WO2022030182A1 - 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
WO2022030182A1
WO2022030182A1 PCT/JP2021/025950 JP2021025950W WO2022030182A1 WO 2022030182 A1 WO2022030182 A1 WO 2022030182A1 JP 2021025950 W JP2021025950 W JP 2021025950W WO 2022030182 A1 WO2022030182 A1 WO 2022030182A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
outside air
heating mode
heat
temperature
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/JP2021/025950
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English (en)
French (fr)
Japanese (ja)
Inventor
祐一 加見
大輝 加藤
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 DE112021004134.7T priority Critical patent/DE112021004134T5/de
Publication of WO2022030182A1 publication Critical patent/WO2022030182A1/ja
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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
    • 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
    • B60H1/3204—Cooling devices using compression
    • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
    • B60H1/32284—Cooling devices using compression characterised by refrigerant circuit configurations comprising two or more secondary circuits, e.g. at evaporator and condenser side
    • 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
    • B60H1/3204—Cooling devices using compression
    • B60H1/323—Cooling devices using compression characterised by comprising auxiliary or multiple systems, e.g. plurality of evaporators, or by involving auxiliary cooling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H2001/00307—Component temperature regulation using a liquid flow
    • 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
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
    • B60H2001/3257—Cooling devices information from a variable is obtained related to temperature of the refrigerant at a compressing unit
    • 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
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
    • B60H2001/3258—Cooling devices information from a variable is obtained related to temperature of the air at a condensing unit
    • 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
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
    • B60H2001/326—Cooling devices information from a variable is obtained related to temperature of the refrigerant at a condensing unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present disclosure relates to a refrigeration cycle device that absorbs heat from a plurality of heat sources to perform heating.
  • the vehicle air conditioner described in Patent Document 1 heats the vehicle interior by absorbing heat from an outdoor heat exchanger and a non-temperature control target.
  • the waste heat of the non-temperature control target is used for heating, thereby improving the efficiency and performance of the heating.
  • the refrigerant temperature in the outdoor heat exchanger may be higher than the outside air temperature.
  • the outdoor heat exchanger dissipates heat from the refrigerant to the outside air, which deteriorates the efficiency and performance of heating.
  • the present disclosure aims to improve the efficiency of heating in a refrigeration cycle apparatus that absorbs heat from a plurality of heat sources to perform heating.
  • the refrigerating cycle apparatus includes a compressor, a heating unit, an expansion valve for heating, an outdoor heat exchanger, an expansion valve for cooling, an indoor evaporator, an expansion valve for heat absorption, and an endothermic unit. , A refrigerant circuit switching unit, and a control unit.
  • the compressor compresses and discharges the refrigerant.
  • the heating unit heats the air blown to the air-conditioned space using the discharged refrigerant discharged from the compressor as a heat source.
  • the expansion valve for heating decompresses the refrigerant flowing out from the heating part.
  • the outdoor heat exchanger exchanges heat between the refrigerant flowing out from the heating expansion valve and the outside air.
  • the cooling expansion valve reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger.
  • the indoor evaporator evaporates the refrigerant flowing out from the cooling expansion valve to cool the air before being heated by the heating unit.
  • the endothermic expansion valve reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger.
  • the endothermic unit evaporates the refrigerant flowing out from the endothermic expansion valve and absorbs heat from the endothermic object.
  • the refrigerant circuit switching unit is a waste heat heating mode refrigerant circuit that does not absorb heat from the outside air with the outdoor heat exchanger but absorbs heat from the endothermic object with the heat absorbing part, and the outdoor heat exchanger absorbs heat from the outside air and the endothermic object with the heat absorbing part. Switch to the outside air waste heat heating mode endothermic circuit that absorbs heat from.
  • the control unit In the outside air waste heat heating mode, the control unit has the outside air refrigerant temperature difference, which is the temperature difference obtained by subtracting the temperature of the refrigerant sucked into the compressor from the outside air temperature Tam, not more than the lower limit temperature difference, and the temperature of the heat absorbing object. If is equal to or higher than the heat absorption temperature, the refrigerant circuit switching unit is controlled so as to switch to the waste heat heating mode.
  • the refrigeration cycle device 10 of the present embodiment is applied to a vehicle air conditioner 1 mounted on an electric vehicle.
  • An electric vehicle is a vehicle that obtains driving force for traveling from an electric motor.
  • the vehicle air conditioner 1 air-conditions the interior of the vehicle, which is the space to be air-conditioned.
  • the vehicle air conditioner 1 includes a refrigerating cycle device 10, an indoor air conditioner unit 30, a high temperature side heat medium circuit 40, a low temperature side heat medium circuit 50, and the like.
  • the refrigerating cycle device 10 cools the air blown into the vehicle interior and heats the high temperature side heat medium circulating in the high temperature side heat medium circuit 40 in order to air-condition the vehicle interior.
  • the refrigeration cycle device 10 cools the low temperature side heat medium circulating in the low temperature side heat medium circuit 50 in order to absorb heat from the waste heat device 80.
  • the refrigerating cycle device 10 can switch the refrigerant circuit for various operation modes in order to perform air conditioning in the vehicle interior. For example, the refrigerant circuit in the cooling mode, the refrigerant circuit in the dehumidifying / heating mode, the refrigerant circuit in the heating mode, and the like can be switched.
  • the refrigeration cycle apparatus 10 employs an HFO-based refrigerant (specifically, R1234yf) as the refrigerant, and the pressure of the discharged refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant, which is a steam compression type subcritical. It constitutes a refrigeration cycle.
  • Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. Some of the refrigerating machine oil circulates in the cycle together with the refrigerant.
  • the compressor 11 sucks the refrigerant in the refrigerating cycle device 10, compresses it, and discharges it.
  • the compressor 11 is arranged in front of the vehicle interior and is arranged in the drive unit chamber in which the electric motor and the like are housed.
  • the compressor 11 is an electric compressor that rotationally drives a fixed-capacity compression mechanism having a fixed discharge capacity by an electric motor. The number of revolutions (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by the control signal output from the control device 60 shown in FIG.
  • the inlet side of the refrigerant passage of the water refrigerant heat exchanger 12 is connected to the discharge port of the compressor 11.
  • the water-refrigerant heat exchanger 12 has a refrigerant passage for circulating the high-pressure refrigerant discharged from the compressor 11 and a water passage for circulating the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40.
  • the water refrigerant heat exchanger 12 is a heat exchanger for heating that heats the high temperature side heat medium by exchanging heat between the high pressure refrigerant flowing through the refrigerant passage and the high temperature side heat medium flowing through the water passage.
  • the inlet side of the first joint 13a having three inflow outlets communicating with each other is connected to the outlet of the refrigerant passage of the water refrigerant heat exchanger 12.
  • 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 device 10 includes second to fourth joints 13b to 13d.
  • the third joint 13c is a three-way joint similar to the first joint 13a.
  • the second joint 13b and the fourth joint 13d are four-sided joints having four inflow ports communicating with each other.
  • the inlet side of the heating expansion valve 14a is connected to one of the outlets of the first joint 13a.
  • One inlet side of the second joint 13b is connected to the other outlet of the first joint 13a via a bypass passage 22a.
  • a dehumidifying on-off valve 15a is arranged in the bypass passage 22a.
  • the dehumidifying on-off valve 15a is a solenoid valve that opens and closes the bypass passage 22a.
  • the refrigeration cycle device 10 includes a heating on-off valve 15b.
  • the basic configuration of the heating on-off valve 15b is the same as that of the dehumidifying on-off valve 15a.
  • the dehumidifying on-off valve 15a and the heating on-off valve 15b can switch the refrigerant circuit of each operation mode by opening and closing the refrigerant passage.
  • the dehumidifying on-off valve 15a and the heating on-off valve 15b are refrigerant circuit switching units that switch the refrigerant circuit of the cycle.
  • the dehumidifying on-off valve 15a and the heating on-off valve 15b are controlled by a control voltage output from the control device 60.
  • the heating expansion valve 14a reduces the pressure of the high-pressure refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12 at least in the operation mode of heating the vehicle interior, and reduces the flow rate (mass flow rate) of the refrigerant flowing out to the downstream side. It is a decompression unit for heating to be adjusted.
  • the heating expansion valve 14a is an electric type having a valve body configured to change the throttle opening degree and an electric actuator (in other words, an electric mechanism) for changing the opening degree of the valve body.
  • Variable throttle mechanism in other words, an electric expansion valve).
  • the refrigeration cycle device 10 includes a cooling expansion valve 14b and an endothermic expansion valve 14c.
  • the basic configuration of the cooling expansion valve 14b and the endothermic expansion valve 14c is the same as that of the heating expansion valve 14a.
  • the expansion valve 14a for heating, the expansion valve 14b for cooling, and the expansion valve 14c for endothermic function have a fully open function that functions as a mere refrigerant passage without exerting a flow rate adjusting action and a refrigerant depressurizing action by fully opening the valve opening. It also has a fully closed function that closes the refrigerant passage by fully closing the valve opening.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the endothermic expansion valve 14c can switch the refrigerant circuit in each operation mode.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the endothermic expansion valve 14c function as a refrigerant circuit switching unit.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the endothermic expansion valve 14c are 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 from 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 unit room. Therefore, when the vehicle is running, the running wind can be applied to the outdoor heat exchanger 16.
  • the inlet side of the third joint 13c is connected to the refrigerant outlet of the outdoor heat exchanger 16.
  • the first inlet side of the fourth joint 13d is connected to one outlet of the third joint 13c via the heating passage 22b.
  • a heating on-off valve 15b for opening and closing the refrigerant passage is arranged in the heating passage 22b.
  • a first check valve 17a is arranged in the heating passage 22b. The first check valve 17a allows the refrigerant to flow from the third joint 13c side to the fourth joint 13d side, and prohibits the refrigerant from flowing from the fourth joint 13d side to the third joint 13c side.
  • the other inlet side of the second joint 13b is connected to the other outlet of the third joint 13c.
  • a second check valve 17b is arranged in a refrigerant passage connecting the other outlet side of the third joint 13c and the other inlet side of the second joint 13b.
  • the second check valve 17b allows the refrigerant to flow from the third joint 13c side to the second joint 13b side, and prohibits the refrigerant from flowing from the second joint 13b side to the third joint 13c side.
  • the inlet side of the cooling expansion valve 14b is connected to one of the outlets of the second joint 13b.
  • the inlet side of the endothermic expansion valve 14c is connected to the other outlet of the second joint 13b.
  • the cooling expansion valve 14b is an air-conditioning decompression unit that depressurizes the refrigerant flowing out from the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant flowing out to the downstream side at least in the operation mode for cooling the vehicle interior.
  • 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 the air conditioning case 31 of the indoor air conditioning unit 30.
  • the indoor evaporator 18 exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 14b and the air blown from the blower 32 to evaporate the low-pressure refrigerant, and causes the low-pressure refrigerant to exert a heat absorbing action to absorb air. It is an air conditioning evaporative unit that cools.
  • the indoor evaporator 18 is the first evaporation unit.
  • the second inflow port side of the fourth joint 13d is connected to the refrigerant outlet of the indoor evaporator 18.
  • a third check valve 17c is arranged in the refrigerant passage connecting the refrigerant outlet side of the indoor evaporator 18 and the second inlet side of the fourth joint 13d.
  • the third check valve 17c allows the refrigerant to flow from the indoor evaporator 18 side to the fourth joint 13d side, and prohibits the refrigerant from flowing from the fourth joint 13d side to the indoor evaporator 18 side.
  • the endothermic expansion valve 14c is an endothermic decompression unit that reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant flowing out to the downstream side in the operation mode in which heat is absorbed from the waste heat device 80. ..
  • the inlet side of the refrigerant passage of the chiller 19 is connected to the outlet of the endothermic expansion valve 14c.
  • the chiller 19 has a refrigerant passage for circulating a low-pressure refrigerant decompressed by the heat absorption expansion valve 14c, and a water passage for circulating a low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50.
  • the chiller 19 is an evaporation unit that exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage and the low-temperature side heat medium flowing through the water passage to evaporate the low-pressure refrigerant and exert a heat absorbing action.
  • the third inflow port side of the fourth joint 13d is connected to the outlet of the refrigerant passage of the chiller 19.
  • the indoor evaporator 18 and the chiller 19 are connected in parallel to each other with respect to the refrigerant flow.
  • the inlet side of the accumulator 21 is connected to the outlet of the fourth joint 13d.
  • the accumulator 21 is a gas-liquid separation unit that separates the gas-liquid of the refrigerant that has flowed into the inside and stores the excess liquid-phase refrigerant in the cycle.
  • the suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 21.
  • the accumulator 21 is formed with an oil return hole for returning the refrigerating machine oil mixed in the separated liquid phase refrigerant to the compressor 11.
  • the refrigerating machine oil in the accumulator 21 is returned to the compressor 11 together with a small amount of liquid phase refrigerant.
  • the high temperature side heat medium circuit 40 is a heat medium circulation circuit that circulates the high temperature side heat medium.
  • a solution containing ethylene glycol, dimethylpolysiloxane, a nanofluid, or the like, an antifreeze solution, or the like can be adopted.
  • a water passage of the water refrigerant heat exchanger 12 a high temperature side heat medium pump 41, a heater core 42, an electric heater 43, and the like are arranged.
  • the high temperature side heat medium pump 41 is a water pump that pumps the high temperature side 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 heat medium inlet side of the heater core 42 is connected to the outlet of the water passage of the water refrigerant heat exchanger 12.
  • the heater core 42 is a heat exchanger that heats the air by exchanging heat between the high temperature side heat medium heated by the water refrigerant heat exchanger 12 and the air that has passed through the indoor evaporator 18.
  • the heater core 42 is arranged in the air conditioning case 31 of the indoor air conditioning unit 30.
  • the suction port side of the high temperature side heat medium pump 41 is connected to the heat medium outlet of the heater core 42.
  • the high temperature side heat medium pump 41 adjusts the flow rate of the high temperature side heat medium flowing into the heater core 42 to dissipate heat of the high temperature side heat medium in the heater core 42 to the air (that is, that is). , The amount of heat of air in the heater core 42) can be adjusted.
  • the water-refrigerant heat exchanger 12, the high-temperature side heat medium circuit 40, and the heater core 42 are heating units that heat air using the refrigerant discharged from the compressor 11 as a heat source.
  • the electric heater 43 is, for example, a PTC heater having a PTC element (that is, a positive characteristic thermistor).
  • the electric heater 43 can arbitrarily adjust the amount of heat for heating the high temperature side heat medium by the control voltage output from the control device 60.
  • the low temperature side heat medium circuit 50 is a heat medium circulation circuit that circulates the low temperature side heat medium.
  • the low temperature side heat medium the same fluid as the high temperature side heat medium can be adopted.
  • a water passage of a chiller 19 a low temperature side heat medium pump 51, a waste heat device 80, and the like are arranged.
  • the low temperature side heat medium pump 51 is a water pump that pumps the low temperature side heat medium to the inlet side of the water passage of the chiller 19.
  • the basic configuration of the low temperature side heat medium pump 51 is the same as that of the high temperature side heat medium pump 41.
  • the inlet side of the waste heat device 80 is connected to the discharge port of the low temperature side heat medium pump 51.
  • the waste heat device 80 is provided with a heat medium flow path through which the low temperature side heat medium flows.
  • the waste heat device 80 is an in-vehicle device that generates waste heat as it operates.
  • the waste heat device 80 is, for example, an inverter, a motor generator, a power control unit, or the like, which generates waste heat as the vehicle travels.
  • the waste heat device 80 may be a secondary battery for storing electric power supplied to an in-vehicle device such as an electric motor.
  • the inlet side of the water passage of the chiller 19 is connected to the heat medium outlet of the waste heat apparatus 80.
  • the suction port side of the low temperature side heat medium pump 51 is connected to the outlet of the water passage of the chiller 19.
  • the low temperature side heat medium circuit 50 may be provided with a low temperature side radiator that dissipates heat from the low temperature side heat medium to the outside air.
  • the low temperature side heat medium pump 51 adjusts the flow rate of the low temperature side heat medium flowing into the waste heat device 80 to adjust the amount of heat absorbed by the low temperature side heat medium from the waste heat device 80. can do.
  • the chiller 19 and the low temperature side heat medium circuit 50 are endothermic portions that evaporate the refrigerant flowing out from the endothermic expansion valve 14c and absorb heat from the waste heat apparatus 80.
  • the waste heat device 80 and the low temperature side heat medium are endothermic objects that are endothermic by the refrigerant flowing through the chiller 19.
  • the indoor air conditioning unit 30 blows out 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 front of the vehicle interior.
  • the indoor air conditioning unit 30 houses a blower 32, an indoor evaporator 18, a heater core 42, and the like in an air passage formed in an air conditioning case 31 forming an outer shell thereof.
  • the air conditioning case 31 forms an air passage for air to be blown into the vehicle interior.
  • the air-conditioning case 31 is made of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.
  • An inside / outside air switching device 33 is arranged on the most upstream side of the air flow of the air conditioning case 31.
  • the inside / outside air switching device 33 switches and introduces the inside air (that is, the vehicle interior air) and the outside air (that is, the vehicle interior outside air) into the air conditioning case 31.
  • the inside / outside air switching device 33 continuously adjusts the opening areas 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 introduction air volume of the inside air and the outside air. Change the introduction ratio with the introduction air volume.
  • the inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door.
  • the electric actuator for the inside / outside air switching door is controlled by a control signal output from the control device 60.
  • a blower 32 is arranged on the downstream side of the air flow of the inside / outside air switching device 33.
  • the blower 32 blows the air sucked 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 air flow.
  • the indoor evaporator 18 is arranged on the upstream side of the air flow with respect to the heater core 42.
  • the air conditioning case 31 is provided with a cold air bypass passage 35 that allows air 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 air flow of the indoor evaporator 18 in the air conditioning case 31 and on the upstream side of the air flow of the heater core 42.
  • the air mix door 34 is an air volume ratio adjusting unit that adjusts the air volume ratio between the air volume of the air passing through the heater core 42 side and the air volume of the air passing through the cold air bypass passage 35 among the air after passing through the indoor evaporator 18. ..
  • the air mix door 34 is driven by an electric actuator for the air mix door. This electric actuator is controlled by a control signal output from the control device 60.
  • a mixing space is arranged on the downstream side of the air flow of the heater core 42 and the cold air bypass passage 35 in the air conditioning case 31.
  • the mixing space is a space in which the air heated by the heater core 42 and the unheated air passing through the cold air bypass passage 35 are mixed.
  • an opening hole for blowing out the air mixed in the mixing space (that is, the air conditioning air) into the vehicle interior, which is the air conditioning target space, is arranged.
  • the face opening hole is an opening hole for blowing air-conditioned air toward the upper body of the occupant in the vehicle interior.
  • the foot opening hole is an opening hole for blowing air-conditioned air toward the feet of the occupant.
  • the defroster opening hole is an opening hole for blowing air conditioning air toward the inner side surface of the front window glass of the vehicle.
  • These face opening holes, foot opening holes, and defroster opening holes are the face outlets, foot outlets, and defroster outlets (none of which are shown) provided in the vehicle interior via ducts forming air passages, respectively. )It is connected to the.
  • the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air volume ratio between the air volume passing through the heater core 42 and the air volume passing through the cold air bypass passage 35 by the air mix door 34. As a result, the temperature of the air (air-conditioned air) blown from each outlet into the vehicle interior is adjusted.
  • Face doors, foot doors, and defroster doors are arranged on the upstream side of the air flow of the face opening hole, the foot opening hole, and the defroster opening hole, respectively.
  • the face door adjusts the opening area of the face opening hole.
  • the foot door adjusts the opening area of the foot opening hole.
  • the defroster door adjusts the opening area of the defroster opening hole.
  • These face doors, foot doors, and defroster doors constitute an outlet mode switching device that switches the outlet mode.
  • These doors are connected to an electric actuator for driving the outlet mode door via a link mechanism or the like, and are rotated in conjunction with each other. The operation of this electric actuator is also controlled by a control signal output from the control device 60.
  • the face mode is an outlet mode in which the face outlet is fully opened and air is blown out from the face outlet toward the upper body of the passenger in the passenger compartment.
  • the bi-level mode is an outlet mode in which both the face outlet and the foot outlet are opened to blow air toward the upper body and feet of the passengers in the passenger compartment.
  • 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 occupant can also switch to the defroster mode by manually operating the blowout mode changeover switch provided on the operation panel 70 shown in FIG.
  • 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 front window glass.
  • the control device 60 includes a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof. Then, various operations and processes are performed based on the control program stored in the ROM, and various controlled devices 11, 14a to 14c, 15a to 15b, 32, 41, 51 and the like connected to the output side are operated. To control.
  • a first refrigerant pressure sensor 65a, a second refrigerant pressure sensor 65b, a high temperature side heat medium temperature sensor 66a, a first low temperature side heat medium temperature sensor 67a, a second low temperature side heat medium temperature sensor 67b, and the like are connected. Then, the detection signals of these sensor groups are input to the control device 60.
  • the internal air temperature sensor 61 is an internal air temperature detection unit that detects the internal air temperature Tr (that is, the vehicle interior temperature).
  • the outside air temperature sensor 62 is an outside air temperature detection unit that detects the outside air temperature Tam (that is, the outside air temperature of the vehicle interior).
  • the solar radiation sensor 63 is a solar radiation amount detection unit that detects the solar radiation amount As irradiated to the vehicle interior.
  • the first refrigerant temperature sensor 64a is a discharge refrigerant temperature detection unit that detects the temperature T1 of the refrigerant discharged from the compressor 11.
  • the second refrigerant temperature sensor 64b is a second refrigerant temperature detecting unit that detects the temperature T2 of the refrigerant flowing out from 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 detection unit that detects the temperature T4 of the refrigerant flowing out from the indoor evaporator 18.
  • the fifth refrigerant temperature sensor 64e is a fifth refrigerant temperature detection unit that detects the temperature T5 of the refrigerant flowing out from the refrigerant passage of the chiller 19.
  • the evaporator temperature sensor 64f is an evaporator temperature detection unit that detects the evaporator temperature Tefien, which is the refrigerant evaporation temperature in the indoor evaporator 18.
  • the evaporator temperature sensor 64f of the present embodiment detects the heat exchange fin temperature of the indoor evaporator 18.
  • the first refrigerant pressure sensor 65a is a first refrigerant pressure detecting unit that detects the pressure P1 of the refrigerant flowing out from the refrigerant passage of the water refrigerant heat exchanger 12.
  • the second refrigerant pressure sensor 65b is a second refrigerant pressure detecting unit that detects the pressure P2 of the refrigerant flowing out from the refrigerant passage of the chiller 19.
  • the high temperature side heat medium temperature sensor 66a is a high temperature side heat medium temperature detection unit that detects the high temperature side heat medium temperature TWH, which is the temperature of the high temperature side heat medium flowing out from the water passage of the water refrigerant heat exchanger 12.
  • the first low temperature side heat medium temperature sensor 67a is a first low temperature side heat medium temperature detection unit that detects the first low temperature side heat medium temperature TWL1, which is the temperature of the low temperature side heat medium flowing out from the water passage of the chiller 19.
  • the second low temperature side heat medium temperature sensor 67b is a second low temperature side heat medium temperature detection unit that detects the second low temperature side heat medium temperature TWL2 which is the temperature of the low temperature side heat medium flowing out from the waste heat apparatus 80.
  • an operation panel 70 arranged near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device 60, and operation signals from various operation switches provided on the operation panel 70 are connected. Is entered.
  • the various operation switches provided on the operation panel 70 include an auto switch that sets or cancels the automatic control operation of the vehicle air conditioner, an air conditioner switch that requires the indoor evaporator 18 to cool the air, and the like.
  • the control device 60 of the present embodiment is integrally configured with a control unit that controls various controlled devices connected to the output side of the control device 60.
  • the configuration (hardware and software) that controls the operation of each of the control target devices in the control device 60 is a control unit that controls the operation of each control target device.
  • the configuration for controlling the refrigerant discharge capacity of the compressor 11 (specifically, the rotation speed of the compressor 11) is the compressor control unit 60a.
  • the configuration for controlling the operation of the heating expansion valve 14a, the cooling expansion valve 14b, and the endothermic expansion valve 14c is the expansion valve control unit 60b.
  • the configuration that controls the operation of the dehumidifying on-off valve 15a and the heating on-off valve 15b is the refrigerant circuit switching control unit 60c.
  • the configuration for controlling the pumping capacity of the high temperature side heat medium of the high temperature side heat medium pump 41 is the high temperature side heat medium pump control unit 60d.
  • the configuration for controlling the pumping capacity of the low temperature side heat medium of the low temperature side heat medium pump 51 is the low temperature side heat medium pump control unit 60e.
  • the refrigerant circuit can be switched to perform air conditioning operation in the following five operation modes.
  • Cooling mode is an operation mode in which the interior of the vehicle is cooled by cooling the air and blowing it into the interior of the vehicle.
  • the outside air heating mode is an operation mode in which the inside of the vehicle is heated by heating the air using the heat absorbed from the outside air and blowing it into the vehicle interior.
  • outside air waste heat heating mode In the outside air waste heat heating mode, the air is heated by using the heat absorbed from the outside air and the waste heat absorbed from the waste heat device 80 and blown into the vehicle interior. This is an operation mode for heating.
  • Waste heat heating mode is an operation mode in which the inside of the vehicle is heated by heating the air using the waste heat absorbed from the waste heat device 80 and blowing it into the vehicle interior.
  • Waste heat heating mode during frost formation In the waste heat heating mode during frost formation, the air is heated by using the waste heat absorbed from the waste heat device 80 when the outdoor heat exchanger 16 is frosted and cannot be used. This is an operation mode in which the interior of the vehicle is heated by blowing it into the interior of the vehicle.
  • the control program is executed when the ignition switch of the vehicle is turned on (ON).
  • TAO Kset x Tset-Kr x Tr-Kam x Tam-Ks x As + C ... (F1)
  • Tset is the vehicle interior set temperature set by the temperature setting switch. Tr is the vehicle interior temperature detected by the internal air temperature sensor 61. Tam is the outside temperature of the vehicle interior detected by the outside air temperature sensor 62. As 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 outside air temperature Tam is less than the heating reference temperature Tht, or when the air conditioner switch is not turned on (OFF), one of the outside air heating mode, the outside air waste heat heating mode, and the waste heat heating mode is selected. To.
  • the intake refrigerant temperature Ts, the outside temperature Tam, and the second low temperature side heat medium temperature are selected.
  • TWL2 the outside air heating mode, the outside air waste heat heating mode, and the waste heat heating mode are switched.
  • frost is formed on the outdoor heat exchanger 16 in the outside air heating mode, the outside air waste heat heating mode, and the waste heat heating mode, the mode is switched to the waste heat heating mode at the time of frost formation.
  • the suction refrigerant temperature Ts is the temperature of the refrigerant sucked into the compressor 11.
  • the refrigerant saturation temperature calculated from the refrigerant pressure P2 that is, the pressure of the refrigerant flowing out from the refrigerant passage of the chiller 19
  • the second refrigerant pressure sensor 65b is used as the suction refrigerant temperature Ts.
  • the temperature T3 of the refrigerant detected by the third refrigerant temperature sensor 64c (that is, the temperature of the refrigerant flowing out from the outdoor heat exchanger 16) and the temperature T5 of the refrigerant detected by the fifth refrigerant temperature sensor 64e (that is, the temperature of the refrigerant flowing out from the outdoor heat exchanger 16). That is, the lower temperature of the temperature of the refrigerant flowing out from the refrigerant passage of the chiller 19) may be used.
  • the second low temperature side heat medium temperature TWL2 is the temperature of the low temperature side heat medium flowing out from the waste heat apparatus 80.
  • the state in which the temperature difference (outside air refrigerant temperature difference) obtained by subtracting the intake refrigerant temperature Ts from the outside air temperature Tam is equal to or more than the heat-absorbable temperature difference ⁇ 1 continues for the first duration t1 or more, and is the first. 2
  • the mode shifts to the outside air waste heat heating mode.
  • the endothermic temperature difference ⁇ 1 is about 0 to 10 ° C (for example, 5 ° C).
  • the first duration t1 is about 0 to 60 seconds (for example, 30 seconds).
  • the values of the endothermic temperature difference ⁇ 1 and the first duration t1 are the values experimentally obtained as the endothermic temperature difference and time that can be reliably absorbed from the outside air by the outdoor heat exchanger 16.
  • the first predetermined temperature difference ⁇ 1 is about 0 to 5 ° C.
  • the value of the first predetermined temperature difference ⁇ 1 is a value experimentally obtained as a temperature difference capable of reliably absorbing heat from the low temperature side heat medium in the chiller 19.
  • the endothermic temperature TW1 is the larger of the value obtained by adding the second predetermined temperature difference ⁇ 2 to the outside air temperature Tam and the value obtained by adding the third predetermined temperature difference ⁇ 3 to the endothermic lower limit temperature TWmin. That is, the endothermic temperature TW1 is determined using the following mathematical formula F2.
  • TW1 MAX [Tam + ⁇ 2, TWmin + ⁇ 3] ... (F2)
  • the second predetermined temperature difference ⁇ 2 is about 0 to 10 ° C (for example, 5 ° C).
  • the third predetermined temperature difference ⁇ 3 is about 0 to 10 ° C (for example, 5 ° C).
  • the values of the second predetermined temperature difference ⁇ 2 and the third predetermined temperature difference ⁇ 3 are the values experimentally obtained as the temperature difference in which the low temperature side heat medium can be used as the heat source for heating.
  • the endothermic lower limit temperature TWmin is a temperature set from the viewpoint of preventing dew condensation on the waste heat device 80 and from the device characteristics, and is basically set to a temperature equal to or higher than the outside air temperature.
  • the state in which the temperature difference obtained by subtracting the intake refrigerant temperature Ts from the outside air temperature Tam is the lower limit temperature difference ⁇ 2 or less continues for the second duration t2 or more, and the second low temperature side heat medium.
  • the temperature TWL2 is equal to or higher than the heat absorbing temperature TW1, the mode shifts to the waste heat heating mode.
  • the lower limit temperature difference ⁇ 2 is about 0 to 4 ° C (for example, 2 ° C).
  • the second duration t2 is about 0 to 60 seconds (for example, 30 seconds).
  • the lower limit temperature difference ⁇ 2 and the second duration t2 are values experimentally obtained as the temperature difference and time at which it becomes difficult for the outdoor heat exchanger 16 to absorb heat from the outside air.
  • the lower limit temperature difference ⁇ 2 is set to a value smaller than the endothermic temperature difference ⁇ 1.
  • the outside air waste heat heating mode when the temperature difference obtained by subtracting the intake refrigerant temperature Ts from the outside air temperature Tam is the endothermic temperature difference ⁇ 1 or more for the first duration t1 or more, the outside air waste heat heating mode is set. Transition.
  • the mode shifts to the outside air heating mode.
  • the state in which the temperature difference obtained by subtracting the intake refrigerant temperature Ts from the outside air temperature Tam is the lower limit temperature difference ⁇ 2 or less continues for the second duration t2 or more, and the second low temperature side heat medium.
  • the mode shifts to the outside air heating mode.
  • the mode shifts to the outside air heating mode.
  • frost occurs on the outdoor heat exchanger 16 in any of the outside air heating mode, the outside air waste heat heating mode, and the waste heat heating mode, the mode shifts to the waste heat heating mode at the time of frost formation. For example, when the intake refrigerant temperature Ts is lower than the outside air temperature Tam by a predetermined value or more for a predetermined time or longer, it is determined that frost has formed on the outdoor heat exchanger 16.
  • the mode shifts to one of the outside air heating mode, the outside air waste heat heating mode, and the waste heat heating mode. For example, it shifts to the operation mode that was executed immediately before shifting to the waste heat heating mode at the time of frost formation. For example, when the suction refrigerant temperature Ts continues to be at or above the frosting temperature (for example, 0 ° C.) for a predetermined time or longer, it is determined that frosting has not occurred in the outdoor heat exchanger 16.
  • the frosting temperature for example, 0 ° C.
  • control device 60 executes the control flow of each operation mode.
  • Cooling mode In the control flow of the cooling mode, the rotation speed of 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 64f, by a feedback control method. , The evaporator temperature Tefin is determined to approach the target evaporator temperature TEO.
  • the target evaporator temperature TEO is determined based on the target blowout temperature TAO with reference to the control map stored in the control device 60. In the control map of the present embodiment, it is determined that the target evaporator temperature TEO increases as the target blowout temperature TAO increases.
  • the throttle opening of the cooling expansion valve 14b is based on the deviation between the target supercooling degree SCO1 and the supercooling degree SC1 of the outlet side refrigerant of the outdoor heat exchanger 16 by the feedback control method.
  • the supercooling degree SC1 of the outlet side refrigerant of the outdoor heat exchanger 16 is determined to approach the target supercooling degree SCO1.
  • the target supercooling degree SCO1 is determined with reference to the control map, for example, based on the outside air temperature Tam.
  • the target supercooling degree SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • the degree of supercooling SC1 of the outlet side refrigerant of the outdoor heat exchanger 16 is calculated based on the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P1 detected by the first refrigerant pressure sensor 65a.
  • the opening SW of the air mix door 34 is calculated using the following mathematical formula F3.
  • SW ⁇ TAO- (Tefin + C2) ⁇ / ⁇ TWH- (Tefin + C2) ⁇ ...
  • the TWH is the high temperature side heat medium temperature detected by the high temperature side heat medium temperature sensor 66a.
  • C2 is a constant for control.
  • the expansion valve 14a for heating is set to the fully open state
  • the expansion valve 14b for cooling is set to the throttle state to exert the refrigerant depressurizing action, and endothermic.
  • the expansion valve 14c is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed.
  • the compressor 11 the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the second check valve 17b, the cooling expansion valve 14b, and the indoor evaporator
  • a steam compression type refrigeration cycle in which the refrigerant circulates in the order of 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
  • the water refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator (in other words, a radiator) for dissipating the refrigerant discharged from the compressor 11 for cooling.
  • a steam compression type refrigeration cycle is configured in which the expansion valve 14b functions as a pressure reducing unit for reducing the pressure of the refrigerant, and the indoor evaporator 18 functions as an evaporator.
  • the 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 cooling mode a part of the air cooled by the indoor evaporator 18 is reheated by the heater core 42 by adjusting the opening degree of the air mix door 34, and approaches the target blowout temperature TAO.
  • TAO target blowout temperature
  • the rotation speed of the compressor 11 is on the high temperature side by the feedback control method based on the deviation between the target high temperature side heat medium temperature TWHO and the high temperature side heat medium temperature TWH.
  • the heat medium temperature TWH is determined to approach the target high temperature side heat medium temperature TWHO.
  • the target high temperature side heat medium temperature TWHO is determined with reference to the control map based on the target blowout temperature TAO and the efficiency of the heater core 42. In the control map of the present embodiment, it is determined that the target high temperature side heat medium temperature TWHO increases as the target blowout temperature TAO increases.
  • the throttle opening of the heating expansion valve 14a is a feedback control method based on the deviation between the target supercooling degree SCO2 and the supercooling degree SC2 of the outlet side refrigerant of the water refrigerant heat exchanger 12. Therefore, the supercooling degree SC2 is determined to approach the target supercooling degree SCO2.
  • the target supercooling degree SCO2 is determined with reference to the control map, for example, based on the outside air temperature Tam.
  • the target supercooling degree SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • the degree of supercooling SC2 of the outlet side refrigerant of the water refrigerant heat exchanger 12 is calculated based on the temperature T2 detected by the second refrigerant temperature sensor 64b and the pressure P1 detected by the first refrigerant pressure sensor 65a.
  • the endothermic expansion valve 14c In the control flow of the outside air heating mode, the endothermic expansion valve 14c is fully closed, and the opening SW of the air mix door 34 is calculated in the same manner as in the cooling mode.
  • the target outlet temperature TAO becomes high, so that the opening SW of the air mix door 34 approaches 100%. Therefore, in the outside air heating mode, the opening degree of the air mix door 34 is determined so that almost the entire flow rate of the air after passing through the indoor evaporator 18 passes through the heater core 42.
  • the heating expansion valve 14a In the control flow of the outside air heating mode, in order to switch the refrigerating cycle device 10 to the refrigerant circuit of the outside air heating mode, the heating expansion valve 14a is set to the throttled state, the cooling expansion valve 14b is set to the fully closed state, and the endothermic expansion valve 14c is set. Is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is opened.
  • 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 are used in this order.
  • a circulating steam compression refrigeration cycle is constructed.
  • the water refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) that dissipates heat from the refrigerant discharged from the compressor 11, and the heating expansion valve 14a decompresses.
  • a refrigeration cycle is configured in which the outdoor heat exchanger 16 functions as an evaporator, which functions as a unit.
  • heat can be absorbed from the outside air by the outdoor heat exchanger 16 and the high temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the outside air heating mode, the interior of the vehicle can be heated by blowing out the air heated by the heater core 42 into the interior of the vehicle.
  • the throttle opening of the endothermic expansion valve 14c is based on the deviation between the target superheat degree SHCO and the superheat degree SHC of the outlet side refrigerant of the chiller 19, and the degree of superheat is determined by the feedback control method.
  • the SHC is determined to approach the target superheat degree SHCO.
  • a predetermined constant 5 ° C. in this embodiment
  • the degree of superheat SHC of the outlet side refrigerant of the chiller 19 is calculated based on the temperature T5 detected by the fifth refrigerant temperature sensor 64e and the pressure P2 detected by the second refrigerant pressure sensor 65b.
  • the throttle opening of the heat absorption expansion valve 14c is the second by the feedback control method based on the deviation between the target low temperature side heat medium temperature TWLO and the second low temperature side heat medium temperature TWL2.
  • the low temperature side heat medium temperature TWL2 is determined so as not to fall below the target low temperature side heat medium temperature TWLO.
  • the throttle opening of the heat absorption expansion valve 14c is reduced to reduce the flow rate of the refrigerant in the chiller 19. Thereby, the amount of heat absorbed from the low temperature side heat medium in the chiller 19 is reduced to suppress the decrease in the second low temperature side heat medium temperature TWL2.
  • the suction refrigerant temperature Ts is set to the outside air temperature by the feedback control method based on the deviation between the outside air temperature Tam and the intake refrigerant temperature Ts in the throttle opening of the endothermic expansion valve 14c. It is decided not to exceed Tam. Specifically, when the suction refrigerant temperature Ts is about to exceed the outside temperature Tam, the throttle opening of the heat absorption expansion valve 14c is reduced to reduce the refrigerant flow rate in the chiller 19, thereby reducing the low temperature side in the chiller 19. The amount of heat absorbed from the heat medium is reduced to suppress an increase in the intake refrigerant temperature Ts.
  • the heating expansion valve 14a In the control flow of the outside air waste heat heating mode, in order to switch the refrigeration cycle device 10 to the refrigerant circuit of the outside air waste heat heating mode, the heating expansion valve 14a is set to the throttled state, the cooling expansion valve 14b is set to the fully closed state, and heat absorption is performed.
  • the expansion valve 14c is set to the throttled state, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened.
  • 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 are in this order.
  • a steam compression type refrigeration cycle in which the refrigerant circulates in the order of the compressor 11, the water refrigerant heat exchanger 12, the bypass passage 22a, the heat absorption expansion valve 14c, the chiller 19, the accumulator 21, and the compressor 11 is configured. Will be done.
  • the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a radiator) that dissipates the refrigerant discharged from the compressor 11, and the heating expansion valve 14a
  • a refrigeration cycle is configured in which the heat absorption expansion valve 14c functions as a pressure reducing unit, and the outdoor heat exchanger 16 and the chiller 19 function as an evaporator.
  • the outdoor heat exchanger 16 absorbs heat from the outside air
  • the chiller 19 absorbs heat from the waste heat device 80 via the low temperature side heat medium
  • the water refrigerant heat exchanger 12 heats the high temperature side heat medium. can do. Therefore, in the vehicle air conditioner 1 in the outside air waste heat heating mode, the interior of the vehicle can be heated by blowing out the air heated by the heater core 42 into the interior of the vehicle.
  • Waste heat heating mode In the control flow of the waste heat heating mode, the rotation speed of the compressor 11 and the opening SW of the air mix door 34 are determined as in the outside air heating mode. In the control flow of the waste heat heating mode, the heating expansion valve 14a is fully closed.
  • the throttle opening of the heat absorption expansion valve 14c is feedback controlled based on the deviation between the target supercooling degree SCO2 and the supercooling degree SC2 of the outlet side refrigerant of the water refrigerant heat exchanger 12. The method determines that the supercooling degree SC2 approaches the target supercooling degree SCO2.
  • the target supercooling degree SCO2 is determined with reference to the control map, for example, based on the outside air temperature Tam.
  • the target supercooling degree SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • the degree of supercooling SC2 of the outlet side refrigerant of the water refrigerant heat exchanger 12 is calculated based on the temperature T2 detected by the second refrigerant temperature sensor 64b and the pressure P1 detected by the first refrigerant pressure sensor 65a.
  • the heating expansion valve 14a and the cooling expansion valve 14b are fully closed, and the endothermic expansion valve 14c is throttled. In this state, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is closed.
  • the water-refrigerant heat exchanger 12 functions as a radiator (in other words, a heat dissipation unit) that dissipates heat from the refrigerant discharged from the compressor 11, and the endothermic expansion valve 14c is used.
  • a refrigeration cycle is configured in which the chiller 19 functions as a decompressor and an evaporator.
  • the chiller 19 can absorb heat from the waste heat device 80 via the low temperature side heat medium, and the water refrigerant heat exchanger 12 can heat the high temperature side heat medium. Therefore, in the vehicle air conditioner 1 in the waste heat heating mode, the interior of the vehicle can be heated by blowing out the air heated by the heater core 42 into the interior of the vehicle.
  • Waste heat heating mode during frost formation In the control flow of the waste heat heating mode during frost formation, the throttle opening of the endothermic expansion valve 14c and the opening SW of the air mix door 34 are determined as in the waste heat heating mode. Will be done. In the control flow of the waste heat heating mode at the time of frost formation, the heating expansion valve 14a is fully closed as in the waste heat heating mode.
  • the rotation speed of the compressor 11 is basically determined in the same manner as in the waste heat heating mode. However, in the control flow of the waste heat heating mode at the time of frost formation, the rotation speed of the compressor 11 is determined so that the second low temperature side heat medium temperature TWL2 does not fall below the endothermic lower limit temperature TWmin. Specifically, when the second low temperature side heat medium temperature TWL2 is likely to fall below the endothermic lower limit temperature TWmin, the rotation speed of the compressor 11 is lowered. This is because if the second low temperature side heat medium temperature TWL2 falls below the endothermic lower limit temperature TWmin, the chiller 19 cannot absorb heat, the compressor 11 stops, and heating cannot be performed.
  • the refrigeration cycle device 10 In the control flow of the waste heat heating mode at the time of frost, the refrigeration cycle device 10 is switched to the same refrigerant circuit as the waste heat heating mode.
  • the interior of the vehicle can be heated while maintaining the state where the chiller 19 can absorb heat from the low temperature side heat medium as much as possible.
  • dehumidifying and heating can be performed by setting the cooling expansion valve 14b to the throttled state.
  • the vehicle air conditioner 1 can realize comfortable air conditioning in the vehicle interior.
  • FIG. 4 is a Moriel diagram showing a change in the state of the refrigerant in the outside air waste heat heating mode of the present embodiment.
  • the refrigerant temperature in the outdoor heat exchanger 16 is lower than the outside air temperature
  • the refrigerant temperature in the chiller 19 is higher than the waste heat temperature (that is, the temperature of the low temperature side heat medium). If it is low, the heat can be absorbed from the outside air and the waste heat of the waste heat apparatus 80 can be absorbed for heating, so that the efficiency and performance of heating can be improved.
  • FIG. 5 is a Moriel diagram showing a change in the state of the refrigerant in the outside air waste heat heating mode of the comparative example.
  • the low pressure of the refrigeration cycle rises by absorbing the waste heat of the waste heat device 80 in the outside air waste heat heating mode, and the refrigerant temperature in the outdoor heat exchanger 16 becomes higher than the outside air temperature. Shows.
  • the outdoor heat exchanger 16 dissipates heat from the refrigerant to the outside air, resulting in deterioration of heating efficiency and performance.
  • the temperature difference obtained by subtracting the intake refrigerant temperature Ts from the outside air temperature Tam is the lower limit temperature difference ⁇ 2 or less, and the temperature TWL2 of the low temperature side heat medium absorbs heat. If the possible temperature is TW1 or higher, the mode is switched to the waste heat heating mode.
  • the temperature difference obtained by subtracting the intake refrigerant temperature Ts from the outside air temperature Tam is equal to or more than the heat absorbing temperature difference ⁇ 1, and the temperature TWL2 of the low temperature side heat medium is first predetermined to the heat absorbing temperature TW1. If the temperature difference is equal to or greater than the value obtained by adding ⁇ 1, the mode is switched to the outside air waste heat heating mode.
  • the mode in the waste heat heating mode, when the temperature difference obtained by subtracting the intake refrigerant temperature Ts from the outside air temperature Tam is equal to or more than the heat absorbing possible temperature difference ⁇ 1, the mode is switched to the outside air waste heat heating mode.
  • the heating efficiency and performance can be improved by switching to the outside air waste heat heating mode.
  • the mode in the waste heat heating mode, when the temperature TWL2 of the low temperature side heat medium is equal to or less than the endothermic lower limit temperature TWmin, the mode is switched to the outside air heating mode. As a result, the heating operation can be continued while suppressing the supercooling of the waste heat device 80.
  • the temperature difference obtained by subtracting the intake refrigerant temperature Ts from the outside temperature Tam is the lower limit temperature difference ⁇ 2 or less, and the temperature TWL2 of the low temperature side heat medium is less than the heat absorbing temperature difference ⁇ 1.
  • the mode is switched to the outside air heating mode.
  • the heat can be absorbed from the outside air as soon as possible by switching to the outside air heating mode.
  • the waste heat device 80 can switch to the outside air heating mode and continue the heating operation while suppressing supercooling.
  • the refrigerant discharge capacity of the compressor 11 is controlled so as to prevent the temperature TWL2 of the low temperature side heat medium from falling below the heat absorption lower limit temperature TWmin in the waste heat heating mode at the time of frost formation.
  • the opening degree of the heating expansion valve 14a in the outside air heating mode, is controlled based on the supercooling degree SC2 of the refrigerant flowing out from the water refrigerant heat exchanger 12.
  • the opening degree of the endothermic expansion valve 14c is controlled based on the supercooling degree SC2 of the refrigerant flowing out from the water refrigerant heat exchanger 12.
  • the opening degree of the heating expansion valve 14a is controlled based on the supercooling degree SC2 of the refrigerant flowing out from the water refrigerant heat exchanger 12, and based on the superheating degree SHC of the refrigerant flowing out from the chiller 19.
  • the opening degree of the heat absorption expansion valve 14c is controlled.
  • the opening degree of the heating expansion valve 14a and the opening degree of the heat absorption expansion valve 14c are appropriately controlled, and the outdoor heat exchanger 16 and the chiller are used.
  • the refrigerant pressure at 19 (in other words, the refrigerant temperature) can be appropriately controlled.
  • the opening degree of the heat absorption expansion valve 14c is controlled based on the supercooling degree SC2 of the refrigerant flowing out from the water refrigerant heat exchanger 12, and the evaporated refrigerant flowing out from the outdoor heat exchanger 16 is controlled.
  • the opening degree of the heating expansion valve 14a may be controlled based on the degree of superheat SHC.
  • the opening degree of the endothermic expansion valve 14c is controlled so that the temperature Ts of the refrigerant sucked into the compressor 11 does not exceed the outside air temperature Tam.
  • the frequency of switching between the outside air waste heat heating mode and the waste heat heating mode can be reduced, so that the fluctuation of the blowing temperature due to the mode switching can be reduced.
  • the opening degree of the endothermic expansion valve 14c is controlled so as to prevent the temperature TWL2 of the low temperature side heat medium from becoming the endothermic lower limit temperature TWmin or less.
  • the frequency of switching between the outside air waste heat heating mode and the outside air heating mode can be reduced, so that the fluctuation of the blowing temperature due to the mode switching can be reduced.
  • the refrigerating cycle device 10 of the first embodiment is an accumulator cycle including an accumulator 21, but the refrigerating cycle device 10 of the present embodiment is a receiver cycle including a receiver 25 instead of the accumulator 21 as shown in FIG. Is.
  • the inlet side of the three-way valve 15e is arranged at the discharge port of the compressor 11.
  • the three-way valve 15e is an electric three-way flow rate adjusting valve having one inlet and two outlets and capable of continuously adjusting the passage area ratio of the two outlets.
  • the three-way valve 15e is controlled by a control signal output from the control device 60.
  • the inlet side of the refrigerant passage of the water refrigerant heat exchanger 12 is connected to one of the outlets of the three-way valve 15e.
  • the first connection port side of the seventh joint 13g is connected to the other outlet of the three-way valve 15e via the first cooling passage 22c.
  • connection port side of the outdoor heat exchanger 16 is connected to the second connection port of the 7th joint 13g.
  • the first inflow port side of the fourth joint 13d is connected to the third connection port of the seventh joint 13g via the heating passage 22b.
  • a heating on-off valve 15b is arranged at a portion of the heating passage 22b between the 7th joint 13g and the 4th joint 13d.
  • One inflow port side of the eighth joint 13h is connected to the outlet of the refrigerant passage of the water refrigerant heat exchanger 12.
  • a fourth check valve 17d is arranged in the refrigerant passage connecting the outlet side of the refrigerant passage of the water refrigerant heat exchanger 12 and the one inlet side of the eighth joint 13h.
  • the fourth check valve 17d allows the refrigerant to flow from the water-refrigerant heat exchanger 12 side to the eighth joint 13h side, and prohibits the refrigerant from flowing from the eighth joint 13h side to the water-refrigerant heat exchanger 12 side. do.
  • the refrigerant inlet side of the receiver 25 is connected to the outlet of the 8th joint 13h.
  • the receiver 25 is a liquid storage unit having a gas-liquid separation function. That is, the receiver 25 separates the gas and liquid of the refrigerant flowing out from the heat exchange unit that functions as a condenser that condenses the refrigerant in the refrigeration cycle device 10. Then, the receiver 25 causes a part of the separated liquid phase refrigerant to flow out to the downstream side, and stores the remaining liquid phase refrigerant as the surplus refrigerant in the cycle.
  • the inlet side of the first joint 13a is connected to the refrigerant outlet of the receiver 25.
  • the inlet side of the heating expansion valve 14a is connected to one of the outlets of the first joint 13a.
  • the first connection port side of the ninth joint 13i is connected to the outlet of the heating expansion valve 14a.
  • the refrigerant inlet side of the outdoor heat exchanger 16 is connected to the second connection port of the ninth joint 13i.
  • the other inlet side of the eighth joint 13h is connected to the third connection port of the ninth joint 13i via the second cooling passage 22d.
  • a fifth check valve 17e is arranged in the second cooling passage 22d.
  • the fifth check valve 17e allows the refrigerant to flow from the ninth joint 13i side to the eighth joint 13h side, and prohibits the refrigerant from flowing from the eighth joint 13h side to the ninth joint 13i side.
  • the inlet side of the fifth joint 13e is connected to the other outlet of the first joint 13a via the bypass passage 22a.
  • the fifth joint 13e is a three-way joint similar to the first joint 13a.
  • the inlet side of the cooling expansion valve 14b is connected to one of the outlets of the fifth joint 13e.
  • the inlet side of the endothermic expansion valve 14c is connected to the other outlet of the fifth joint 13e.
  • the dehumidifying on-off valve 15a of the first embodiment is not arranged in the bypass passage 22a.
  • the refrigerating cycle device 10 is provided with first, third to fifth refrigerant temperature sensors 64a, 64c to 64e, and second to fifth refrigerant pressure sensors 65e.
  • the detection signal of these sensor groups is input to the control device 60.
  • the third refrigerant pressure sensor 65c is a third refrigerant pressure detecting unit that detects the pressure P3 of the refrigerant discharged from the compressor 11.
  • the fourth refrigerant pressure sensor 65d is a fourth refrigerant pressure detecting unit that detects the pressure P4 of the refrigerant flowing out from the outdoor heat exchanger 16.
  • the fifth refrigerant pressure sensor 65e is a fifth refrigerant pressure detecting unit that detects the pressure P5 of the refrigerant flowing out of the indoor evaporator 18.
  • the operation of the vehicle air conditioner of the present embodiment having the above configuration will be described.
  • the refrigeration cycle device 10 of the present embodiment there are five operation modes: cooling mode, outside air heating mode, outside air waste heat heating mode, waste heat heating mode, and waste heat heating mode at the time of frost formation. It is possible to perform air-conditioning operation in. The conditions for switching these operation modes are the same as those in the first embodiment.
  • control device 60 executes the control flow of each operation mode.
  • Cooling mode In the control flow of the cooling mode, the rotation speed of the compressor 11 and the opening degree SW of the air mix door 34 are determined as in the cooling mode of the first embodiment. In the control flow of the cooling mode, the endothermic expansion valve 14c is fully closed.
  • the throttle opening of the expansion valve 14b for cooling is based on the deviation between the target superheat degree SHEO and the superheat degree SHE of the outlet side refrigerant of the indoor evaporator 18, and the indoor evaporator is operated by a feedback control method.
  • the superheat degree SH of the outlet side refrigerant of 18 is determined to approach the target superheat degree SHEO.
  • the target superheat degree SHEO As the target superheat degree SHEO, a predetermined constant (5 ° C. in this embodiment) can be adopted.
  • the degree of superheat SHE of the outlet-side refrigerant of the indoor evaporator 18 is calculated based on the temperature T4 detected by the fourth refrigerant temperature sensor 64d and the pressure P5 detected by the fifth refrigerant pressure sensor 65e.
  • the control device 60 closes the heating on-off valve 15b, and the three-way valve 15e closes the outlet on the water refrigerant heat exchanger 12 side. Close and open the outlet on the 22c side of the first cooling passage. Further, the control device 60 puts the heating expansion valve 14a in a fully closed state, the cooling expansion valve 14b in a throttle state that exerts a refrigerant depressurizing action, and the endothermic expansion valve 14c in a fully closed state.
  • the refrigerating cycle device 10 in the cooling mode can cool the vehicle interior in the same manner as in the cooling mode of the first embodiment.
  • the throttle opening of the heating expansion valve 14a is overheated by the feedback control method based on the deviation between the target superheat degree SHO1 and the superheat degree SH1 of the outlet side refrigerant of the outdoor heat exchanger 16.
  • Degree SH1 is determined to approach the target superheat degree SHO1.
  • the target superheat degree SHO1 As the target superheat degree SHO1, a predetermined constant (5 ° C. in this embodiment) can be adopted.
  • the degree of superheat SH1 of the outlet side refrigerant of the outdoor heat exchanger 16 is calculated based on the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P4 detected by the fourth refrigerant pressure sensor 65d.
  • the control device 60 In the control flow of the outside air heating mode, in order to switch the refrigerating cycle device 10 to the refrigerant circuit of the outside air heating mode, the control device 60 opens the heating on-off valve 15b, and the three-way valve 15e is the flow on the water refrigerant heat exchanger 12 side. The outlet is opened and the outlet on the side of the first cooling passage 22c is closed. Further, the control device 60 puts the heating expansion valve 14a in a throttled state that exerts a refrigerant depressurizing action, and puts the cooling expansion valve 14b and the endothermic expansion valve 14c in a fully closed state.
  • the refrigerating cycle device 10 in the outside air heating mode heat is absorbed from the outside air by the outdoor heat exchanger 16 and the high temperature side heat medium is used by the water refrigerant heat exchanger 12 as in the outside air heating mode of the first embodiment. It can be heated to heat the interior of the vehicle.
  • the throttle opening of the endothermic expansion valve 14c is determined as in the outside air waste heat heating mode of the first embodiment.
  • the control device 60 In the control flow of the outside air waste heat heating mode, in order to switch the refrigeration cycle device 10 to the refrigerant circuit of the outside air waste heat heating mode, the control device 60 opens the heating on-off valve 15b, and the three-way valve 15e is the water refrigerant heat exchanger. The outlet on the 12 side is opened and the outlet on the first cooling passage 22c side is closed. Further, the control device 60 puts the heating expansion valve 14a in a throttle state that exerts a refrigerant decompression effect, the cooling expansion valve 14b in a fully closed state, and the endothermic expansion valve 14c in a throttle state that exerts a refrigerant decompression action. ..
  • the compressor 11, the water refrigerant heat exchanger 12, the receiver 25, the expansion valve 14a for heating, the outdoor heat exchanger 16, and the suction port of the compressor 11 are circulated in this order.
  • a steam compression type refrigeration cycle in which the refrigerant circulates in the order of the receiver 25, the heat absorption expansion valve 14c, the chiller 19, and the suction port of the compressor 11 is configured.
  • the refrigerating cycle device 10 in the outside air waste heat heating mode heat is absorbed from the outside air by the outdoor heat exchanger 16 and the low temperature side heat medium is used by the chiller 19 as in the outside air waste heat heating mode of the first embodiment. It is possible to heat the interior of the vehicle by absorbing heat from the waste heat device 80 and heating the heat medium on the high temperature side with the water refrigerant heat exchanger 12.
  • Waste heat heating mode In the control flow of the waste heat heating mode, the rotation speed of the compressor 11 and the opening SW of the air mix door 34 are determined as in the waste heat heating mode of the first embodiment. ..
  • the throttle opening of the endothermic expansion valve 14c is based on the deviation between the target superheat degree SHCO and the superheat degree SHC of the outlet side refrigerant of the chiller 19, and the superheat degree SHC is used by the feedback control method. Is determined to approach the target superheat degree SHCO. As the target superheat degree SHCO, a predetermined constant (5 ° C. in this embodiment) can be adopted.
  • the control device 60 closes the heating on-off valve 15b, and the three-way valve 15e is on the water refrigerant heat exchanger 12 side.
  • the outlet on the 22c side of the first cooling passage 22c is closed by opening the outlet.
  • the control device 60 puts the heating expansion valve 14a and the cooling expansion valve 14b in a fully closed state, and puts the endothermic expansion valve 14c in a throttle state that exerts a refrigerant depressurizing action.
  • the refrigerant is supplied in the order of the compressor 11, the water refrigerant heat exchanger 12, the receiver 25, the bypass passage 22a, the heat absorption expansion valve 14c, the chiller 19, and the suction port of the compressor 11.
  • a circulating steam compression refrigeration cycle is constructed.
  • the refrigerating cycle device 10 in the waste heat heating mode heat is absorbed from the waste heat device 80 via the low temperature side heat medium by the chiller 19 and heat exchange is performed in the water refrigerant, as in the waste heat heating mode of the first embodiment.
  • the air inside the vehicle can be heated by heating the air with the vessel 12.
  • the rotation speed of the compressor 11 is determined as in the frosted waste heat heating mode of the first embodiment.
  • the refrigerating cycle device 10 is switched to the same refrigerant circuit as the waste heat heating mode of the present embodiment.
  • the chiller 19 absorbs heat from the low temperature side heat medium. It is possible to heat the interior of the vehicle while maintaining the state in which it can be done as much as possible.
  • the opening degree of the heating expansion valve 14a in the outside air heating mode, is controlled based on the superheat degree SH1 of the refrigerant flowing out from the outdoor heat exchanger 16.
  • the opening degree of the endothermic expansion valve 14c is controlled based on the superheat degree SHC of the refrigerant flowing out from the chiller 19.
  • the opening degree of the heating expansion valve 14a is controlled based on the superheat degree SH1 of the refrigerant flowing out from the outdoor heat exchanger 16, and for heat absorption based on the superheat degree SH1 of the refrigerant flowing out from the chiller 19.
  • the opening degree of the expansion valve 14c is controlled.
  • the opening degree of the heating expansion valve 14a and the opening degree of the heat absorption expansion valve 14c are appropriately controlled, and the outdoor heat exchanger 16 and the chiller are used.
  • the refrigerant pressure at 19 (in other words, the refrigerant temperature) can be appropriately controlled.
  • the refrigeration cycle device 10 capable of switching to a plurality of operation modes has been described, but the switching of the operation mode of the refrigeration cycle device 10 is not limited to this. At least, it suffices if the operation mode targeted for oil return control can be executed.
  • the components of the refrigeration cycle device are not limited to those disclosed in the above-described embodiment.
  • a plurality of cycle components may be integrated so that the above-mentioned effects can be exhibited.
  • the cooling expansion valve 14b and the endothermic expansion valve 14c those in which an electric expansion valve having no fully closed function and an on-off valve are directly connected may be adopted.
  • R1234yf is adopted as the refrigerant
  • the refrigerant is not limited to this.
  • R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted.
  • a mixed refrigerant or the like in which a plurality of types of these refrigerants are mixed may be adopted.
  • Carbon dioxide may be adopted as the refrigerant to form a supercritical refrigeration cycle in which the pressure of the refrigerant on the high pressure side is equal to or higher than the critical pressure of the refrigerant.
  • the configuration of the heating unit is not limited to that disclosed in the above-described embodiment.
  • a radiator may be added to the high temperature side heat medium circuit 40 and the low temperature side heat medium circuit 50 described in the first embodiment to dissipate excess heat to the outside air.
  • engine an internal combustion engine
  • engine cooling water may be circulated in the high temperature side heat medium circuit 40.
  • the configuration of the endothermic unit is not limited to that disclosed in the above-described embodiment.
  • a thermosiphon may be adopted in which the chiller 19 of the low temperature side heat medium circuit 50 described in the first embodiment is used as a condensing unit and the waste heat device 80 functions as an evaporation unit. According to this, the low temperature side heat medium pump 51 can be abolished.
  • the thermosiphon has an evaporating part for evaporating the refrigerant and a condensing part for condensing the refrigerant, and is configured by connecting the evaporating part and the condensing part in a closed loop shape (that is, in a ring shape). Then, the temperature difference between the temperature of the refrigerant in the evaporating part and the temperature of the refrigerant in the condensing part causes a difference in specific gravity in the refrigerant in the circuit, and the action of gravity naturally circulates the refrigerant to transport heat together with the refrigerant. It is a circuit.
  • heat is absorbed from the waste heat device 80 to the refrigerant via the low temperature side heat medium, but heat may be absorbed from the waste heat device 80 to the refrigerant via air, or waste heat may be absorbed. Heat may be absorbed directly from the device 80 to the refrigerant.
  • the refrigeration cycle device 10 according to the present disclosure is applied to the vehicle air conditioner 1, but the application of the refrigeration cycle device 10 is not limited to this.
  • it may be applied to an air conditioner or the like that performs indoor air conditioning.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Air Conditioning Control Device (AREA)
PCT/JP2021/025950 2020-08-05 2021-07-09 冷凍サイクル装置 Ceased WO2022030182A1 (ja)

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CN115111732A (zh) * 2022-06-14 2022-09-27 青岛海尔空调器有限总公司 空调器的控制方法、装置及空调器

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WO2012114447A1 (ja) * 2011-02-22 2012-08-30 株式会社日立製作所 車両用熱システム
JP2014088060A (ja) * 2012-10-29 2014-05-15 Mitsubishi Heavy Ind Ltd ヒートポンプ式車両用空調装置及び車両
JP2014223891A (ja) * 2013-05-17 2014-12-04 トヨタ自動車株式会社 温度調節装置

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JP7268976B2 (ja) 2018-08-10 2023-05-08 サンデン株式会社 車両用空気調和装置
JP6577685B1 (ja) 2019-02-13 2019-09-18 佰龍機械廠股▲ふん▼有限公司 給糸位置が変更可能な横編機用給糸器

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WO2012114447A1 (ja) * 2011-02-22 2012-08-30 株式会社日立製作所 車両用熱システム
JP2014088060A (ja) * 2012-10-29 2014-05-15 Mitsubishi Heavy Ind Ltd ヒートポンプ式車両用空調装置及び車両
JP2014223891A (ja) * 2013-05-17 2014-12-04 トヨタ自動車株式会社 温度調節装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115111732A (zh) * 2022-06-14 2022-09-27 青岛海尔空调器有限总公司 空调器的控制方法、装置及空调器

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