 bypassing the high-temperature side radiator 44 and sucking the high-temperature side heat medium. Adjust the flow ratio.
  • the high-temperature radiator 44 is a heat exchanger that exchanges heat between the high-temperature heat medium flowing out of the heater core 42 and the outside air blown by an outside air fan (not shown), and radiates heat of the high-temperature heat medium to the outside air.
  • the high-temperature side radiator 44 is disposed on the front side in the drive device chamber. Therefore, when the vehicle is traveling, the traveling wind can be applied to the high-temperature side radiator 44.
  • the heat medium outlet of the high temperature radiator 44 is connected to the suction port side of the high temperature heat medium pump 41.
  • the control device 60 operates the high-temperature side heat medium pump 41 so that the refrigerant discharged from the compressor 11 in the water-refrigerant heat exchanger 12 and the high-temperature side heat medium are separated.
  • the high-temperature side heat medium can be heated by heat exchange.
  • the heater core 42 the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12 and the blown air can be heat-exchanged to heat the blown air.
  • each component of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 constitutes a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source. I have.
  • the battery-side heat medium circuit 50 is a heat medium circulation circuit that circulates the battery-side heat medium.
  • the battery-side heat medium the same fluid as the high-temperature-side heat medium can be used.
  • a water passage of the chiller 19 a battery-side heat medium pump 51, a heat exchange unit 52, and the like are arranged.
  • the battery-side heat medium pump 51 is a water pump that pumps the battery-side heat medium to the inlet side of the water passage in the chiller 19.
  • the basic configuration of the battery-side heat medium pump 51 is the same as that of the high-temperature side heat medium pump 41.
  • the inlet of the heat exchange unit 52 is connected to the outlet of the water passage of the chiller 19.
  • the heat exchange section 52 has a plurality of heat medium passages formed by a metal plate arranged so as to contact a plurality of battery cells 81 forming the battery 80.
  • the heat exchange unit is a heat exchange unit that adjusts the temperature of the battery 80 by exchanging heat between the battery cells 81 and the battery-side heat medium flowing through the heat medium flow path.
  • heat exchange unit 52 a unit in which a heat medium flow path is arranged between the battery cells 81 arranged in a stack may be adopted. Further, heat exchange section 52 may be formed integrally with battery 80.
  • the battery case may be formed integrally with the battery 80 by providing a heat medium flow path in a dedicated case for accommodating the stacked battery cells 81.
  • the outlet of the heat exchange unit 52 is connected to the suction side of the battery-side heat medium pump 51.
  • the control device 60 operates the battery-side heat medium pump 51 to cause the chiller 19 to exchange heat between the refrigerant flowing out of the cooling expansion valve 14c and the battery-side heat medium.
  • the temperature of the battery-side heat medium can be adjusted.
  • the battery 80 can be heat-exchanged by exchanging heat between the battery-side heat medium whose temperature has been adjusted and the battery 80.
  • each component of the chiller 19 and the battery-side heat medium circuit 50 constitutes a temperature adjustment unit that adjusts the temperature of the battery 80 with the refrigerant flowing out of the cooling expansion valve 14c.
  • the battery-side heat medium is a temperature-adjustment-side heat medium
  • the battery-side heat medium circuit 50 is a temperature-adjustment-side heat medium circuit that circulates the temperature-adjustment-side heat medium.
  • the indoor air-conditioning unit 30 blows out the blast air whose temperature has been adjusted by the refrigeration cycle device 10 into the vehicle interior.
  • the indoor air-conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the forefront of the vehicle interior.
  • the indoor air-conditioning unit 30 houses the blower 32, the indoor evaporator 18, the heater core 42, and the like in an air passage formed in an air-conditioning case 31 forming an outer shell.
  • the air-conditioning case 31 forms an air passage for blowing air blown into the vehicle interior.
  • the air-conditioning case 31 has a certain degree of elasticity and is formed of a resin having excellent strength (for example, polypropylene).
  • An inside / outside air switching device 33 is disposed on the most upstream side of the airflow of the air conditioning case 31.
  • the inside / outside air switching device 33 switches and introduces inside air (vehicle interior air) and outside air (vehicle outside air) into the air conditioning case 31.
  • the inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port for introducing the inside air into the air conditioning case 31 and the outside air introduction port for introducing the outside air by the inside / outside air switching door, and the inside air introduction air volume and the outside air. Is to change the rate of introduction with the amount of air introduced.
  • the inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door. The operation of the electric actuator is controlled by a control signal output from the control device 60.
  • a blower 32 is disposed downstream of the inside / outside air switching device 33 in the blown air flow.
  • the blower 32 blows the air taken in through the inside / outside air switching device 33 toward the vehicle interior.
  • the blower 32 is an electric blower that drives a centrifugal multi-blade fan with an electric motor.
  • the rotation speed (that is, the blowing capacity) of the blower 32 is controlled by the control voltage output from the control device 60.
  • the indoor evaporator 18 and the heater core 42 are arranged in this order with respect to the blown air flow. That is, the indoor evaporator 18 is arranged on the upstream side of the flow of the blown air from the heater core 42.
  • a cool air bypass passage 35 is provided in the air conditioning case 31 to allow the air blown after passing through the indoor evaporator 18 to bypass the heater core 42.
  • An air mix door 34 is arranged on the downstream side of the blown air flow of the indoor evaporator 18 in the air conditioning case 31 and on the upstream side of the blown air flow of the heater core 42.
  • the air mix door 34 adjusts a flow rate ratio of a flow rate of the blown air passing through the heater core 42 and a flow rate of the blown air passing through the cool air bypass passage 35 among the blown air after passing through the indoor evaporator 18. Department.
  • the air mix door 34 is driven by an electric actuator for the air mix door. The operation of the electric actuator is controlled by a control signal output from the control device 60.
  • the mixing space is disposed downstream of the air flow of the heater core 42 and the cool air bypass passage 35 in the air conditioning case 31.
  • the mixing space is a space for mixing the blast air heated by the heater core 42 and the blast air that has not passed through the cool air bypass passage 35 and is not heated.
  • an opening hole for blowing out the blast air (that is, the conditioned air) mixed in the mixing space into the passenger compartment, which is a space to be air-conditioned, is disposed downstream of the blast air flow of the air conditioning case 31.
  • the face opening hole is an opening hole for blowing out conditioned air toward the upper body of the occupant in the passenger compartment.
  • the foot opening hole is an opening hole for blowing out conditioned air toward the feet of the occupant.
  • the defroster opening hole is an opening hole for blowing out conditioned air toward the inner surface of the vehicle front window glass.
  • the face opening, the foot opening, and the defroster opening are respectively connected to a face outlet, a foot outlet, and a defroster outlet provided in the vehicle cabin through ducts forming air passages. )It is connected to the.
  • the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air flow ratio of the air flow passing through the heater core 42 and the air flow passing through the cool air bypass passage 35 by the air mixing door 34. Then, the temperature of the blown air (conditioned air) blown out from each outlet into the vehicle interior is adjusted.
  • Face doors, foot doors, and defroster doors are disposed on the upstream side of the airflow from the face opening, the foot opening, and the defroster opening.
  • the face door adjusts the opening area of the face opening hole.
  • the foot door adjusts the opening area of the foot opening hole.
  • the defroster door adjusts the opening area of the froster opening hole.
  • These face doors, foot doors and defroster doors constitute an outlet mode switching device for switching the outlet mode.
  • These doors are connected to an electric actuator for driving the outlet mode door via a link mechanism or the like, and are rotated in conjunction therewith.
  • the operation of the electric actuator is also controlled by a control signal output from the control device 60.
  • Specific examples of the outlet mode switched by the outlet mode switching device include a face mode, a bi-level mode, and a foot mode.
  • the face mode is an outlet mode in which the face outlet is fully opened and air is blown from the face outlet toward the upper body of the passenger in the vehicle.
  • the bi-level mode is an air outlet mode in which both the face air outlet and the foot air outlet are opened to blow air toward the upper body and feet of the occupant in the vehicle.
  • the foot mode is an outlet mode in which the foot outlet is fully opened and the defroster outlet is opened by a small opening, and air is mainly blown out from the foot outlet.
  • the defroster mode is an outlet mode in which the defroster outlet is fully opened and air is blown from the defroster outlet to the inner surface of the windshield.
  • the vehicle air conditioner 1 has a control device 60 for controlling the operation of the components.
  • the control device 60 includes a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and its peripheral circuits.
  • the control device 60 performs various calculations and processes based on the control program stored in the ROM, and controls the operation of various control target devices connected to the output side.
  • Various control target devices include a compressor 11, a heating expansion valve 14a, a cooling expansion valve 14b, a cooling expansion valve 14c, a dehumidifying on-off valve 15a, a heating on-off valve 15b, a blower 32, and a high-temperature side heat medium pump 41.
  • the various sensors are connected to the input side of the control device 60, and detection signals of the various sensors are input.
  • the various sensors include an internal air temperature sensor 61, an external air temperature sensor 62, a solar radiation sensor 63, first to fifth refrigerant temperature sensors 64a to 64e, a first refrigerant pressure sensor 65a, and a second refrigerant.
  • a pressure sensor 65b is included.
  • the various sensors include an evaporator temperature sensor 66, a high-temperature-side heat medium temperature sensor 67a, a battery-side heat medium temperature sensor 67b, a battery temperature sensor 68, an air-conditioning air temperature sensor 69, and the like.
  • the inside air temperature sensor 61 is an inside air temperature detection unit that detects the vehicle interior temperature (inside air temperature) Tr.
  • the outside air temperature sensor 62 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam.
  • the solar radiation sensor 63 is a solar radiation amount detecting unit that detects a solar radiation amount Ts applied to the vehicle interior.
  • the first refrigerant temperature sensor 64a is a discharged refrigerant temperature detecting unit that detects the temperature T1 of the discharged refrigerant discharged from the compressor 11.
  • the second refrigerant temperature sensor 64b is a second refrigerant temperature detector that detects the temperature T2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the third refrigerant temperature sensor 64c is a third refrigerant temperature detection unit that detects the temperature T3 of the refrigerant flowing out of the outdoor heat exchanger 16.
  • the fourth refrigerant temperature sensor 64d is a fourth refrigerant temperature detector that detects the temperature T4 of the refrigerant flowing out of the indoor evaporator 18.
  • the fifth refrigerant temperature sensor 64e is a fifth refrigerant temperature detector that detects the temperature T5 of the refrigerant flowing out of the refrigerant passage of the chiller 19.
  • the first refrigerant pressure sensor 65a is a first refrigerant pressure detector that detects the pressure P1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the second refrigerant pressure sensor 65b is a second refrigerant pressure detector that detects the pressure P2 of the refrigerant flowing out of the refrigerant passage of the chiller 19.
  • the evaporator temperature sensor 66 is an evaporator temperature detector that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18.
  • the evaporator temperature sensor 66 specifically detects the heat exchange fin temperature of the indoor evaporator 18.
  • the high-temperature heat medium temperature sensor 67a detects a high-temperature heat medium temperature TWH that is the temperature of the high-temperature heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 and flowing into the heater core 42. It is a detection unit.
  • the battery-side heat medium temperature sensor 67b is a battery-side heat medium temperature detection unit that detects a cell-side heat medium temperature TWC that is the temperature of the battery-side heat medium flowing out of the water passage of the chiller 19 and flowing into the heat exchange unit 52. is there.
  • the battery temperature sensor 68 is a battery temperature detector that detects the battery temperature TB (that is, the temperature of the battery 80).
  • the battery temperature sensor 68 includes a plurality of detection units and detects temperatures at a plurality of locations of the battery 80. For this reason, the control device 60 can also detect the temperature difference between the components of the battery 80. Furthermore, as the battery temperature TB, an average value detected by a plurality of detection units is employed.
  • the air-conditioning air temperature sensor 69 is an air-conditioning air temperature detecting unit that detects the temperature of the air blown from the mixing space into the vehicle compartment TAV.
  • an operation panel 70 is connected to the input side of the control device 60 as shown in FIG.
  • the operation panel 70 is arranged near the instrument panel at the front of the vehicle compartment, and has various operation switches. Therefore, operation signals from various operation switches provided on the operation panel 70 are input to the control device 60.
  • the various operation switches of the operation panel 70 include, specifically, an auto switch for setting or canceling the automatic control operation of the vehicle air conditioner, and an air conditioner switch for requesting the indoor evaporator 18 to cool the blown air. ing. Further, the various operation switches of the operation panel 70 include an air volume setting switch for manually setting the air volume of the blower 32, a temperature setting switch for setting the target temperature Tset in the vehicle compartment, and a blowing mode switching switch for manually setting the blowing mode. Have been.
  • the control device 60 has an integrated control unit for controlling various control target devices connected to its output side. However, the control device 60 controls the operation of each control target device (hardware and software). ) Constitute a control unit that controls the operation of each control target device.
  • the configuration that controls the refrigerant discharge capacity of the compressor 11 constitutes the compressor control unit 60a.
  • the configuration for controlling the operations of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c constitutes an expansion valve control unit 60b.
  • the configuration for controlling the operations of the dehumidifying on-off valve 15a and the heating on-off valve 15b constitutes a refrigerant circuit switching control unit 60c.
  • the configuration for controlling the operations of the high-temperature side heat medium pump 41 and the high-temperature side three-way valve 43 of the high-temperature side heat medium circuit 40 is such that the heat release amount of the discharged refrigerant in the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 is reduced.
  • the radiation amount control unit 60d to be controlled is configured.
  • the configuration for controlling the pumping ability of the battery-side heat medium pump 51 of the battery-side heat medium pump 51 in the battery-side heat medium circuit 50 constitutes the battery-side heat medium temperature control unit 60e.
  • the vehicle air conditioner 1 of the present embodiment has a function of adjusting the temperature of the battery 80 in addition to a function of performing air conditioning of the vehicle interior. For this reason, in the vehicle air conditioner 1, it is possible to perform operation in the following 12 operation modes by switching the refrigerant circuit.
  • the single cooling mode is an operation mode in which the air in the vehicle compartment is cooled by cooling the blown air and blowing it out into the vehicle compartment without adjusting the temperature of the battery 80.
  • the single heating mode is an operation mode in which the inside of the vehicle compartment is heated by heating the blown air and blowing it out into the vehicle compartment without adjusting the temperature of the battery 80.
  • the single warm-up mode is an operation mode in which the battery 80 is warmed up without performing air conditioning in the vehicle interior.
  • the single warm-up mode is an example of the object warm-up mode.
  • Heating / warm-up mode The heating / warm-up mode is an operation mode in which the blast air is heated and blown into the vehicle interior to heat the vehicle interior and to warm up the battery 80.
  • the heating warm-up mode is an example of the object warm-up mode.
  • the single cooling mode is an operation mode in which the battery 80 is cooled without performing air conditioning in the vehicle compartment.
  • Cooling cooling mode The cooling cooling mode is an operation mode for cooling the battery 80 while cooling the inside of the vehicle by cooling the blown air and blowing it out into the vehicle interior.
  • In-line dehumidification heating / cooling mode In-series dehumidification heating / cooling mode performs dehumidification heating in the vehicle interior by reheating the cooled and dehumidified blast air and blowing it out into the vehicle interior, and also cools battery 80. Operation mode.
  • Parallel dehumidifying heating / cooling mode In the parallel dehumidifying heating / cooling mode, the dehumidified air that has been cooled and dehumidified is reheated with a higher heating capacity than the serial dehumidifying heating / cooling mode and is blown out into the vehicle interior to dehumidify the vehicle interior. This is an operation mode in which heating and cooling of the battery 80 are performed.
  • First heating / cooling mode The first heating / cooling mode is an aspect of an operation mode in which the inside of the vehicle compartment is heated by cooling the battery 80 by heating the blown air and blowing it out into the vehicle compartment.
  • the second heating / cooling mode is an aspect of an operation mode in which the inside of the passenger compartment is heated by heating the blown air and blown out into the passenger compartment, and the battery 80 is cooled. In the second heating / cooling mode, it is possible to perform heating of the vehicle interior and cooling of the battery 80 while eliminating the influence of heat exchange with the outside air in the outdoor heat exchanger 16.
  • the switching of each operation mode in the vehicle air conditioner 1 is performed by executing a control program stored in the control device 60 in advance.
  • the detection signal of the above-described sensor group and the operation signal of the operation panel 70 are read every predetermined control cycle. Then, the target blowing temperature TAO of the blown air blown into the vehicle compartment is determined using the read detection signal and operation signal.
  • TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ Ts + C (F1)
  • Tset is the vehicle interior set temperature set by the temperature setting switch. Tr is a vehicle interior temperature detected by the internal air temperature sensor 61. Tam is the vehicle outside temperature detected by the outside temperature sensor 62. Ts is the amount of solar radiation detected by the solar radiation sensor 63. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.
  • the operation mode of the vehicle air conditioner 1 is changed from 11 types of operation modes. The other operation mode is determined and switched.
  • the air conditioning mode of the operation mode is determined to be the cooling operation. .
  • the operation mode is switched to the cooling cooling mode.
  • the battery temperature TB is equal to or higher than the predetermined reference lower limit temperature KTBL (in the present embodiment, 20 ° C.) and lower than the reference upper limit temperature KTBH (that is, within the appropriate temperature range)
  • the operation mode is switched to the single cooling mode.
  • the air conditioning mode in the operation mode is as follows. , Is determined to be the series dehumidifying heating operation.
  • the operation mode is switched to the series dehumidifying heating / cooling mode.
  • the operation mode is switched to the single series dehumidification heating mode.
  • the air conditioning mode in the operation mode is determined to be the parallel dehumidification heating operation.
  • the operation mode is switched to the parallel dehumidifying heating / cooling mode.
  • the operation mode is switched to the single parallel dehumidifying and heating mode.
  • an operation mode is set. Is determined to be a heating operation.
  • the operation mode is switched to one of the first heating / cooling mode and the second heating / cooling mode.
  • the operation mode is switched to the heating warm-up mode.
  • the operation mode is switched to the single heating mode.
  • the temperature of the battery 80 is adjusted. That is, in this situation, when the battery temperature TB becomes equal to or higher than the reference upper limit temperature KTBH, the operation mode is switched to the single cooling mode. When the battery temperature TB is equal to or lower than the reference lower limit temperature KTBL, the operation mode is switched to the single warm-up mode.
  • the temperature of the battery 80 is always maintained within an appropriate temperature range when the vehicle system is activated, regardless of whether or not the vehicle compartment is air-conditioned.
  • the refrigeration cycle apparatus 10 be operated in an operation mode in which the temperature of the battery 80 can be adjusted when the vehicle system is activated.
  • the operation modes in which the temperature of the battery 80 can be adjusted include a cooling cooling mode, a dehumidifying heating cooling mode, a heating warming mode, a first heating cooling mode, a second heating cooling mode, a single cooling mode, and a single warming mode. is there.
  • the operation is switched to the single cooling mode or the single warm-up mode.
  • the control device 60 controls the operation of the high-temperature side heat medium pump 41 so as to exhibit a predetermined heat medium pumping ability for the single cooling mode, and controls the battery-side heat medium pump 51 to operate. Stop. Further, the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows into the high-temperature side radiator 44.
  • the compressor 11 In the refrigeration cycle apparatus 10 in the single cooling mode, the compressor 11, the water-refrigerant heat exchanger 12, (the expansion valve 14a for heating), the outdoor heat exchanger 16, the check valve 17, the expansion valve 14b for cooling, the indoor evaporator
  • the refrigerant circulates in the order of 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • control device 60 determines the operation states of various control devices (control signals to be output to various control devices) based on the target blowing temperature TAO, the detection signals of the sensor group, and the like.
  • the refrigerant discharge capacity of the compressor 11 in the single cooling mode (that is, the control signal output to the electric motor of the compressor 11) is determined as follows. First, the target evaporator temperature TEO is determined with reference to a control map stored in the control device 60 in advance based on the target outlet temperature TAO.
  • the control signal output to the compressor 11 is based on the deviation between the target evaporator temperature TEO and the evaporator temperature Tefin detected by the evaporator temperature sensor 66, and the evaporator temperature Tefin is determined by the feedback control method. It is determined to approach the temperature TEO.
  • control signal output to the cooling expansion valve 14b is such that the degree of supercooling of the refrigerant flowing into the cooling expansion valve 14b approaches a target subcooling degree that is predetermined so that the COP has a maximum value. Is determined.
  • the actuator for the air mixing door is controlled so that the opening of the air mixing door 34 becomes the opening SW determined by using the following equation F2.
  • SW ⁇ TAO- (Tefin + C2) ⁇ / ⁇ TWH- (Tefin + C2) ⁇ (F2)
  • TWH is the high-temperature-side heat medium temperature detected by the high-temperature-side heat medium temperature sensor 67a.
  • C2 is a control constant.
  • the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator, and the indoor evaporator 18 functions as an evaporator. That is, the blown air can be cooled by the indoor evaporator 18, and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12.
  • the vehicle air conditioner 1 in the single cooling mode by adjusting the opening of the air mix door 34, a part of the blast air cooled by the indoor evaporator 18 is reheated by the heater core 42, and the target outlet temperature TAO is set. Can be supplied into the vehicle cabin. That is, the vehicle air conditioner 1 in the single cooling mode can cool the passenger compartment.
  • the vehicle air conditioner 1 in the single cooling mode can perform cooling of the vehicle interior without adjusting the temperature of the battery 80.
  • the control device 60 controls the operation of the high-temperature side heat medium pump 41 so as to exhibit a predetermined heat medium pumping ability for the single series dehumidifying and heating mode, and performs the battery-side heat transfer.
  • the medium pump 51 is stopped.
  • the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows into the high-temperature side radiator 44.
  • a vapor compression refrigeration cycle is configured.
  • the compressor 11 the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure adjustment
  • the refrigerant circulates in the order of the valve 20, the accumulator 21, and the compressor 11.
  • control device 60 determines the operation states of various control devices (control signals to be output to various control devices) based on the target blowing temperature TAO, the detection signals of the sensor group, and the like.
  • the determination of the target evaporator temperature TEO and the determination of the control signal for the compressor 11 are performed in the same manner as in the above-described single cooling mode.
  • the throttle opening of the heating expansion valve 14a and the cooling expansion valve 14b in the single series dehumidifying and heating mode is determined by referring to the control map stored in the control device 60 based on the target outlet temperature TAO. Specifically, it is determined that the throttle opening of the heating expansion valve 14a decreases and the throttle opening of the cooling expansion valve 14b increases as the target outlet temperature TAO increases.
  • the actuator for the air mix door is controlled in the same manner as in the single cooling mode. Since the target outlet temperature TAO is higher than in the single cooling mode, the opening degree SW of the air mix door 34 approaches 100%. For this reason, in the single series dehumidification heating mode, the opening of the air mix door 34 is determined such that most of the flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • a vapor compression refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a radiator and the indoor evaporator 18 functions as an evaporator is configured.
  • the vehicle air conditioner 1 in the single series dehumidification and heating mode can perform dehumidification and heating of the vehicle interior.
  • the throttle opening of the heating expansion valve 14a is reduced along with the increase of the target blowout temperature TAO, and The throttle opening of the cooling expansion valve 14b is increased.
  • the saturation temperature of the refrigerant in the outdoor heat exchanger 16 decreases, and the difference from the outdoor temperature Tam decreases.
  • the amount of heat radiation of the refrigerant in the outdoor heat exchanger 16 can be reduced, the amount of heat radiation of the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the ability of the heater core 42 to heat the blown air can be improved. it can.
  • the throttle opening of the heating expansion valve 14a is reduced along with the increase of the target outlet temperature TAO.
  • the throttle opening of the cooling expansion valve 14b is increased.
  • the mild temperature of the refrigerant in the outdoor heat exchanger 16 decreases, and the temperature difference from the outside air temperature Tam increases.
  • the heat absorption amount of the refrigerant in the outdoor heat exchanger 16 can be increased, the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the heating capability of the blower air by the heater core 42 can be improved. it can.
  • the throttle opening of the heating expansion valve 14a is reduced and the throttle opening of the cooling expansion valve 14b is increased as the target outlet temperature TAO rises.
  • the amount of heat release of the refrigerant in the refrigerant heat exchanger 12 can be increased. Therefore, in the single-series dehumidifying and heating mode, the ability of the water-refrigerant heat exchanger 12 and the high-temperature heat medium circuit 40 to heat the blown air can be improved with an increase in the target outlet temperature TAO.
  • the control device 60 controls the operation of the high-temperature side heat medium pump 41 so as to exhibit the predetermined heat medium pumping ability for the single parallel dehumidifying and heating mode, and controls the battery-side heat medium.
  • the pump 51 is stopped.
  • the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows into the high-temperature side radiator 44.
  • the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the compressor 11. .
  • a vapor compression type in which the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11. Is configured.
  • control device 60 determines the operation states of various control devices (control signals to be output to various control devices) based on the target blowing temperature TAO, the detection signals of the sensor group, and the like.
  • the throttle opening of the heating expansion valve 14a and the cooling expansion valve 14b in the single parallel dehumidifying and heating mode is determined as follows.
  • the target superheat degree SHEO of the refrigerant on the outlet side of the indoor evaporator 18 is determined.
  • a predetermined constant for example, 5 ° C.
  • the throttle opening degree of the heating expansion valve 14a and the cooling expansion valve 14b is determined based on the difference between the target superheat degree SHEO and the superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18 by the feedback control method. It is determined so as to approach the target superheat degree SHEO.
  • the actuator for the air mix door is controlled in the same manner as in the single cooling mode. Since the target outlet temperature TAO is higher than in the single cooling mode, the opening degree SW of the air mix door 34 approaches 100% as in the single in-line dehumidifying and heating mode. For this reason, in the single parallel dehumidifying and heating mode, the opening of the air mix door 34 is determined such that most of the flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • the water-refrigerant heat exchanger 12 functions as a radiator, and the outdoor heat exchanger 16 and the indoor evaporator 18 connected in parallel to the refrigerant flow function as evaporators.
  • the refrigeration cycle is performed.
  • the blown air can be cooled by the indoor evaporator 18, and the blown air that has been cooled and dehumidified can be reheated via the water-refrigerant heat exchanger 12 and the heater core 42. . Therefore, the vehicle air conditioner 1 in the single parallel dehumidification and heating mode can perform dehumidification and heating of the vehicle interior.
  • the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel to the refrigerant flow, and the evaporation pressure regulating valve 20 is provided downstream of the indoor evaporator 18. Are located. Thereby, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be made lower than the refrigerant evaporation temperature in the indoor evaporator 18.
  • the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased and the amount of heat released by the refrigerant in the water-refrigerant heat exchanger 12 can be increased as compared with the single serial dehumidifying and heating mode.
  • the blown air can be reheated with a higher heating capacity than in the single serial dehumidifying and heating mode.
  • the heating expansion valve 14a is adjusted to the throttle opening determined in the single heating mode, and the cooling expansion valve 14b and the cooling expansion valve 14c are fully closed. Then, the on-off valve 15a for dehumidification is closed, and the on-off valve 15b for heating is opened.
  • the control device 60 controls the operation of the high-temperature side heat medium pump 41 and stops the battery-side heat medium pump 51 so as to exhibit a predetermined heat medium pumping ability for the single heating mode. Let it. Further, the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows out to the suction port side of the high-temperature side heat medium pump 41.
  • control device 60 determines the operation states of various control devices (control signals to be output to various control devices) based on the target blowing temperature TAO, the detection signals of the sensor group, and the like.
  • the throttle opening of the heating expansion valve 14a in the heating mode is determined as follows. First, a target supercooling degree SCO of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is determined. The target degree of subcooling SCO is determined with reference to a control map based on the intake temperature of the air blown into the indoor evaporator 18 or the outside air temperature Tam. In the control map, the target degree of supercooling SCO is determined such that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • COP coefficient of performance
  • the throttle opening of the heating expansion valve 14a is determined by a feedback control method based on a deviation between the target supercooling degree SCO and the supercooling degree SC of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12. .
  • the throttle opening of the heating expansion valve 14a is determined so that the supercooling degree SC of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO.
  • the actuator for the air mix door is controlled in the same manner as in the single cooling mode. Since the target outlet temperature TAO is higher than in the single cooling mode, the opening degree SW of the air mix door 34 approaches 100%. For this reason, in the single heating mode, the opening of the air mix door 34 is determined such that most of the flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • a refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a radiator and the outdoor heat exchanger 16 functions as an evaporator.
  • the blast air can be heated by the water-refrigerant heat exchanger 12 and the heater core 42, so that the heated blast air can be blown out into the vehicle interior to heat the vehicle interior.
  • control device 60 controls the operation of the battery-side heat medium pump 51 so as to exhibit the predetermined heat medium pumping ability for the single warm-up mode, and To stop.
  • the compressor 11 the (water-refrigerant heat exchanger 12), the bypass passage 22a, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 in this order. Circulates to form a vapor compression refrigeration cycle.
  • control device 60 appropriately controls the operation of each device to be controlled.
  • the rotation speed of the compressor 11 is controlled such that the battery-side heat medium temperature TWC approaches the target battery-side heat medium temperature TWCO.
  • the target battery-side heat medium temperature TWCO is determined based on the battery temperature TB with reference to a control map for the single warm-up mode stored in the control device 60 in advance. In this control map, the target battery-side heat medium temperature TWCO is determined to decrease as the battery temperature TB increases. Further, in the single warm-up mode, the target battery-side heat medium temperature TWCO is determined to be higher than the temperature of the battery-side heat medium flowing into the water passage of the chiller 19. The opening degree SW of the actuator for the air mix door is controlled so that the opening degree SW becomes 0%.
  • the state of the refrigerant changes as shown in the Mollier diagram of FIG. That is, as indicated by points a1 to a2 in FIG. 3, the refrigerant sucked into the compressor 11 is discharged while being compressed to a high temperature and a high pressure.
  • the high-pressure discharge refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12.
  • the refrigerant flowing into the water-refrigerant heat exchanger 12 hardly radiates heat to the high-temperature side heat medium and the bypass passage 22 a Spill to the side. Therefore, the refrigerant flowing out of the water-refrigerant heat exchanger 12 passes through the bypass passage 22a and reaches the cooling expansion valve 14c in a state of a high-temperature and high-pressure hot gas.
  • the battery-side heat medium pump 51 exhibits a predetermined heat medium pumping ability. Therefore, as shown by points a3 to a1 in FIG. 3, the heat of the overheated refrigerant is radiated by the chiller 19 to the battery-side heat medium. Thereby, the battery-side heat medium is heated using the overheated refrigerant as a heat source.
  • the battery-side heat medium heated by the chiller 19 flows into the heat exchange unit 52 by the operation of the battery-side heat medium pump 51, and exchanges heat with the battery 80.
  • the battery 80 is heated, and the battery 80 can be warmed up.
  • the battery-side heat medium that has flowed out of the heat exchange unit 52 is sucked into the battery-side heat medium pump 51, and is again pumped to the water passage of the chiller 19.
  • the refrigerant flowing out of the chiller 19 flows into the accumulator 21 via the sixth three-way joint 13f and the evaporation pressure regulating valve 20, and is separated into gas and liquid. Then, the gas-phase refrigerant separated by the accumulator 21 is sucked from the suction side of the compressor 11 and is compressed by the compressor 11 again.
  • the refrigeration cycle apparatus 10 in the single warm-up mode a refrigeration cycle in which the chiller 19 functions as a radiator is configured.
  • the battery-side heat medium can be heated by the chiller 19, and the battery 80 can be warmed up via the battery-side heat medium.
  • the high-temperature side heat transfer medium pump 41 is stopped, so that the refrigerant flowing into the refrigerant passage of the water-refrigerant heat exchanger 12 hardly radiates heat from the water-refrigerant heat exchanger 12. leak. Therefore, the blown air is not heated by the heater core 42.
  • the battery 80 is heated by flowing the battery-side heat medium heated by the chiller 19 into the heat exchange unit 52 without performing air conditioning in the vehicle interior. Can be warmed up.
  • Heating / warm-up mode In the heating / warm-up mode, the heating expansion valve 14a and the cooling expansion valve 14b are fully closed, and the cooling expansion valve 14c is adjusted to the throttle opening determined in the heating / warm-up mode. I do. Then, the on-off valve 15a for dehumidification is opened, and the on-off valve 15b for heating is closed.
  • the control device 60 controls the operation of the high-temperature side heat medium pump 41 and the battery side heat medium pump 51, respectively, so as to exhibit a predetermined heating medium pumping capacity for the heating warm-up mode. I do.
  • the heat medium pumping capacity of the high-temperature side heat medium pump 41 is determined to be lower than the heat medium pumping capacity of the high-temperature side heat medium pump 41 in the single heating mode.
  • the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows out to the suction port side of the high-temperature side heat medium pump 41.
  • the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • a vapor compression refrigeration cycle is constructed.
  • control device 60 appropriately controls the operation of each device to be controlled.
  • the rotation speed of the compressor 11 is controlled such that the high-temperature-side heat medium temperature TWH approaches the target high-temperature-side heat medium temperature TWHO.
  • the target high-temperature-side heat medium temperature TWHO is determined based on the target blowout temperature TAO with reference to a control map stored in the control device 60 in advance. In this control map, it is determined that the target high-temperature-side heat medium temperature TWHO is increased with the increase of the target outlet temperature TAO so that the temperature of the blown air blown into the vehicle compartment approaches the target outlet temperature TAO.
  • the throttle opening of the cooling expansion valve 14c is controlled such that the battery-side heat medium temperature TWC approaches the target battery-side heat medium temperature TWCO.
  • the target battery-side heat medium temperature TWCO is determined based on the battery temperature TB with reference to a heating / warm-up mode control map stored in the control device 60 in advance. Further, the target battery-side heat medium temperature TWCO is determined to be higher than the temperature of the battery-side heat medium flowing into the water passage of the chiller 19.
  • the actuator for the air mix door is controlled in the same manner as in the single cooling mode.
  • the opening degree SW of the air mix door 34 approaches 100%.
  • the air mix door 34 is displaced such that approximately the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • the heat medium pumping capacity of the high-temperature side heat medium pump 41 is controlled to be lower than in the single heating mode, as described above.
  • Various modes can be adopted as a control mode for realizing this.
  • the rotation speed of the high-temperature heat medium pump 41 may be lower than that in the single heating mode, or control may be performed such that the operation and stop of the high-temperature heat medium pump 41 are periodically repeated.
  • the state of the refrigerant changes as shown in the Mollier diagram of FIG. That is, as indicated by points b1 to b2 in FIG. 4, the refrigerant sucked into the compressor 11 is discharged while being compressed to a high temperature and a high pressure.
  • the high-pressure discharge refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12.
  • the high-temperature side heat medium pump 41 pumps the high-temperature side heat medium at a predetermined heat medium pumping capacity. Accordingly, as indicated by points b2 to b3 in FIG. 4, the heat of the refrigerant flowing into the water-refrigerant heat exchanger 12 is radiated to the high-temperature heat medium circulating in the high-temperature heat medium circuit 40.
  • the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 is smaller than in the single warm-up mode.
  • the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42 by the operation of the high-temperature side heat medium pump 41 and flows inside the indoor air conditioning unit 30. Exchange heat with blast air. Thereby, the temperature of the blown air blown into the vehicle compartment approaches the target blowout temperature TAO.
  • the vehicle air conditioner 1 can supply the blast air heated by the heater core 42 to the vehicle room, which is the space to be air-conditioned, so that the vehicle interior can be heated.
  • the high-temperature-side heat medium is drawn from the heater core 42 into the high-temperature-side heat medium pump 41, and is again pressure-fed to the water passage of the water-refrigerant heat exchanger 12.
  • the refrigerant passes through the bypass passage 22a in the state of a high-temperature, high-pressure hot gas and reaches the cooling expansion valve 14c.
  • the superheated refrigerant is reduced in pressure until it becomes a low-pressure refrigerant.
  • the refrigerant decompressed by the cooling expansion valve 14c flows into the chiller 19 in an overheated state.
  • the battery-side heat medium pump 51 exhibits a predetermined heat medium pumping ability. Therefore, as shown by points b4 to b1 in FIG. 4, the heat of the overheated refrigerant is radiated by the chiller 19 to the battery-side heat medium. Thereby, the battery-side heat medium is heated using the overheated refrigerant as a heat source.
  • the battery-side heat medium heated by the chiller 19 flows into the heat exchange unit 52 by the operation of the battery-side heat medium pump 51, and exchanges heat with the battery 80. Thereby, the battery 80 is heated and the battery 80 can be warmed up.
  • the battery-side heat medium that has flowed out of the heat exchange unit 52 is sucked into the battery-side heat medium pump 51, and is again pumped to the water passage of the chiller 19.
  • the refrigerant flowing out of the chiller 19 flows into the accumulator 21 via the sixth three-way joint 13f and the evaporation pressure regulating valve 20, and is separated into gas and liquid. Then, the gas-phase refrigerant separated by the accumulator 21 is sucked from the suction side of the compressor 11 and is compressed by the compressor 11 again.
  • a refrigeration cycle in which the water-refrigerant heat exchanger 12 and the chiller 19 function as a radiator is configured. Therefore, in the refrigeration cycle apparatus 10 in the heating / warm-up mode, the water-refrigerant heat exchanger 12 can heat the high-temperature side heat medium. Further, the chiller 19 can heat the battery-side heat medium.
  • the vehicle air conditioner 1 in the heating / warm-up mode can use the refrigerant discharged from the compressor 11 as a heat source to heat the blast air via the high-temperature side heat medium, thereby heating the vehicle interior. It can be performed. Further, by causing the battery-side heat medium heated by the chiller 19 to flow into the heat exchange section 52, the battery 80 can be heated and the battery 80 can be warmed up.
  • the control device 60 stops the operation of the high-temperature side heat transfer medium pump 41 to make the heat radiation amount in the refrigerant heat exchanger 12 and the heater core 42 constituting the heating unit the lowest. Then, the control device 60 controls the operation of the battery-side heat medium pump 51 so as to exhibit a predetermined heat medium pumping ability for the single cooling mode.
  • a vapor compression refrigeration cycle is configured.
  • the compressor 11 the (water-refrigerant heat exchanger 12, the heating expansion valve 14a), the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14c, the chiller 19, and the evaporation pressure regulating valve 20 .
  • the refrigerant circulates in the order of the accumulator 21 and the compressor 11.
  • control device 60 appropriately controls the operation of each device to be controlled.
  • the rotation speed of the compressor 11 is controlled such that the battery-side heat medium temperature TWC approaches the target battery-side heat medium temperature TWCO.
  • the target battery-side heat medium temperature TWCO is determined based on the battery temperature TB with reference to a control map for the single cooling mode stored in the control device 60 in advance. In this control map, the target battery-side heat medium temperature TWCO is determined to decrease as the battery temperature TB increases. In the single cooling mode, the target battery-side heat medium temperature TWCO is determined to be lower than the temperature of the battery-side heat medium flowing into the water passage of the chiller 19.
  • the throttle opening of the cooling expansion valve 14c is controlled such that the supercooling degree SC of the refrigerant flowing out of the outdoor heat exchanger 16 approaches the target supercooling degree SCO.
  • the target supercooling degree SCO is determined based on the outside temperature Tam with reference to a control map for the single cooling mode stored in the control device 60 in advance. In this control map, the target degree of supercooling SCO is determined so that the COP of the cycle approaches the maximum value.
  • the actuator for the air mix door is controlled so that the opening degree SW becomes 0%. That is, control is performed such that the cool air bypass passage 35 is fully opened and the air passage on the heater core 42 side is completely closed.
  • the air mixing door 34 completely closes the air passage on the heater core 42 side. Therefore, the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 hardly radiates heat to the blown air by the heater core 42. Further, since the operation of the high-temperature side heat medium pump 41 is stopped, the high-temperature side heat medium does not circulate in the high-temperature side heat medium circuit 40. That is, in the single cooling mode, the blown air is not heated by the heater core 42.
  • the battery-side heat medium cooled by the chiller 19 flows into the heat exchange unit 52 of the battery-side heat medium circuit 50 without performing air conditioning in the vehicle interior. Thereby, the battery 80 can be cooled.
  • Cooling Cooling Mode In the cooling cooling mode, the heating expansion valve 14a is fully opened, and the cooling expansion valve 14b and the cooling expansion valve 14c are respectively adjusted to the throttle openings determined in the cooling cooling mode. Then, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed.
  • the control device 60 stops the operation of the high-temperature side heat transfer medium pump 41 to make the heat radiation amount in the refrigerant heat exchanger 12 and the heater core 42 constituting the heating unit the lowest. Then, the control device 60 controls the operation of the battery-side heat medium pump 51 so as to exhibit a predetermined heat medium pumping ability for the cooling / cooling mode.
  • a vapor compression refrigeration cycle is configured.
  • the compressor 11, the water-refrigerant heat exchanger 12, the (heating expansion valve 14a), the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure adjustment The refrigerant circulates in the order of the valve 20, the accumulator 21, and the compressor 11.
  • the refrigerant circulates in the order of the compressor 11.
  • the flow path of the refrigerant in the order of the cooling expansion valve 14b and the indoor evaporator 18 and the flow path of the refrigerant in the order of the cooling expansion valve 14c and the chiller 19 become the refrigerant flow.
  • the refrigerant circuit is switched to a refrigerant circuit connected in parallel.
  • the control device 60 appropriately controls the operation of each device to be controlled. For example, with respect to the compressor 11, the rotation speed (that is, the refrigerant discharge capacity) is controlled such that the evaporator temperature Tefin detected by the evaporator temperature sensor 66 approaches the target evaporator temperature TEO.
  • the target evaporator temperature TEO is determined based on the target blowout temperature TAO with reference to a control map stored in the control device 60 in advance. In this control map, the target evaporator temperature TEO is determined to decrease as the target outlet temperature TAO decreases.
  • the expansion opening of the cooling expansion valve 14b is controlled so that the degree of supercooling SC of the refrigerant flowing out of the refrigerant passage of the outdoor heat exchanger 16 approaches the target degree of supercooling SCO.
  • This degree of supercooling SC is calculated from the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P1 detected by the first refrigerant pressure sensor 65a.
  • the target degree of subcooling SCO is determined based on the outside temperature Tam with reference to a control map stored in the control device 60 in advance. In this control map, the target degree of supercooling SCO is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • the throttle opening of the cooling expansion valve 14c is controlled such that the superheat degree SHC of the refrigerant flowing out of the refrigerant passage of the chiller 19 approaches the target superheat degree SHCO.
  • the superheat degree SHC is calculated from the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P2 detected by the second refrigerant pressure sensor 65b.
  • a predetermined constant 5 ° C. in the present embodiment
  • the target battery-side heat medium temperature TWCO is determined based on the battery temperature TB with reference to a control map stored in the control device 60 in advance. In this control map, the target battery-side heat medium temperature TWCO is determined to decrease as the battery temperature TB increases. At this time, in the cooling cooling mode, the target battery-side heat medium temperature TWCO is determined to be lower than the temperature of the battery-side heat medium flowing into the water passage of the chiller 19.
  • the actuator for the air mix door is controlled so that the opening degree SW becomes 0%. That is, control is performed such that the cool air bypass passage 35 is fully opened and the air passage on the heater core 42 side is completely closed.
  • the outdoor heat exchanger 16 functions as a radiator
  • the indoor evaporator 18 and the chiller 19 function as evaporators.
  • the air blown by the indoor evaporator 18 can be cooled.
  • the battery-side heat medium can be cooled by the chiller 19. Cooling can be performed.
  • the control device 60 controls the operation of the high-temperature side heat medium pump 41 and the battery side heat medium pump 51 so as to exhibit a predetermined heat medium pumping capacity for the series dehumidifying heating / cooling mode.
  • the heat medium pumping capacity of the high-temperature side heat medium pump 41 is controlled to be lower than the heat medium pumping capacity of the high-temperature side heat medium pump 41 in the single heating mode.
  • the heat radiation amount in the refrigerant heat exchanger 12 and the heater core 42 that constitute the heating unit is controlled to be lower than in the single heating mode.
  • the rotation speed of the high-temperature heat medium pump 41 may be reduced, or the heat medium pump 41 may be controlled to operate intermittently.
  • the compressor 11, the water-refrigerant heat exchanger 12, the (heating expansion valve 14a), the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, and the indoor evaporator 18 The refrigerant circulates in the order of the evaporation pressure adjusting valve 20, the accumulator 21, and the compressor 11.
  • the compressor 11, the water-refrigerant heat exchanger 12, (the heating expansion valve 14a), the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21 Then, a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the compressor 11 is configured.
  • the two paths pass through the refrigerant flow. Connected in parallel.
  • the two paths are a path through which the refrigerant flows in the order of the cooling expansion valve 14b and the indoor evaporator 18, and a path through which the refrigerant flows in the order of the cooling expansion valve 14c and the chiller 19.
  • the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator, and the indoor evaporator 18 and the chiller 19 function as an evaporator.
  • control device 60 appropriately controls the operation of various control target devices as in the cooling / cooling mode.
  • the opening degree SW of the air mix door 34 is determined in the same manner as in the single series dehumidifying and heating mode.
  • the high-temperature heat medium pump 41 is operated to circulate the high-temperature heat medium in the high-temperature heat medium circuit 40. Is dissipated to the high-temperature side heat medium.
  • the blown air cooled by the indoor evaporator 18 passes through the heater core 42 of the high-temperature side heat medium circuit 40. It can be heated by the heat of the heat medium.
  • the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, thereby dehumidifying the vehicle interior. Heating can be performed.
  • the heating capability of the blower air in the heater core 42 can be improved.
  • the vehicle air conditioner 1 in the series dehumidification heating cooling mode can cool the battery-side heat medium by the chiller 19 while performing the dehumidification and heating. By flowing the battery, the battery 80 can be cooled.
  • the control device 60 controls the operation of the high-temperature side heat medium pump 41 and the battery side heat medium pump 51 so as to exhibit a predetermined heat medium pumping capacity for the parallel dehumidifying heating / cooling mode.
  • the heat medium pumping capacity of the high-temperature heat medium pump 41 is controlled so as to be lower in the parallel dehumidification heating mode than in the single heating mode. That is, the heat radiation amount in the refrigerant heat exchanger 12 and the heater core 42 that constitute the heating unit is controlled to be lower than in the single heating mode.
  • the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the compressor 11. .
  • the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • the refrigerant circulates in parallel with the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 in parallel.
  • a vapor compression refrigeration cycle is constructed.
  • the refrigerant branches into three refrigerant paths. That is, a path through which the refrigerant flows in the order of the heating expansion valve 14a and the outdoor heat exchanger 16, a path through which the refrigerant flows in the order of the cooling expansion valve 14b and the indoor evaporator 18, and a refrigerant in the order of the cooling expansion valve 14c and the chiller 19. Are connected in parallel to the refrigerant flow.
  • the water-refrigerant heat exchanger 12 functions as a radiator, and the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 19 connected in parallel to the refrigerant flow function as evaporators. I do.
  • control device 60 appropriately controls the operation of various control target devices as in the cooling / cooling mode.
  • the opening degree SW of the air mix door 34 is determined in the same manner as in the single parallel dehumidifying and heating mode.
  • the high-temperature heat medium pump 41 is operated to circulate the high-temperature heat medium in the high-temperature heat medium circuit 40 and to control the opening degree SW of the air mix door 34.
  • the blown air cooled by the indoor evaporator 18 passes through the heater core 42 of the high-temperature side heat medium circuit 40.
  • the air blown by cooling and dehumidification by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, thereby dehumidifying the vehicle interior. Heating can be performed.
  • the vehicle air conditioner 1 in the parallel dehumidification heating / cooling mode can cool the battery 80 by flowing the battery-side heat medium cooled by the chiller 19 into the heat exchange unit 52.
  • the control device 60 controls the operations of the high-temperature heat medium pump 41 and the battery-side heat medium pump 51 so as to exhibit a predetermined heat medium pumping ability for the first heating / cooling mode.
  • the heat medium pumping capacity of the high temperature side heat medium pump 41 is controlled to be equal to the heat medium pumping capacity of the high temperature side heat medium pump 41 in the single heating mode.
  • a vapor compression refrigeration cycle is configured.
  • the compressor 11 the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14c, the chiller 19, and the evaporation pressure regulating valve 20 .
  • the refrigerant circulates in the order of the accumulator 21 and the compressor 11.
  • control device 60 appropriately controls the operation of each device to be controlled.
  • the rotation speed of the compressor 11 is controlled such that the high-temperature-side heat medium temperature TWH approaches the target high-temperature-side heat medium temperature TWHO.
  • the target high-temperature-side heat medium temperature TWHO is determined based on the target blowout temperature TAO with reference to a control map stored in the control device 60 in advance. In this control map, it is determined that the target high-temperature-side heat medium temperature TWHO is increased with the increase of the target outlet temperature TAO so that the temperature of the blown air blown into the vehicle compartment approaches the target outlet temperature TAO.
  • the supercooling degree SC of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 becomes the target supercooling degree SCO. It is controlled to approach.
  • the throttle opening of the heating expansion valve 14a and the cooling expansion valve 14c decreases as the target outlet temperature TAO increases, and the throttle opening of the heating expansion valve 14a decreases.
  • the opening is determined so as to increase.
  • the actuator for the air mix door is controlled in the same manner as in the single cooling mode.
  • the opening degree SW of the air mix door 34 approaches 100%.
  • the air mix door 34 is displaced such that approximately the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • the water-refrigerant heat exchanger 12 functions as a radiator
  • the chiller 19 functions as an evaporator.
  • the chiller 19 can cool the battery 80 via the battery-side heat medium and can heat the blown air via the water-refrigerant heat exchanger 12 and the heater core 42. Therefore, in the vehicle air conditioner 1 in the first heating / cooling mode, heating of the vehicle interior and cooling of the battery 80 can be performed in parallel.
  • a cooling priority mode and a heating priority mode can be executed.
  • the outdoor heat exchanger 16 is made to function as a radiator, and the cooling of the battery 80 is mainly performed in the heating of the vehicle interior and the cooling of the battery 80.
  • the outdoor heat exchanger 16 is made to function as a heat absorber, and heating of the vehicle interior is performed with emphasis on heating of the vehicle interior and cooling of the battery 80.
  • the cooling priority mode and the heating priority mode in the first heating / cooling mode are switched by controlling the throttle opening EX1 of the heating expansion valve 14a and the throttle opening EX2 of the cooling expansion valve 14c. Specifically, the switching is performed by adjusting the opening ratio EX1 / EX2 of the throttle opening EX1 of the heating expansion valve 14a to the throttle opening EX2 of the cooling expansion valve 14c.
  • the control device 60 increases the throttle opening EX1 of the heating expansion valve 14a and decreases the throttle opening EX2 of the cooling expansion valve 14c. That is, the opening degree ratio EX1 / EX2 is adjusted to be large. Thereby, the saturation temperature of the refrigerant in the outdoor heat exchanger 16 becomes higher than the outside air temperature Tam, so that the outdoor heat exchanger 16 functions as a radiator for the outside air.
  • the state of the refrigerant changes as shown in the Mollier diagram shown in FIG. That is, as indicated by points c1 to c2 in FIG. 5, the refrigerant drawn into the compressor 11 is discharged in a state where it is compressed to a high temperature and a high pressure.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the discharged refrigerant is supplied to the water passage of the water-refrigerant heat exchanger 12 as shown by points c2 to c3 in FIG. Heat is exchanged with the high-temperature side heat medium flowing through and heat is radiated.
  • the high-temperature side heat medium flowing through the water passage of the water-refrigerant heat exchanger 12 is heated.
  • the high-temperature side heat medium heated in the water passage of the water-refrigerant heat exchanger 12 exchanges heat with the blown air in the heater core 42 to radiate heat.
  • the temperature of the blown air blown into the vehicle compartment approaches the target blowout temperature TAO.
  • the high-temperature-side heat medium flowing out of the heater core 42 is sucked into the high-temperature-side heat medium pump 41 through the high-temperature-side three-way valve 43 and is again pressure-fed to the water passage of the water-refrigerant heat exchanger 12.
  • the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 reaches the heating expansion valve 14a without flowing into the bypass passage 22a, and is reduced in pressure as shown by points c3 to c4 in FIG.
  • the saturation temperature of the refrigerant depressurized by the heating expansion valve 14a becomes higher than the outside air temperature Tam. Accordingly, as indicated by points c4 to c5 in FIG. 5, the refrigerant decompressed by the heating expansion valve 14a exchanges heat with the outside air in the outdoor heat exchanger 16 and radiates heat.
  • the gas-phase refrigerant separated by the accumulator 21 is drawn into the compressor 11 and compressed again, as shown at point c1 in FIG.
  • the refrigeration cycle apparatus 10 in the cooling priority mode in the first heating / cooling mode the refrigeration in which the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator and the chiller 19 functions as an evaporator.
  • a cycle is configured. That is, since the refrigerant radiates heat also in the outdoor heat exchanger 16, the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 is smaller than in the heating priority mode. In other words, the cooling of the battery 80 can be performed more heavily than the heating of the vehicle interior.
  • the control device 60 decreases the throttle opening EX1 of the heating expansion valve 14a and increases the throttle opening EX2 of the cooling expansion valve 14c. That is, the opening degree ratio EX1 / EX2 is adjusted to be small. Thereby, the saturation temperature of the refrigerant in the outdoor heat exchanger 16 becomes lower than the outside air temperature Tam, so that the outdoor heat exchanger 16 functions as a heat absorber for the outside air.
  • the state of the refrigerant changes as shown in the Mollier diagram shown in FIG. That is, as indicated by points d1 to d2 in FIG. 6, the refrigerant drawn into the compressor 11 is discharged while being compressed to a high temperature and a high pressure.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the discharged refrigerant is supplied to the water passage of the water-refrigerant heat exchanger 12 as shown by points d2 to d3 in FIG. Heat is exchanged with the high-temperature side heat medium flowing through and heat is radiated.
  • the high-temperature side heat medium flowing through the water passage of the water-refrigerant heat exchanger 12 is heated.
  • the blower air is heated by the heater core 42, similarly to the cooling priority mode in the first heating / cooling mode. Thereby, the temperature of the blown air blown into the vehicle compartment approaches the target blowout temperature TAO.
  • the refrigerant that has flowed out of the refrigerant passage of the water-refrigerant heat exchanger 12 reaches the heating expansion valve 14a without flowing into the bypass passage 22a, and is reduced in pressure as indicated by points d3 to d4 in FIG.
  • the saturation temperature of the refrigerant depressurized by the heating expansion valve 14a becomes lower than the outside air temperature Tam. Accordingly, as indicated by points d4 to d5 in FIG. 6, the refrigerant decompressed by the heating expansion valve 14a exchanges heat with the outside air in the outdoor heat exchanger 16 and absorbs heat from the outside air.
  • the gas-phase refrigerant separated by the accumulator 21 is drawn into the compressor 11 and compressed again, as shown at point d1 in FIG.
  • the water-refrigerant heat exchanger 12 functions as a radiator
  • the outdoor heat exchanger 16 and the chiller 19 function as heat absorbers. Can be.
  • the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, the amount of heat released by the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the heating capability of the blower air by the heater core 42 can be improved. it can. That is, according to the heating priority mode in the first heating / cooling mode, the heating of the vehicle interior can be performed more heavily than the cooling of the battery 80.
  • Second heating / cooling mode In the second heating / cooling mode, the cooling expansion valve 14c is adjusted to the throttle opening determined in the second heating / cooling mode, and the heating expansion valve 14a and the cooling expansion valve 14b are controlled. Make it fully closed. The on-off valve 15a for dehumidification is opened, and the on-off valve 15b for heating is closed.
  • the control device 60 controls the operations of the high-temperature side heat medium pump 41 and the battery side heat medium pump 51 so as to exhibit the predetermined heat medium pumping ability for the second heating / cooling mode.
  • the heat medium pumping capacity of the high temperature side heat medium pump 41 is controlled to be equal to the heat medium pumping capacity of the high temperature side heat medium pump 41 in the single heating mode.
  • the refrigerant flows in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • a circulating vapor compression refrigeration cycle is configured.
  • control device 60 appropriately controls the operation of each device to be controlled.
  • the rotation speed of the compressor 11 is controlled such that the high-temperature-side heat medium temperature TWH approaches the target high-temperature-side heat medium temperature TWHO.
  • the target high-temperature-side heat medium temperature TWHO is determined with reference to a control map stored in the control device 60 in advance, as in the first heating / cooling mode.
  • the throttle opening degree of the cooling expansion valve 14c is controlled such that the supercooling degree SC of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO.
  • the actuator for the air mix door is controlled in the same manner as in the single cooling mode.
  • the opening degree SW of the air mix door 34 approaches 100%.
  • the water-refrigerant heat exchanger 12 functions as a radiator
  • the chiller 19 functions as an evaporator.
  • the chiller 19 can cool the battery 80 via the battery-side heat medium and can heat the blown air via the water-refrigerant heat exchanger 12 and the heater core 42. Therefore, in the vehicle air conditioner 1 in the second heating / cooling mode, heating of the vehicle interior and cooling of the battery 80 can be performed in parallel.
  • the outdoor heat exchanger 16 is disposed on the front side inside the drive unit room, and outside air such as traveling wind introduced from the outside of the drive unit room and refrigerant flowing inside the outside. And heat exchange.
  • the vehicle air conditioner 1 employs a cycle configuration in which the refrigerant passes through the outdoor heat exchanger 16
  • the heat exchange with the outside air in the outdoor heat exchanger 16 affects the air conditioning in the passenger compartment and the cooling of the battery 80. May be affected.
  • the refrigerant flowing out of the water-refrigerant heat exchanger 12 is guided to the cooling expansion valve 14c via the bypass passage 22a, thereby increasing the heating expansion.
  • the valve 14a and the outdoor heat exchanger 16 are bypassed. According to this configuration, the influence of heat exchange with the outside air in the outdoor heat exchanger 16 can be suppressed, and the heating of the vehicle interior and the cooling of the battery 80 can be controlled with high accuracy.
  • the temperatures of the high-temperature heat medium and the battery-side heat medium are controlled in advance in order to cope with an increase in the required amount of heat due to the switching of the operation mode.
  • the shortage of the amount of heat due to the switching of the operation mode is reduced, and the influence on the air conditioning in the vehicle compartment and the temperature adjustment of the battery 80 is suppressed.
  • the refrigeration cycle apparatus 10 of the present embodiment when the rapid charging of the battery 80 is started in a state where the heating of the vehicle interior is requested, the operation in the single heating mode is performed. Thereafter, when the rapid charging is completed, the mode is switched from the single heating mode to the heating warm-up mode.
  • the target high-temperature-side heat medium temperature TWHO is increased. That is, in the refrigeration cycle device 10 of the present embodiment, when the rapid charging of the battery 80 is started in a state where the heating of the vehicle interior is requested, it is determined that the predetermined heating switching condition is satisfied.
  • the target high-temperature side heat medium temperature TWHO is increased to increase the temperature of the high-temperature side heat medium before switching from the single heating mode to the heating warm-up mode. I have.
  • the battery 80 is warmed up in addition to the heating of the cabin due to the driving condition in which the cabin is heated. Therefore, there is a possibility that the amount of heat for heating the vehicle interior may be insufficient.
  • the vehicle air conditioner 1 when the heating switching condition is satisfied, the temperature of the high-temperature side heat medium is raised, so that heat can be stored in the high-temperature side heat medium circuit 40. Thereby, the vehicle air conditioner 1 can suppress the effect of the warm-up of the battery 80 in the heating warm-up mode on the heating of the vehicle interior (that is, the temperature fluctuation of the blown air during heating).
  • the refrigeration cycle apparatus 10 of the present embodiment can perform pre-air conditioning.
  • the pre-air conditioning is executed by the occupant having the control device 60 store the target temperature Tset in the vehicle compartment, the pre-air-conditioning start time, and the like using the operation panel 70 or the remote control terminal.
  • the pre-air-conditioning start time is a time at which the time when the occupant gets on board is approaching, and there is a high possibility that the vehicle will travel in the relatively near future.
  • the battery temperature TB is equal to or lower than the reference lower limit temperature KTBL at a time that is a predetermined time before the pre-air conditioning start time (for example, 10 minutes before).
  • the operation is performed in the single warm-up mode. Thereafter, when the pre-air conditioning start time comes, the operation mode of the vehicle air conditioner 1 is switched from the single warm-up mode to the heating warm-up mode.
  • the target battery-side heat medium temperature TWCO is increased. That is, in the refrigeration cycle apparatus 10 of the present embodiment, when the pre-air conditioning is set and the operation in the single warm-up mode is performed, it is determined that the predetermined warm-up switching condition is satisfied.
  • the target battery-side heat medium temperature TWCO is increased to increase the temperature of the battery-side heat medium before switching from the single warm-up mode to the heating warm-up mode. Has become.
  • the pre-air conditioning of the vehicle compartment is performed in accordance with the operation state of the warm-up of the battery 80.
  • the amount of heat for warming up the battery 80 in the machine mode may be insufficient.
  • the vehicle air conditioner 1 when the warm-up switching condition is satisfied, the temperature of the battery-side heat medium is raised, so that heat can be stored in the battery-side heat medium circuit 50, and heating is performed. The effect of starting the pre-air conditioning in the warm-up mode on the warm-up of the battery 80 can be suppressed.
  • the refrigeration cycle apparatus 10 As described above, according to the refrigeration cycle apparatus 10 according to the present embodiment, the operations of the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, the dehumidifying on-off valve 15a, and the heating on-off valve 15b. , The refrigerant circuit of the refrigeration cycle device 10 is switched. Thereby, the refrigeration cycle apparatus 10 can realize 12 types of operation modes from (1) single cooling mode to (12) second heating / cooling mode.
  • the refrigeration cycle apparatus 10 allows the outdoor heat exchanger 16 to function as a radiator by setting the operation mode to the cooling cooling mode, and also functions the indoor evaporator 18 and the chiller 19 as a heat exchange unit for temperature control as a heat absorber. Can be done. As a result, the refrigeration cycle apparatus 10 can achieve both the cooling of the vehicle interior and the cooling of the battery 80, which is a temperature adjustment target, in the vehicle air conditioner 1.
  • the refrigeration cycle apparatus 10 can guide the refrigerant discharged from the compressor 11 to the chiller 19 via the bypass passage 22a by switching the operation mode. Thereby, the refrigeration cycle apparatus 10 can warm up the battery 80 in the vehicle air conditioner 1 using the heat of the discharged refrigerant as a heat source.
  • the refrigeration cycle apparatus 10 can improve the comfort in the vehicle compartment and adjust the battery 80 within an appropriate temperature range.
  • the refrigeration cycle apparatus 10 includes a high-temperature side heat medium circuit 40 as a heating unit including a water-refrigerant heat exchanger 12, a heating expansion valve 14a, a heating open / close valve 15b, and a heating passage 22b. Is arranged. For this reason, the refrigeration cycle apparatus 10 can heat the blown air using the heat of the discharged refrigerant as a heat source in the heater core 42 of the high-temperature side heat medium circuit 40, and realizes heating of the vehicle interior in the vehicle air conditioner 1. be able to.
  • the operation of the high-temperature side heat medium pump 41 of the high-temperature side heat medium circuit 40 is stopped to minimize the amount of heat discharged from the water-refrigerant heat exchanger 12 by the discharged refrigerant. Can be supplied to the chiller 19 as much as possible. As a result, the refrigeration cycle device 10 can quickly warm up the battery 80 in the vehicle air conditioner 1.
  • the heat medium pumping capacity of the high-temperature side heat medium pump 41 in the high-temperature side heat medium circuit 40 is adjusted to be lower than in the single heating mode, so that the heat release amount of the discharged refrigerant in the water-refrigerant heat exchanger 12 is adjusted. Can be lower than in the single heating mode.
  • the heating of the blown air in the high-temperature side heat medium circuit 40 and the heating of the battery 80 in the battery side heat medium circuit 50 are realized using the heat of the discharged refrigerant.
  • both heating of the vehicle interior and warming up of the battery 80 can be achieved.
  • the compressor 11 In the first heating / cooling mode, the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14c, the chiller 19, and the evaporating pressure control are provided.
  • the refrigeration cycle apparatus 10 allows the water-refrigerant heat exchanger 12 to function as a radiator and the chiller 19 to function as a heat absorber. As a result, the refrigeration cycle apparatus 10 can achieve both heating of the blown air in the high-temperature side heat medium circuit 40 and cooling of the battery 80 in the battery side heat medium circuit 50.
  • the outdoor heat exchanger 16 is controlled by adjusting the opening ratio EX1 / EX2 of the throttle opening EX1 of the heating expansion valve 14a to the throttle opening EX2 of the cooling expansion valve 14c. It can function as either a radiator or a heat sink.
  • the outdoor heat exchanger 16 functions as a radiator in the first heating / cooling mode
  • the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator
  • the chiller 19 functions as a heat absorber. become. Therefore, the cooling of the battery 80 can be performed more heavily than the heating of the vehicle interior.
  • the refrigerant heat exchanger 12 functions as a radiator
  • the outdoor heat exchanger 16 and the chiller 19 function as heat absorbers. Become. For this reason, the heating of the vehicle interior can be performed more heavily than the cooling of the battery 80.
  • the refrigeration cycle apparatus 10 can switch the function of the outdoor heat exchanger 16 to one of the cooling priority mode and the heating priority mode. This makes it possible to balance heating of the vehicle interior and cooling of battery 80 in an appropriate manner according to the situation of the vehicle.
  • the refrigerant flows in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • a circulating vapor compression refrigeration cycle is configured.
  • the water-refrigerant heat exchanger 12 functions as a radiator
  • the chiller 19 functions as a heat absorber. According to this, the chiller 19 can cool the battery 80 via the battery-side heat medium and can heat the blown air via the water-refrigerant heat exchanger 12 and the heater core 42.
  • the refrigerant flowing out of the water-refrigerant heat exchanger 12 passes through the bypass passage 22a and flows into the cooling expansion valve 14c. You are bypassing. Thereby, the refrigeration cycle apparatus 10 can suppress the influence of heat exchange with the outside air in the outdoor heat exchanger 16, and can accurately balance the heating of the vehicle interior and the cooling of the battery 80.
  • the temperature of the high-temperature side heat medium is increased before switching from the single heating mode to the heating warm-up mode. According to this, the temperature of the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40 can be increased before switching to the heating / warm-up mode, and heat can be stored in the high-temperature side heat medium circuit 40.
  • the heat stored in the high-temperature side heat medium circuit 40 is used to suppress a decrease in the heating capacity of the blown air, Warm up can be performed.
  • the temperature of the battery-side heat medium is increased before switching from the single warm-up mode to the heating warm-up mode.
  • the temperature of the battery-side heat medium circulating in the battery-side heat medium circuit 50 can be increased before switching to the heating / warm-up mode, and the heat can be stored in the battery-side heat medium circuit 50.
  • the heat stored in the battery-side heat medium circuit 50 is used to suppress a decrease in the heating capacity of the battery 80, and quickly.
  • the blast air can be heated.
  • the heating capacity of the refrigeration cycle device 10 is used to heat the blown air when switching from the single warm-up mode to the heating temperature control mode, the heat stored in the battery-side heat medium circuit 50 is used. , The battery 80 can be warmed up.
  • the refrigeration cycle device 10 according to the present disclosure is applied to the vehicle air conditioner 1 mounted on an electric vehicle and the temperature adjustment target is the battery 80 has been described.
  • the application object of the refrigeration cycle device is not limited to this.
  • the present invention may be applied to a vehicle air conditioner mounted on a hybrid vehicle that obtains a driving force for vehicle traveling from both an engine and an electric motor.
  • the temperature adjustment target is not limited to the battery 80, but may be an in-vehicle device such as an inverter or a motor generator.
  • the application of the present disclosure is not limited to vehicles, and may be applied to an air conditioner or the like having a server temperature adjustment function for performing indoor air conditioning while appropriately adjusting the temperature of a computer server.
  • the refrigeration cycle apparatus 10 that can be switched to a plurality of operation modes has been described.
  • the switching of the operation mode is not limited to the one disclosed in the above-described embodiment.
  • the effects in the cooling cooling mode and the single warm-up mode can be performed, the effect of achieving both the improvement of the comfort in the vehicle compartment by the cooling and the realization of the appropriate temperature adjustment of the temperature adjustment target can be obtained. be able to.
  • the heating warm-up mode and the first heating / cooling mode or the second heating / cooling mode can be executed, the realization of appropriate temperature adjustment of the temperature adjustment target and the improvement of the comfort in the vehicle compartment due to heating can be achieved. The effect of achieving both can be obtained.
  • each operation mode is not limited to the mode disclosed in each of the above embodiments.
  • a switch for switching may be provided on the operation panel 70, and each operation mode may be switched by the operation of the occupant.
  • the configuration of the refrigeration cycle device 10 is not limited to the configuration disclosed in the above embodiment.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c those in which an electric expansion valve having no fully closed function and an on-off valve may be directly connected may be employed. Then, a plurality of cycle components may be integrated.
  • the temperature-type expansion valve includes a temperature-sensitive portion having a deformable member (specifically, a diaphragm) that is deformed in accordance with the temperature and pressure of the refrigerant flowing from the refrigerant passage, and a throttle that is displaced in accordance with the deformation of the deformable member.
  • a deformable member specifically, a diaphragm
  • a mechanical mechanism including a valve body that changes the opening degree can be employed.
  • R1234yf is used as the refrigerant
  • the refrigerant is not limited to this.
  • R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted.
  • a mixed refrigerant obtained by mixing plural kinds of these refrigerants may be employed.
  • a supercritical refrigeration cycle in which carbon dioxide is adopted as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.
  • the control mode of the refrigeration cycle device 10 is not limited to those disclosed in each of the above embodiments.
  • the operation of the actuator for the air mix door may be controlled such that the blast air temperature TAV detected by the conditioned air temperature sensor 69 approaches the target outlet temperature TAO.
  • the heating unit configured by the respective components of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 is employed, but the heating unit is not limited to this.
  • an indoor condenser that directly exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air may be adopted, and the indoor condenser may be arranged in the air-conditioning case 31 like the heater core 42.
  • the refrigeration cycle device 10 when the refrigeration cycle device 10 is applied to an air conditioner for a vehicle mounted on a hybrid vehicle, the engine cooling water may flow into the high-temperature side heat medium circuit 40 and circulate. According to this, the blown air can be heated by the heater core 42 using the waste heat of the engine as a heat source.
  • the temperature adjustment unit constituted by the components of the chiller 19 and the battery-side heat medium circuit 50 is employed, but the temperature adjustment unit is not limited to this.
  • a heat exchange unit for temperature adjustment that directly exchanges heat between the refrigerant flowing out of the cooling expansion valve 14c and the battery 80 may be employed.
  • a heat exchanger for exchanging heat between the refrigerant flowing out of the cooling expansion valve 14c and the air for temperature adjustment, and the air for temperature adjustment adjusted in temperature by the heat exchanger to the battery 80.
  • a blower for adjusting the temperature to be blown may be employed.
  • the high-temperature side heat medium circuit 40 and the battery side heat medium circuit 50 described in the above-described embodiment may be connected to each other via an on-off valve or the like so that the high-temperature side heat medium and the battery side heat medium can be mixed. Good.
  • one end of the bypass passage 22a is connected to the refrigerant flow path from the outlet of the water-refrigerant heat exchanger 12 to the inlet of the heating expansion valve 14a, and the other end of the check valve 17 is connected to the other end.
  • the present invention is not limited to this mode.
  • the bypass passage 22a may employ various configurations as long as the refrigerant discharged from the compressor 11 can be guided to the upstream side of the fifth three-way joint 13e, bypassing the outdoor heat exchanger 16.
  • one end of the bypass passage 22a may be connected to a refrigerant passage from a discharge port of the compressor 11 to an inlet of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • connection of the heating passage 22b is not limited to the above-described embodiment.
  • the heating passage 22b employs various connection modes as long as the refrigerant flowing out of the outdoor heat exchanger 16 can be guided to the suction port side of the compressor 11 by bypassing the indoor evaporator 18 and the chiller 19. Can be.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)
PCT/JP2019/032752 2018-09-06 2019-08-22 冷凍サイクル装置 Ceased WO2020050040A1 (ja)

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DE112019004481.8T DE112019004481T5 (de) 2018-09-06 2019-08-22 Kältekreisvorrichtung
US17/191,487 US12038207B2 (en) 2018-09-06 2021-03-03 Refrigeration cycle device

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JP2023107645A (ja) * 2022-01-24 2023-08-03 サンデン株式会社 車両用空調装置
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CN116056932A (zh) * 2020-09-23 2023-05-02 三电株式会社 热管理系统

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US12038207B2 (en) 2024-07-16
CN112638674A (zh) 2021-04-09
CN112638674B (zh) 2024-09-17
US20210190389A1 (en) 2021-06-24
DE112019004481T5 (de) 2021-06-10

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