WO2019244765A1 - 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
WO2019244765A1
WO2019244765A1 PCT/JP2019/023461 JP2019023461W WO2019244765A1 WO 2019244765 A1 WO2019244765 A1 WO 2019244765A1 JP 2019023461 W JP2019023461 W JP 2019023461W WO 2019244765 A1 WO2019244765 A1 WO 2019244765A1
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WO
WIPO (PCT)
Prior art keywords
temperature
refrigerant
evaporator
cooling
mode
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/023461
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
寛幸 小林
伊藤　誠司
祐一 加見
賢吾 杉村
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 DE112019003105.8T priority Critical patent/DE112019003105T5/de
Priority to CN201980041462.9A priority patent/CN112334715B/zh
Publication of WO2019244765A1 publication Critical patent/WO2019244765A1/ja
Priority to US17/125,387 priority patent/US20210101451A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • B60H1/3211—Control means therefor for increasing the efficiency of a vehicle refrigeration cycle
    • 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 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 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
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K1/04—Arrangement or mounting of electrical propulsion units of the electric storage means for propulsion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/02—Arrangement in connection with cooling of propulsion units with liquid cooling
    • B60K11/04—Arrangement or mounting of radiators, radiator shutters, or radiator blinds
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/24—Conjoint control of vehicle sub-units of different type or different function including control of energy storage means
    • B60W10/26—Conjoint control of vehicle sub-units of different type or different function including control of energy storage means for electrical energy, e.g. batteries or capacitors
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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 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 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
    • B60H2001/3261—Cooling devices information from a variable is obtained related to temperature of the air at an evaporating 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 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
    • B60H2001/3263—Cooling devices information from a variable is obtained related to temperature of the refrigerant at an evaporating 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 devices
    • B60H1/32—Cooling devices
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3266—Cooling devices information from a variable is obtained related to the operation of the vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L1/00—Supplying electric power to auxiliary equipment of vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L3/00—Electric devices on electrically-propelled vehicles for safety purposes; Monitoring operating variables, e.g. speed, deceleration or energy consumption
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by 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
    • F25B2700/2116—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
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/70—Energy storage systems for electromobility, e.g. batteries

Definitions

  • the present disclosure relates to a refrigeration cycle device including a plurality of evaporators.
  • Patent Literature 1 describes a refrigeration cycle device for a vehicle that can perform cooling, heating, dehumidifying and heating in a vehicle cabin. Specifically, it has a radiator, an outdoor heat exchanger, and an evaporator.
  • the indoor evaporator absorbs heat from the air blown into the cabin into the refrigerant, and the outdoor heat exchanger radiates heat from the refrigerant to the outside air. Thereby, the air blown into the vehicle interior is cooled.
  • the outdoor heat exchanger absorbs heat from the outside air into the refrigerant, and the radiator radiates heat from the refrigerant to the air blown into the vehicle interior. Thereby, the air blown into the vehicle interior is heated.
  • the indoor evaporator causes the refrigerant to absorb heat from the air blown into the vehicle interior
  • the outdoor heat exchanger causes the refrigerant to absorb heat from the outside air
  • the radiator uses the air absorbed by the indoor evaporator. Radiates heat from the refrigerant.
  • the air blown into the vehicle compartment is heated after being dehumidified.
  • the present applicant is studying cooling the battery by adding a battery cooling evaporator to the refrigeration cycle device of Patent Document 1.
  • the power consumption of the vehicle refrigeration cycle device depends on how many times the target temperature of the battery cooling evaporator is set. (Power consumption) greatly changed (see FIG. 24 described later).
  • This problem also occurs in a refrigeration cycle device that can switch between a case where the refrigerant absorbs heat by a plurality of evaporators and a case where the refrigerant absorbs heat only by one evaporator.
  • a refrigeration cycle device includes a compressor, a radiator, a first evaporator, a second evaporator, a first throttle unit, a second throttle unit, and a control unit.
  • the compressor compresses and discharges the refrigerant.
  • the radiator radiates the refrigerant discharged from the compressor.
  • the first evaporator evaporates the refrigerant.
  • the second evaporator absorbs heat from the heat medium circulating between the heat absorbing target and the heat absorbing target to evaporate the refrigerant.
  • the first throttle section can change the flow rate of the refrigerant flowing into the first evaporator.
  • the second throttle section can change the flow rate of the refrigerant flowing into the second evaporator.
  • the control unit controls the operation of the compressor and the second throttle unit such that the temperature related to the temperature of the second evaporator approaches the target temperature.
  • the control unit switches between the first mode and the second mode.
  • the first throttle unit and the second throttle unit are controlled such that the refrigerant does not evaporate in the first evaporator and the refrigerant evaporates in the second evaporator.
  • the first throttle unit and the second throttle unit are controlled such that the refrigerant evaporates in both the first evaporator and the second evaporator.
  • the control unit sets the target temperature higher in the first mode than in the second mode.
  • the compressor is controlled so that the temperature of the second evaporator becomes higher. Therefore, the power consumption of the compressor can be reduced.
  • the second evaporator absorbs heat from the heat medium circulating between the heat absorbing object and the heat absorbing object, and evaporates the refrigerant. Therefore, even if the temperature of the second evaporator increases, the refrigerant of the second evaporator increases.
  • the temperature difference between the heat medium and the heat absorbing object can be secured, and the cooling capacity of the heat medium or the heat absorbing object can be secured.
  • the target temperature is set lower than in the first mode, so that the power consumption of the compressor can be prevented from deteriorating when used in a state where the heat exchange efficiency and the cycle balance are poor (see FIG. 25 described later). ).
  • FIG. 1 is an overall configuration diagram of a vehicle air conditioner according to a first embodiment. It is a block diagram which shows the electric control part of the vehicle air conditioner of 1st Embodiment. It is a flowchart which shows a part of control processing of the air conditioning control program of the first embodiment. It is a flowchart which shows another part of control processing of the air-conditioning control program of 1st Embodiment. It is a control characteristic figure for switching the operation mode of the air-conditioning control program of a 1st embodiment. It is another control characteristic figure for switching the operation mode of the air-conditioning control program of 1st Embodiment.
  • FIG. 4 is a control characteristic diagram for determining an opening degree pattern of a heating expansion valve and a cooling expansion valve in a heating series cooling mode according to the first embodiment. It is a flowchart which shows the control processing of the heating parallel cooling mode of 1st Embodiment.
  • FIG. 4 is a control characteristic diagram for determining an opening pattern of a heating expansion valve and a cooling expansion valve in a heating parallel cooling mode according to the first embodiment. It is a flowchart which shows the control processing of the cooling mode of 1st Embodiment. It is a graph which shows target low-temperature side heat carrier temperature in each operation mode of a 1st embodiment.
  • FIG. 4 is a Mollier chart showing an operation state when a target low-temperature-side heat medium temperature is set high in a cooling cooling mode of the first embodiment.
  • FIG. 4 is a Mollier chart showing an operation state when a target low-temperature-side heat medium temperature is set high in the heating series cooling mode of the first embodiment.
  • It is a whole block diagram of the vehicle air conditioner of 2nd Embodiment. It is a whole block diagram of the air conditioner for vehicles of 3rd Embodiment. It is a whole block diagram of the air conditioner for vehicles of 4th Embodiment.
  • the refrigeration cycle device 10 is applied to a vehicle air conditioner 1 mounted on an electric vehicle that obtains a driving force for traveling from an electric motor.
  • the vehicle air conditioner 1 adjusts the temperature of the battery 80 as well as air-conditions the interior of the vehicle, which is a space to be air-conditioned. For this reason, the vehicle air conditioner 1 can also be called an air conditioner with a battery temperature adjusting function.
  • the battery 80 is a secondary battery that stores electric power supplied to in-vehicle devices such as an electric motor.
  • the battery 80 of the present embodiment is a lithium ion battery.
  • the battery 80 is a so-called assembled battery formed by stacking a plurality of battery cells 81 and electrically connecting these battery cells 81 in series or in parallel.
  • the battery 80 can be cooled by the cold generated by the refrigeration cycle device 10. Therefore, the cooling object different from the blast air in the refrigeration cycle device 10 of the present embodiment is the battery 80.
  • the vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioning unit 30, a high-temperature heat medium circuit 40, a low-temperature heat medium circuit 50, and the like, as shown in the overall configuration diagram of FIG.
  • the refrigeration cycle device 10 cools the air blown into the vehicle compartment to perform air conditioning in the vehicle compartment.
  • the refrigeration cycle device 10 heats the high-temperature heat medium circulating in the high-temperature heat medium circuit 40 in order to perform air conditioning in the vehicle cabin.
  • the refrigeration cycle device 10 cools the low-temperature heat medium circulating in the low-temperature heat medium circuit 50 to cool the battery 80.
  • the refrigeration cycle device 10 is configured to be able to switch refrigerant circuits for various operation modes in order to perform air conditioning in the passenger compartment. For example, it is configured such that a refrigerant circuit in a cooling mode, a refrigerant circuit in a dehumidifying and heating mode, a refrigerant circuit in a heating mode, and the like can be switched. Further, the refrigeration cycle apparatus 10 can switch between an operation mode for cooling the battery 80 and an operation mode for not cooling the battery 80 in each operation mode for air conditioning.
  • an HFO-based refrigerant (specifically, R1234yf) is employed as a refrigerant, and the pressure of the discharged refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Constructs a subcritical refrigeration cycle. Further, a refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. Part of the refrigerating machine oil circulates through the cycle together with the refrigerant.
  • the compressor 11 sucks, compresses, and discharges the refrigerant in the refrigeration cycle device 10.
  • the compressor 11 is disposed in front of a vehicle compartment and is disposed in a driving device compartment in which an electric motor and the like are accommodated.
  • the compressor 11 is an electric compressor in which a fixed displacement compression mechanism having a fixed discharge capacity is rotationally driven by an electric motor.
  • the rotation speed (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60 described later.
  • the inlet of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the outlet of the compressor 11.
  • the water-refrigerant heat exchanger 12 has a refrigerant passage through which the high-pressure refrigerant discharged from the compressor 11 flows, and a water passage through which the high-temperature side heat medium circulating through the high-temperature side heat medium circuit 40 flows.
  • the water-refrigerant heat exchanger 12 is a heating heat exchanger that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage to heat the high-temperature heat medium. is there.
  • the water-refrigerant heat exchanger 12 is a radiator that radiates the refrigerant discharged from the compressor 11.
  • the outlet of the coolant passage of the water-refrigerant heat exchanger 12 is connected to the inlet of a first three-way joint 13a having three inflow ports that communicate with each other.
  • a three-way joint one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be employed.
  • the refrigeration cycle device 10 includes a second three-way joint 13b to a sixth three-way joint 13f, as described later.
  • the basic configuration of these second three-way joint 13b to sixth three-way joint 13f is the same as that of first three-way joint 13a.
  • the inlet of the heating expansion valve 14a is connected to one outlet of the first three-way joint 13a.
  • the other outlet of the first three-way joint 13a is connected to one inlet of the second three-way joint 13b via a bypass passage 22a.
  • An on-off valve 15a for dehumidification is arranged in the bypass passage 22a.
  • the dehumidifying on-off valve 15a is an electromagnetic valve that opens and closes a refrigerant passage connecting the other outflow side of the first three-way joint 13a and one inflow side of the second three-way joint 13b.
  • the dehumidifying on-off valve 15a is a bypass opening and closing unit that opens and closes the bypass passage 22a.
  • the refrigeration cycle device 10 includes a heating on-off valve 15b as described later.
  • the basic configuration of the heating on-off valve 15b is the same as that of the dehumidifying on-off valve 15a.
  • the on-off valve 15a for dehumidification and the on-off valve 15b for heating can switch the refrigerant circuit in each operation mode by opening and closing the refrigerant passage. Therefore, the on-off valve 15a for dehumidification and the on-off valve 15b for heating are refrigerant circuit switching devices for switching the refrigerant circuit of the cycle. The operations of 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 depressurizes the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 at least in the operation mode of heating the vehicle interior, and also causes the flow rate (mass flow rate) of the refrigerant to flow downstream. This is a heating decompression unit that adjusts the pressure.
  • the heating expansion valve 14a is an electric variable throttle mechanism that includes a valve body configured to change the throttle opening and an electric actuator that changes the opening of the valve body.
  • the refrigeration cycle apparatus 10 includes a cooling expansion valve 14b and a cooling expansion valve 14c, as described later.
  • the basic configuration of the cooling expansion valve 14b and the cooling expansion valve 14c is the same as that of the heating expansion valve 14a.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c have a fully open function and a fully closed function.
  • the full-opening function is a function of simply making the refrigerant passage without exerting the flow rate adjusting function and the refrigerant depressurizing function by fully opening the valve opening.
  • the fully closed function is a function of closing the refrigerant passage by fully closing the valve opening.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c can switch the refrigerant circuit in each operation mode by the fully open function and the fully closed function.
  • the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c of the present embodiment also have a function as a refrigerant circuit switching device.
  • the operations of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c are controlled by a control signal (control pulse) output from the control device 60.
  • the heating expansion valve 14a is a throttle unit for an outdoor heat exchanger that can change the flow rate of the refrigerant flowing into the outdoor heat exchanger 16.
  • the cooling expansion valve 14b is a throttle unit for the indoor evaporator that can change the flow rate of the refrigerant flowing into the indoor evaporator 18.
  • the expansion valve for heating 14a and the expansion valve for cooling 14b are first throttle sections that can change the flow rate of the refrigerant flowing into the outdoor heat exchanger 16 and the indoor evaporator 18.
  • the cooling expansion valve 14c is a second throttle unit that can change the flow rate of the refrigerant flowing into the chiller 19.
  • the refrigerant inlet side of the outdoor heat exchanger 16 is connected to the outlet of the heating expansion valve 14a.
  • the outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out of the heating expansion valve 14a and the outside air blown by a cooling fan (not shown).
  • the outdoor heat exchanger 16 is arranged on the front side in the drive device room. Therefore, when the vehicle is traveling, the traveling wind can be applied to the outdoor heat exchanger 16.
  • the outdoor heat exchanger 16 is a radiator that radiates the refrigerant.
  • the outdoor heat exchanger 16 is also a first evaporator that evaporates the refrigerant.
  • the first refrigerant passage 16 a is a refrigerant passage for guiding the refrigerant flowing out of the water-refrigerant heat exchanger 12 to the inlet side of the outdoor heat exchanger 16.
  • the refrigerant outlet of the outdoor heat exchanger 16 is connected to the inlet side of the third three-way joint 13c.
  • One outlet of the fourth three-way joint 13d is connected to one outlet of the third three-way joint 13c via a heating passage 22b.
  • the heating passage 22b is a second refrigerant passage for guiding the refrigerant flowing out of the outdoor heat exchanger 16 to the suction side of the compressor 11.
  • a heating on-off valve 15b for opening and closing the refrigerant passage is arranged in the heating passage 22b.
  • the heating on-off valve 15b is a second refrigerant passage opening / closing unit that opens and closes the second refrigerant passage.
  • the other inlet of the second three-way joint 13b is connected to the other outlet of the third three-way joint 13c.
  • a check valve 17 is arranged in the refrigerant passage connecting the other outlet side of the third three-way joint 13c and the other inlet side of the second three-way joint 13b. The check valve 17 allows the refrigerant to flow from the third three-way joint 13c to the second three-way joint 13b, and prohibits the refrigerant from flowing from the second three-way joint 13b to the third three-way joint 13c.
  • the outlet of the fifth three-way joint 13e is connected to the outlet of the second three-way joint 13b.
  • the inlet side of the cooling expansion valve 14b is connected to one outlet of the fifth three-way joint 13e.
  • the inlet side of the cooling expansion valve 14c is connected to the other outlet of the fifth three-way joint 13e.
  • the cooling expansion valve 14b is a heating decompression unit that depressurizes the refrigerant that has flowed out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant that flows downstream, at least in an operation mode in which cooling is performed in 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 an air-conditioning case 31 of an indoor air-conditioning unit 30 described later.
  • the indoor evaporator 18 blows air by exchanging heat between the low-pressure refrigerant depressurized by the cooling expansion valve 14b and the blast air blown from the blower 32 to evaporate the low-pressure refrigerant and exerting an endothermic effect on the low-pressure refrigerant.
  • This is a cooling heat exchanger that cools air.
  • One inlet side of the sixth three-way joint 13f is connected to the refrigerant outlet of the indoor evaporator 18.
  • the cooling expansion valve 14c is a cooling pressure reducing unit that reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant flowing downstream at least in the operation mode in which the battery 80 is cooled.
  • the outlet side of the cooling expansion valve 14c is connected to the inlet side of the refrigerant passage of the chiller 19.
  • the chiller 19 has a refrigerant passage through which the low-pressure refrigerant depressurized by the cooling expansion valve 14c flows, and a water passage through which the low-temperature heat medium circulating through the low-temperature heat medium circuit 50 flows.
  • the chiller 19 is a second evaporator 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, evaporates the low-pressure refrigerant, and exerts an endothermic effect.
  • the other inlet side of the sixth three-way joint 13f is connected to the outlet of the refrigerant passage of the chiller 19.
  • the inlet of the evaporation pressure regulating valve 20 is connected to the outlet of the sixth three-way joint 13f.
  • the evaporation pressure regulating valve 20 maintains the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined reference pressure in order to suppress frost formation on the indoor evaporator 18.
  • the evaporating pressure adjusting valve 20 is configured by a mechanical variable throttle mechanism that increases the valve opening as the pressure of the refrigerant on the outlet side of the indoor evaporator 18 increases.
  • the evaporation pressure regulating valve 20 maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a frost formation suppression temperature (1 ° C. in the present embodiment) capable of suppressing frost formation on the indoor evaporator 18. . Furthermore, the evaporating pressure regulating valve 20 of the present embodiment is disposed downstream of the sixth three-way joint 13f, which is the junction. For this reason, the evaporation pressure regulating valve 20 also maintains the refrigerant evaporation temperature in the chiller 19 at a temperature equal to or higher than the frost formation suppression temperature.
  • the other inlet side of the fourth three-way joint 13d is connected to the outlet of the evaporation pressure regulating valve 20.
  • the inlet of the accumulator 21 is connected to the outlet of the fourth three-way joint 13d.
  • the accumulator 21 is a gas-liquid separator that separates the gas-liquid of the refrigerant flowing into the inside and stores the surplus liquid-phase refrigerant in the cycle.
  • the suction port side of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 21.
  • the third refrigerant passage 18a is a refrigerant passage for guiding the refrigerant flowing out of the outdoor heat exchanger 16 to the suction side of the compressor 11 via the evaporator 18.
  • the battery cooling passage 19a passes the refrigerant flowing between the outdoor heat exchanger 16 and the cooling expansion valve 14b through the chiller 19 between the indoor evaporator 18 and the suction side of the compressor 11 in the third refrigerant passage 18a. It is a refrigerant passage leading to the space.
  • the fifth three-way joint 13e of the present embodiment functions as a branch part that branches the flow of the refrigerant flowing out of the outdoor heat exchanger 16.
  • the sixth three-way joint 13 f is a junction where the flow of the refrigerant flowing out of the indoor evaporator 18 and the flow of the refrigerant flowing out of the chiller 19 are merged and flown out to the suction side of the compressor 11.
  • the indoor evaporator 18 and the chiller 19 are connected in parallel with each other with respect to the refrigerant flow. Further, the bypass passage 22a guides the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 to an upstream side of the branch portion. The heating passage 22 b guides the refrigerant flowing out of the outdoor heat exchanger 16 to the suction port side of the compressor 11.
  • the high-temperature side heat medium circuit 40 is a heat medium circulation circuit that circulates the high-temperature side heat medium.
  • the high-temperature side heat medium a solution containing ethylene glycol, dimethylpolysiloxane, a nanofluid, or the like, an antifreeze, or the like can be used.
  • the high-temperature-side heat medium circuit 40 includes a water passage of the water-refrigerant heat exchanger 12, a high-temperature-side heat medium pump 41, a heater core 42, and the like.
  • the high-temperature heat medium pump 41 is a water pump that pumps the high-temperature heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12.
  • the high-temperature-side heat medium pump 41 is an electric pump whose rotation speed (ie, pumping capacity) is controlled by a control voltage output from the control device 60.
  • the outlet of the water passage of the water-refrigerant heat exchanger 12 is connected to the heat medium inlet side of the heater core 42.
  • the heater core 42 is a heat exchanger that heats the blown air by exchanging heat between the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 18.
  • the heater core 42 is arranged inside the air conditioning case 31 of the indoor air conditioning unit 30.
  • the heat medium outlet of the heater core 42 is connected to the suction port side of the high-temperature side heat medium pump 41.
  • 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, so that the heat radiation amount of the high-temperature side heat medium to the blow air in the heater core 42 is reduced. Can be adjusted. That is, in the high-temperature-side heat medium circuit 40, 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, so that the heating amount of the blown air in the heater core 42 can be adjusted.
  • each component of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 constitutes a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source. I have.
  • the low-temperature-side heat medium circuit 50 is a heat medium circulation circuit that circulates the low-temperature-side heat medium.
  • the same fluid as the high-temperature side heat medium can be used as the low-temperature side heat medium.
  • a water passage of the chiller 19 a low-temperature side heat medium pump 51, a cooling heat exchange section 52, a three-way valve 53, a low-temperature side radiator 54, and the like are arranged.
  • the low-temperature heat medium pump 51 is a water pump that pumps the low-temperature 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 cooling heat exchange unit 52 is connected to the outlet of the water passage of the chiller 19.
  • the cooling heat exchanging section 52 has a plurality of metal heat medium passages arranged to be in contact with the plurality of battery cells 81 (in other words, the heat absorbing target) forming the battery 80.
  • the heat exchange unit cools the battery 80 by exchanging heat between the battery cell 81 and the low-temperature side heat medium flowing through the heat medium flow path.
  • Such a cooling heat exchange section 52 may be formed by disposing a heat medium flow path between the battery cells 81 arranged in a stack. Further, cooling heat exchanging section 52 may be formed integrally with battery 80.
  • the battery case may be formed integrally with the battery 80 by providing a heat medium flow path in a dedicated case for accommodating the stacked battery cells 81.
  • the outlet of the cooling heat exchange unit 52 is connected to the inflow side of the three-way valve 53.
  • the three-way valve 53 is an electric three-way flow control valve having one inflow port and two outflow ports, and capable of continuously adjusting the passage area ratio of the two outflow ports. The operation of the three-way valve 53 is controlled by a control signal output from the control device 60.
  • the heat medium inlet side of the low-temperature radiator 54 is connected to one outlet of the three-way valve 53.
  • the other outlet of the three-way valve 53 is connected to the suction side of the low-temperature side heat transfer medium pump 51 via a radiator bypass passage 53a.
  • the radiator bypass flow path 53 a is a heat medium flow path in which the low-temperature side heat medium flowing out of the cooling heat exchange unit 52 flows by bypassing the low-temperature side radiator 54.
  • the three-way valve 53 continuously adjusts the flow rate of the low-temperature side heat medium flowing into the low-temperature side radiator 54 among the low-temperature side heat medium flowing out of the cooling heat exchange section 52 in the low-temperature side heat medium circuit 50. .
  • the low-temperature radiator 54 exchanges heat between the low-temperature heat medium flowing out of the cooling heat exchange unit 52 and the outside air blown by an outside air fan (not shown), and radiates heat of the low-temperature heat medium to the outside air. It is a vessel.
  • the low-temperature radiator 54 is disposed on the front side in the drive device room. Therefore, when the vehicle is traveling, the traveling wind can be applied to the low-temperature radiator 54. Therefore, the low temperature radiator 54 may be formed integrally with the outdoor heat exchanger 16 and the like. The heat medium outlet of the low-temperature radiator 54 is connected to the suction port side of the low-temperature heat medium pump 51.
  • the low-temperature side heat medium pump 51 adjusts the flow rate of the low-temperature side heat medium flowing into the cooling heat exchange section 52, so that the low-temperature side heat medium in the cooling heat exchange section 52. Can adjust the amount of heat absorbed from the battery 80. That is, in the present embodiment, the cooling unit that cools the battery 80 by evaporating the refrigerant flowing out of the cooling expansion valve 14c is configured by the respective components of the chiller 19 and the low-temperature side heat medium circuit 50.
  • the indoor air-conditioning unit 30 blows out the blast air whose temperature has been adjusted by the refrigeration cycle device 10 into the vehicle interior.
  • the indoor air-conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the forefront of the passenger compartment.
  • 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 blast air blown into the vehicle interior.
  • the air-conditioning case 31 has a certain degree of elasticity and is formed of a resin (for example, polypropylene) excellent in strength.
  • An inside / outside air switching device 33 is disposed on the most upstream side of the airflow of the air conditioning case 31.
  • the inside / outside air switching device 33 switches and introduces inside air (vehicle interior air) and outside air (vehicle outside air) into the air conditioning case 31.
  • the inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port for introducing the inside air into the air conditioning case 31 and the outside air introduction port for introducing the outside air by the inside / outside air switching door, and the inside air introduction air volume and the outside air. And the introduction ratio with respect to the introduced air volume.
  • the inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door. The operation of the electric actuator is controlled by a control signal output from the control device 60.
  • a blower 32 is disposed downstream of the inside / outside air switching device 33 in the flow of the blown air.
  • 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 blown air flow. That is, the indoor evaporator 18 is arranged on the upstream side of the flow of the blown air with respect to the heater core 42.
  • a cool air bypass passage 35 is provided in the air-conditioning case 31 to allow the air blown after passing through the indoor evaporator 18 to bypass the heater core 42.
  • An air mix door 34 is arranged on the downstream side of the 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 adjusts a flow rate ratio of a flow rate of the blown air passing through the heater core 42 and a flow rate of the blown air passing through the cool air bypass passage 35 among the blown air after passing through the indoor evaporator 18. Department.
  • the air mix door 34 is driven by an electric actuator for the air mix door. The operation of the electric actuator is controlled by a control signal output from the control device 60.
  • the mixing space is disposed downstream of the air flow of the heater core 42 and the cool air bypass passage 35 in the air conditioning case 31.
  • the mixing space is a space that mixes the blast air heated by the heater core 42 with the blast air that has not passed through the cool air bypass passage 35 and is not heated.
  • an opening hole for blowing out the blast air mixed in the mixing space (that is, the conditioned air) into the vehicle interior, which is the space to be air-conditioned, is arranged downstream of the airflow of the air-conditioning case 31.
  • the face opening hole is an opening hole for blowing out conditioned air toward the upper body of the occupant in the passenger compartment.
  • the foot opening hole is an opening hole for blowing out conditioned air toward the feet of the occupant.
  • the defroster opening hole is an opening hole for blowing out conditioned air toward the inside surface of the vehicle front window glass.
  • the face opening, the foot opening, and the defroster opening are respectively formed by a face opening, a foot opening, and a defroster opening provided in the vehicle cabin through ducts forming air passages. )It is connected to the.
  • the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air flow ratio of the air flow passing through the heater core 42 and the air flow passing through the cool air bypass passage 35 by the air mixing door 34. Then, the temperature of the blown air (conditioned air) blown out from each outlet into the vehicle interior is adjusted.
  • Face doors, foot doors, and defroster doors are disposed on the upstream side of the airflow from the face opening, the foot opening, and the defroster opening.
  • the face door adjusts the opening area of the face opening hole.
  • the foot door adjusts the opening area of the foot opening hole.
  • the defroster door adjusts the opening area of the froster opening hole.
  • These face doors, foot doors and defroster doors constitute an outlet mode switching device for switching the outlet mode.
  • These doors are connected to an electric actuator for driving the outlet mode door via a link mechanism or the like, and are rotated in conjunction therewith.
  • the operation of the electric actuator is also controlled by a control signal output from the control device 60.
  • Specific examples of the outlet mode switched by the outlet mode switching device include a face mode, a bi-level mode, and a foot mode.
  • the face mode is an outlet mode in which the face outlet is fully opened and air is blown from the face outlet toward the upper body of the occupant in the vehicle.
  • 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 occupant in the vehicle.
  • the foot mode is an outlet mode in which the foot outlet is fully opened and the defroster outlet is opened by a small opening, and air is mainly blown out from the foot outlet.
  • the defroster mode is an outlet mode in which the defroster outlet is fully opened and air is blown from the defroster outlet to the inner surface of the windshield.
  • the control device 60 is a control unit including a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and peripheral circuits thereof.
  • the control device 60 performs various calculations and processes based on the air-conditioning control program stored in the ROM, and various control target devices 11, 14a to 14c, 15a, 15b, 32, 41, connected to its output side. The operations of 51, 53, etc. are controlled.
  • a sensor group On the input side of the control device 60, a sensor group is connected as shown in the block diagram of FIG.
  • the sensor group includes an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation sensor 63, a first refrigerant temperature sensor 64a to a fifth refrigerant temperature sensor 64e, an evaporator temperature sensor 64f, a first refrigerant pressure sensor 65a, and a second refrigerant pressure sensor.
  • the control unit 60 receives detection signals from these sensor groups.
  • the internal air temperature sensor 61 is an internal air temperature detecting unit that detects the vehicle interior temperature (internal air temperature) Tr.
  • the outside air temperature sensor 62 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam.
  • the solar radiation sensor 63 is a solar radiation amount detecting unit that detects a solar radiation amount Ts 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 detector that detects the temperature T2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the third refrigerant temperature sensor 64c is a third refrigerant temperature detecting unit that detects the temperature T3 of the refrigerant flowing out of the outdoor heat exchanger 16.
  • the fourth refrigerant temperature sensor 64d is a fourth refrigerant temperature detector that detects the temperature T4 of the refrigerant flowing out of the indoor evaporator 18.
  • the fifth refrigerant temperature sensor 64e is a fifth refrigerant temperature detector that detects the temperature T5 of the refrigerant flowing out of the refrigerant passage of the chiller 19.
  • the evaporator temperature sensor 64f is an evaporator temperature detecting unit that detects a refrigerant evaporation temperature Tefin (hereinafter, referred to as an evaporator temperature Tefin) in the indoor evaporator 18. Specifically, 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 detector that detects the pressure P1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the second refrigerant pressure sensor 65b is a second refrigerant pressure detector that detects the pressure P2 of the refrigerant flowing out of the refrigerant passage of the chiller 19.
  • the high-temperature heat medium temperature sensor 66a is a high-temperature heat medium temperature detection unit that detects the high-temperature heat medium temperature TWH, which is the temperature of the high-temperature heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12.
  • the first low-temperature heat medium temperature sensor 67a is a first low-temperature heat medium temperature detection unit that detects the first low-temperature heat medium temperature TWL1, which is the temperature of the low-temperature heat medium flowing out of the water passage of the chiller 19.
  • the first low-temperature-side heat medium temperature TWL ⁇ b> 1 is a temperature related to the temperature 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 that is the temperature of the low-temperature side heat medium flowing out of the cooling heat exchange unit 52. .
  • the battery temperature sensor 68 is a battery temperature detector that detects the battery temperature TB (that is, the temperature of the battery 80).
  • the battery temperature sensor 68 of the present embodiment has a plurality of temperature sensors and detects temperatures at a plurality of locations of the battery 80. For this reason, the control device 60 can also detect a temperature difference between the components of the battery 80. Further, as the battery temperature TB, an average value of detection values of a plurality of temperature sensors is employed.
  • the air-conditioning air temperature sensor 69 is an air-conditioning air temperature detecting unit that detects the temperature of the air blown from the mixing space into the vehicle compartment TAV.
  • an operation panel 70 arranged near the instrument panel in the front of the vehicle compartment is connected to the input side of the control device 60, and various operation switches (in other words, provided on the operation panel 70). For example, operation signals from various operation units) are input.
  • Specific examples of various operation switches provided on the operation panel 70 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, a blowing mode switching switch, and the like.
  • the auto switch is a switch for setting or canceling the automatic control operation of the vehicle air conditioner.
  • the air conditioner switch is a switch for requesting that the air blown by the indoor evaporator 18 be cooled.
  • the air volume setting switch is a switch for manually setting the air volume of the blower 32.
  • the temperature setting switch is a switch for setting a target temperature Tset in the vehicle compartment.
  • the blowout mode changeover switch is a switch for manually setting the blowout mode.
  • control unit 60 of the present embodiment is integrally configured with a control unit that controls various control target devices connected to the output side.
  • the configuration (hardware and software) of the control device 60 that controls the operation of each device to be controlled constitutes a control unit that controls the operation of each device to be controlled.
  • the configuration for controlling the refrigerant discharge capacity of the compressor 11 constitutes the compressor control unit 60a.
  • the configuration of the control device 60 that controls the operations of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c constitutes an expansion valve control unit 60b.
  • the configuration of the control device 60 that controls the operation of the dehumidifying on-off valve 15a and the heating on-off valve 15b constitutes a refrigerant circuit switching control unit 60c.
  • the configuration for controlling the pumping capacity of the high-temperature side heat medium pump of the high-temperature side heat medium pump 41 constitutes the high-temperature side heat medium pump control unit 60d.
  • the configuration for controlling the low-temperature-side heat medium pumping capability of the low-temperature-side heat medium pump 51 constitutes a low-temperature-side heat medium pump control unit 60e.
  • the vehicle air conditioner 1 of the present embodiment not only performs air conditioning of the vehicle interior, but also adjusts the temperature of the battery 80. For this reason, in the refrigeration cycle apparatus 10, it is possible to perform operation in the following 11 operation modes by switching the refrigerant circuit.
  • Cooling mode is an operation mode in which the inside of the vehicle compartment is cooled by cooling the blown air and blowing it out into the vehicle compartment without cooling the battery 80.
  • In-series dehumidification heating mode is an operation in which the cooled and dehumidified blast air is reheated and blown out into the vehicle compartment without cooling the battery 80 to perform dehumidification and heating in the vehicle compartment. Mode.
  • Parallel dehumidifying and heating mode In the parallel dehumidifying and heating mode, the cooled and dehumidified blast air is reheated with a higher heating capacity than the serial dehumidifying and heating mode and is blown into the vehicle interior without cooling the battery 80. This is an operation mode for performing dehumidification and heating of the vehicle interior.
  • the heating mode is an operation mode in which the inside of the vehicle compartment is heated by heating the blown air and blowing it out into the vehicle compartment without cooling the battery 80.
  • Cooling cooling mode is an operation mode in which the battery 80 is cooled, and the inside of the vehicle compartment is cooled by cooling the blown air and blowing it out into the vehicle compartment.
  • Series dehumidification heating / cooling mode performs cooling of the battery 80, and also performs dehumidification and heating of the vehicle interior by reheating the cooled and dehumidified blast air and blowing it out into the vehicle interior. Operation mode.
  • Parallel dehumidification heating / cooling mode cools the battery 80 and reheats the cooled and dehumidified blast air with a higher heating capacity than the serial dehumidification heating / cooling mode to achieve cabin interior. This is an operation mode in which dehumidification and heating of the vehicle interior is performed by blowing air to the vehicle interior.
  • Heating / cooling mode is an operation mode in which the battery 80 is cooled, and the inside of the vehicle is heated by heating the blast air and blowing it out into the vehicle interior.
  • Heating series cooling mode In the heating series cooling mode, the operation of cooling the battery 80 and heating the inside of the vehicle by heating the blast air with a higher heating capacity than the heating and cooling mode and blowing the air into the vehicle interior. Mode.
  • Heating parallel cooling mode In the heating parallel cooling mode, the battery 80 is cooled, and the blast air is heated with a higher heating capacity than the heating serial cooling mode and is blown into the vehicle cabin, thereby heating the vehicle cabin. Operation mode.
  • Cooling mode This is an operation mode in which the battery 80 is cooled without performing air conditioning in the passenger compartment.
  • the refrigerant does not evaporate in the outdoor heat exchanger 16 and the indoor evaporator 18 and the refrigerant evaporates in the chiller 19. This is the first mode to perform.
  • the other operation mode is a second mode in which at least one of the outdoor heat exchanger 16 and the indoor evaporator 18 evaporates the refrigerant and the chiller 19 evaporates the refrigerant. is there.
  • the air-conditioning control program is executed when an automatic switch of the operation panel 70 is turned on (ON) by an occupant's operation and automatic control of the vehicle interior is set.
  • the air conditioning control program will be described with reference to FIGS.
  • Each control step shown in the flowchart of FIG. 3 and the like is a function realizing unit of the control device 60.
  • step S10 of FIG. 3 the detection signal of the above-described sensor group and the operation signal of the operation panel 70 are read.
  • a target outlet temperature TAO which is a target temperature of the air blown into the vehicle interior, is determined based on the detection signal and the operation signal read in step S10. Therefore, step S20 is a target outlet temperature determination unit.
  • TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ Ts + C (F1)
  • Tset is a vehicle interior set temperature set by the temperature setting switch. Tr is a vehicle interior temperature detected by the inside air sensor. Tam is the vehicle outside temperature detected by the outside air sensor. Ts is the amount of solar radiation detected by the solar radiation sensor. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.
  • step S30 it is determined whether or not the air conditioner switch is ON (turned on).
  • the fact that the air conditioner switch is turned on means that the occupant is requesting cooling or dehumidification in the vehicle interior.
  • the fact that the air conditioner switch is ON means that it is required to cool the blown air in the indoor evaporator 18.
  • step S30 If it is determined in step S30 that the air conditioner switch is ON, the process proceeds to step S40. If it is determined in step S30 that the air conditioner switch has not been turned on, the process proceeds to step S160.
  • step S40 it is determined whether the outside temperature Tam is equal to or higher than a predetermined reference outside temperature KA (0 ° C. in the present embodiment).
  • the reference outside air temperature KA is set so that cooling of the blown air by the indoor evaporator 18 is effective for cooling or dehumidifying the space to be air-conditioned.
  • the evaporation pressure regulating valve 20 changes the refrigerant evaporation temperature in the indoor evaporator 18 into a frost formation suppression temperature (1 ° C. in the present embodiment). ) Or more. For this reason, in the indoor evaporator 18, the blown air cannot be cooled to a temperature lower than the frost formation suppression temperature.
  • the reference outside air temperature KA is set to a value lower than the frost formation suppression temperature, and when the outside air temperature Tam is lower than the reference outside air temperature KA, the air blown by the indoor evaporator 18 is not cooled. .
  • step S40 If it is determined in step S40 that the outside temperature Tam is equal to or higher than the reference outside temperature KA, the process proceeds to step S50. If it is determined in step S40 that the outside temperature Tam is not equal to or higher than the reference outside temperature KA, the process proceeds to step S160.
  • step S50 it is determined whether the target outlet temperature TAO is equal to or lower than the cooling reference temperature ⁇ 1.
  • the cooling reference temperature ⁇ 1 is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance. In the present embodiment, as shown in FIG. 5, the cooling reference temperature ⁇ 1 is determined to be a low value as the outside temperature Tam decreases.
  • step S50 If it is determined in step S50 that the target outlet temperature TAO is equal to or lower than the cooling reference temperature ⁇ 1, the process proceeds to step S60. If it is determined in step S50 that the target outlet temperature TAO is not lower than the cooling reference temperature ⁇ 1, the process proceeds to step S90.
  • step S60 it is determined whether cooling of battery 80 is necessary. Specifically, in the present embodiment, when the battery temperature TB detected by the battery temperature sensor 68 is equal to or higher than a predetermined reference cooling temperature KTB (35 ° C. in the present embodiment), the cooling of the battery 80 is performed. Is determined to be necessary. When battery temperature TB is lower than reference cooling temperature KTB, it is determined that cooling of battery 80 is not necessary.
  • a predetermined reference cooling temperature KTB 35 ° C. in the present embodiment
  • step S60 If it is determined in step S60 that the cooling of the battery 80 is necessary, the process proceeds to step S70, and the cooling mode (5) is selected as the operation mode. If it is determined in step S60 that cooling of battery 80 is not necessary, the process proceeds to step S80, and (1) cooling mode is selected as the operation mode.
  • step S90 it is determined whether the target outlet temperature TAO is equal to or lower than the dehumidifying reference temperature ⁇ 1.
  • the dehumidifying reference temperature ⁇ 1 is determined based on the outside temperature Tam with reference to a control map stored in the control device 60 in advance.
  • the dehumidification reference temperature ⁇ 1 is determined to be a low value as the outside air temperature Tam decreases. Further, the dehumidifying reference temperature ⁇ 1 is determined to be higher than the cooling reference temperature ⁇ 1.
  • step S90 If it is determined in step S90 that the target outlet temperature TAO is equal to or lower than the dehumidifying reference temperature ⁇ 1, the process proceeds to step S100. If it is determined in step S90 that the target outlet temperature TAO is not lower than the dehumidifying reference temperature ⁇ 1, the process proceeds to step S130.
  • step S100 similarly to step S60, it is determined whether cooling of battery 80 is necessary.
  • step S100 If it is determined in step S100 that cooling of the battery 80 is necessary, the process proceeds to step S110, and (6) the in-line dehumidifying heating / cooling mode is selected as the operation mode of the refrigeration cycle apparatus 10. If it is determined in step S100 that cooling of battery 80 is not necessary, the process proceeds to step S120, and (2) in-line dehumidifying and heating mode is selected as the operation mode.
  • step S130 similarly to step S60, it is determined whether cooling of battery 80 is necessary.
  • step S130 If it is determined in step S130 that cooling of the battery 80 is necessary, the process proceeds to step S140, and (7) the parallel dehumidifying heating / cooling mode is selected as the operation mode of the refrigeration cycle device 10. If it is determined in step S100 that cooling of battery 80 is not necessary, the process proceeds to step S150, and (3) the parallel dehumidifying and heating mode is selected as the operation mode.
  • step S160 it is determined that cooling the blown air by the indoor evaporator 18 is not effective.
  • step S160 as shown in FIG. 4, it is determined whether or not the target outlet temperature TAO is equal to or higher than the heating reference temperature ⁇ .
  • the heating reference temperature ⁇ is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance. In the present embodiment, as shown in FIG. 6, the heating reference temperature ⁇ is determined to be a low value as the outside temperature Tam decreases. The heating reference temperature ⁇ is set such that heating of the blast air by the heater core 42 is effective for heating the space to be air-conditioned.
  • step S160 If it is determined in step S160 that the target outlet temperature TAO is equal to or higher than the heating reference temperature ⁇ , it is necessary to heat the blown air by the heater core 42, and the process proceeds to step S170. If it is determined in step S160 that the target outlet temperature TAO is not equal to or higher than the heating reference temperature ⁇ , it is not necessary to heat the blown air by the heater core 42, and the process proceeds to step S240.
  • step S170 similarly to step S60, it is determined whether cooling of battery 80 is necessary.
  • step S170 If it is determined in step S170 that cooling of battery 80 is necessary, the process proceeds to step S180. If it is determined in step S170 that cooling of battery 80 is not necessary, the process proceeds to step S230, and (4) heating mode is selected as the operation mode.
  • step S170 if it is determined in step S170 that cooling of battery 80 is necessary and the process proceeds to step S180, both heating of the vehicle interior and cooling of battery 80 need to be performed. Therefore, in the refrigeration cycle apparatus 10, the amount of heat released by the refrigerant to the high-temperature heat medium in the water-refrigerant heat exchanger 12 and the amount of heat absorbed by the refrigerant in the chiller 19 from the low-temperature heat medium are appropriately determined. Need to adjust.
  • the operation mode is switched as shown in steps S180 to S220 in FIG. Specifically, three operation modes of (8) heating / cooling mode, (9) heating series cooling mode, and (10) heating parallel cooling mode are switched.
  • step S180 it is determined whether or not the target outlet temperature TAO is equal to or lower than the first cooling reference temperature ⁇ 2.
  • the first cooling reference temperature ⁇ 2 is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance.
  • the first cooling reference temperature ⁇ 2 is determined to be a low value as the outside temperature Tam decreases. Further, at the same outside temperature Tam, the first cooling reference temperature ⁇ 2 is determined to be higher than the cooling reference temperature ⁇ 1.
  • step S180 If it is determined in step S180 that the target outlet temperature TAO is equal to or lower than the first cooling reference temperature ⁇ 2, the process proceeds to step S190, and (8) the heating / cooling mode is selected as the operation mode. If it is determined in step S180 that the target outlet temperature TAO is not lower than the first cooling reference temperature ⁇ 2, the process proceeds to step S200.
  • step S200 it is determined whether or not target outlet temperature TAO is equal to or lower than second cooling reference temperature ⁇ 2.
  • the second cooling reference temperature ⁇ 2 is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance.
  • the second cooling reference temperature ⁇ 2 is determined to be a low value as the outside air temperature Tam decreases. Further, the second cooling reference temperature ⁇ 2 is determined to be higher than the first cooling reference temperature ⁇ 2. At the same outside temperature Tam, the second cooling reference temperature ⁇ 2 is determined to be higher than the dehumidification reference temperature ⁇ 1.
  • step S200 If it is determined in step S200 that the target outlet temperature TAO is equal to or lower than the second cooling reference temperature ⁇ 2, the process proceeds to step S210, and (9) the heating series cooling mode is selected as the operation mode. If it is determined in step S200 that the target outlet temperature TAO is not lower than the second cooling reference temperature ⁇ 2, the process proceeds to step S220, and (10) the heating parallel cooling mode is selected as the operation mode.
  • step S240 a case where the process proceeds from step S160 to step S240 will be described.
  • step S240 similarly to step S60, it is determined whether cooling of battery 80 is necessary.
  • step S240 If it is determined in step S240 that cooling of battery 80 is necessary, the process proceeds to step S250, and (11) cooling mode is selected as the operation mode. If it is determined in step S200 that cooling of battery 80 is not necessary, the process proceeds to step S260, where the air blowing mode is selected as the operation mode, and the process returns to step S10.
  • the blow mode is an operation mode in which the blower 32 is operated according to a setting signal set by the air flow setting switch. If it is determined in step S240 that cooling of battery 80 is not necessary, it means that it is not necessary to operate refrigeration cycle device 10 for air conditioning in the vehicle compartment and cooling of the battery. Therefore, in step S260, the blower 32 may be stopped.
  • the operation mode of the refrigeration cycle device 10 is switched as described above. Further, the air-conditioning control program controls not only the operation of each component of the refrigeration cycle device 10 but also the operation of other components. Specifically, the air-conditioning control program also controls the operation of the high-temperature heat medium pump 41 of the high-temperature heat medium circuit 40 and the operation of the low-temperature heat medium pump 51 and the three-way valve 53 of the low-temperature heat medium circuit 50.
  • control device 60 controls the operation of the high-temperature side heat transfer medium pump 41 so as to exhibit a predetermined reference pumping capacity in each of the predetermined operation modes regardless of the operation mode of the refrigeration cycle device 10 described above. I do.
  • the heated high-temperature heat medium is pumped to the heater core 42.
  • the high-temperature side heat medium flowing into the heater core 42 exchanges heat with the blown air. Thereby, the blown air is heated.
  • the high-temperature-side heat medium flowing out of the heater core 42 is sucked into the high-temperature-side heat medium pump 41 and is pressure-fed to the water-refrigerant heat exchanger 12.
  • the control device 60 controls the operation of the low-temperature side heat transfer medium pump 51 so as to exhibit a predetermined reference pumping capacity in each operation mode, regardless of the operation mode of the refrigeration cycle device 10 described above.
  • the control device 60 causes the low-temperature side heat medium flowing out of the cooling heat exchange unit 52 to flow into the low-temperature side radiator 54.
  • the operation of the three-way valve 53 is controlled.
  • the second low-temperature heat medium temperature TWL2 is detected by a second low-temperature heat medium temperature sensor 67b.
  • the three-way heat medium flowing out of the cooling heat exchange unit 52 is sucked into the suction port of the low-temperature heat medium pump 51 in three directions.
  • the operation of the valve 53 is controlled.
  • the low-temperature side heat medium circuit 50 when the low-temperature side heat medium is cooled in the water passage of the chiller 19, the cooled low-temperature side heat medium is pumped to the cooling heat exchange section 52.
  • the low-temperature side heat medium that has flowed into the cooling heat exchange section 52 absorbs heat from the battery 80. Thereby, battery 80 is cooled.
  • the low-temperature side heat medium flowing out of the cooling heat exchange section 52 flows into the three-way valve 53.
  • the low-temperature heat medium flowing out of the cooling heat exchange unit 52 flows into the low-temperature radiator 54 and radiates heat to the outside air. I do.
  • the low-temperature side heat medium is cooled until it becomes equal to the outside air temperature Tam.
  • the low-temperature-side heat medium flowing out of the low-temperature-side radiator 54 is sucked into the low-temperature-side heat medium pump 51 and sent to the chiller 19 under pressure.
  • the second low-temperature-side heat medium temperature TWL2 is lower than the outside air temperature Tam
  • the low-temperature-side heat medium flowing out of the cooling heat exchange unit 52 is sucked into the low-temperature-side heat medium pump 51 and chilled. It is pumped to 19. For this reason, the temperature of the low-temperature side heat medium sucked into the low-temperature side heat medium pump 51 becomes equal to or lower than the outside air temperature Tam.
  • control map referred to in each operation mode described below is stored in the control device 60 for each operation mode in advance.
  • the corresponding control maps of the respective operation modes may be equivalent to each other or may be different from each other.
  • step S600 a target evaporator temperature TEO is determined.
  • the target evaporator temperature TEO is determined by referring to a control map stored in the control device 60 based on the target outlet temperature TAO. In the control map of the present embodiment, it is determined that the target evaporator temperature TEO increases as the target outlet temperature TAO increases.
  • step S610 the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is determined.
  • the amount of increase / decrease ⁇ IVO is based on the deviation between the target evaporator temperature TEO and the evaporator temperature Tefin detected by the evaporator temperature sensor 64f, and the feedback control method is used so that the evaporator temperature Tefin approaches the target evaporator temperature TEO. It is determined.
  • step S620 the target supercooling degree SCO1 of the refrigerant flowing out of the outdoor heat exchanger 16 is determined.
  • the target degree of supercooling SCO1 is determined with reference to a control map, for example, based on the outside air temperature Tam.
  • the target degree of supercooling SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • step S630 the amount of increase / decrease ⁇ EVC of the throttle opening of the cooling expansion valve 14b is determined.
  • the amount of increase / decrease ⁇ EVC is based on a deviation between the target degree of supercooling SCO1 and the degree of supercooling SC1 of the refrigerant on the outlet side of the outdoor heat exchanger 16, and the degree of supercooling of the refrigerant on the outlet side of the outdoor heat exchanger 16 is determined by a feedback control method.
  • SC1 is determined so as to approach target supercooling degree SCO1.
  • the degree of supercooling SC1 of the refrigerant on the outlet side 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.
  • step S640 the opening degree SW of the air mix door 34 is calculated using the following equation F2.
  • SW ⁇ TAO- (Tefin + C2) ⁇ / ⁇ TWH- (Tefin + C2) ⁇ (F2)
  • TWH is the high-temperature-side heat medium temperature detected by the high-temperature-side heat medium temperature sensor 66a.
  • C2 is a control constant.
  • step S650 the refrigeration cycle device 10 is switched to the refrigerant circuit in the cooling mode. Specifically, the heating expansion valve 14a is fully opened, the cooling expansion valve 14c is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S610, S630, and S640 is obtained, and the process returns to step S10.
  • the compressor 11 the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, and the indoor evaporator 18
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
  • a water-refrigerant heat exchanger 12 and an outdoor heat exchanger 16 function as a radiator, and an indoor evaporator 18 functions as an evaporator to form a vapor compression refrigeration cycle.
  • the air blown by the indoor evaporator 18 can be cooled, 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 by adjusting the opening of the air mix door 34, a part of the blast air cooled by the indoor evaporator 18 is reheated by the heater core 42 to reach the target outlet temperature TAO.
  • the blast air whose temperature has been adjusted so as to approach is blown into the vehicle interior. Thereby, cooling of the vehicle interior can be performed.
  • step S700 the target evaporator temperature TEO is determined as in the cooling mode.
  • step S710 the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is determined as in the cooling mode.
  • step S720 the target high-temperature heat medium temperature TWHO of the high-temperature heat medium is determined so that the air blown by the heater core 42 can be heated.
  • the target high-temperature-side heat medium temperature TWHO is determined with reference to a control map based on the target outlet 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.
  • step S730 the variation ⁇ KPN1 of the opening degree pattern KPN1 is determined.
  • the opening degree pattern KPN1 is a parameter for determining a combination of a throttle opening degree of the heating expansion valve 14a and a throttle opening degree of the cooling expansion valve 14b.
  • the opening degree pattern KPN1 increases as the target outlet temperature TAO increases. Then, as the opening degree pattern KPN1 increases, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14b increases.
  • step S740 the opening degree SW of the air mix door 34 is calculated as in the cooling mode.
  • the target outlet temperature TAO is higher than in the cooling mode, so that the opening degree SW of the air mix door 34 approaches 100%.
  • the opening of the air mix door 34 is determined such that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • step S750 the refrigeration cycle apparatus 10 is switched to the refrigerant circuit in the series dehumidifying and heating mode. Specifically, the cooling expansion valve 14c is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S710, S730, and S740 is obtained, and the process returns to step S10.
  • the compressor 11 in the serial dehumidification heating mode, the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, and the indoor evaporation
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the device 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
  • a water-refrigerant heat exchanger 12 functions as a radiator
  • an indoor evaporator 18 functions as an evaporator to form a vapor compression refrigeration cycle.
  • the air blown by the indoor evaporator 18 can be cooled, 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 series dehumidifying and heating mode, the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the cabin, thereby dehumidifying and heating the cabin. It can be performed.
  • the amount of heat release of the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 12 can be increased by increasing the opening degree pattern KPN1 in accordance with the increase in the target outlet temperature TAO. it can. Therefore, in the in-line dehumidifying and heating mode, the heating capability of the heater core 42 for blowing air can be improved with an increase in the target outlet temperature TAO.
  • step S800 the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined so that the blower air can be heated by the heater core 42, as in the serial dehumidifying and heating mode.
  • step S810 the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is determined.
  • the increase / decrease amount ⁇ IVO is determined by the feedback control method based on the deviation between the target high-temperature heat medium temperature TWHO and the high-temperature heat medium temperature TWH, and the high-temperature heat medium temperature TWH is set to the target high-temperature heat medium temperature It is determined to approach TWHO.
  • step S820 the target degree of superheat SHEO of the refrigerant on the outlet side of the indoor evaporator 18 is determined.
  • a predetermined constant 5 ° C. in the present embodiment
  • step S830 the variation ⁇ KPN1 of the opening degree pattern KPN1 is determined.
  • the superheat degree SHE is determined to be close to the target superheat degree SHEO by a feedback control method based on a deviation between the target superheat degree SHEO and the superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18. .
  • the superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18 is calculated based on the temperature T4 detected by the fourth refrigerant temperature sensor 64d and the evaporator temperature Tefin.
  • step S840 similarly to the cooling mode, the opening degree SW of the air mix door 34 is calculated.
  • the target outlet temperature TAO is higher than in the cooling mode, so that the opening degree SW of the air mix door 34 approaches 100% as in the serial dehumidifying and heating mode.
  • the opening of the air mix door 34 is determined so that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • step S850 the refrigeration cycle device 10 is switched to the refrigerant circuit in the parallel dehumidifying and heating mode. Specifically, the cooling expansion valve 14c is fully closed, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened. Furthermore, a control signal or a control voltage is output to each control target device so that the control state determined in steps S810, S830, and S840 is obtained, and the process returns to step S10.
  • 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 arranged in this order.
  • the refrigerant circulates, the refrigerant circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • a vapor compression refrigeration cycle is constructed.
  • the water-refrigerant heat exchanger 12 functions as a radiator, and the outdoor heat exchanger 16 and the indoor evaporator 18 connected in parallel to the refrigerant flow evaporate.
  • a refrigeration cycle that functions as a vessel is configured.
  • the blown air can be cooled by the indoor evaporator 18 and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the parallel dehumidifying and heating mode, the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, thereby dehumidifying and heating the vehicle interior. It can be performed.
  • the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel to the refrigerant flow, and the evaporation pressure regulating valve 20 is disposed downstream of the indoor evaporator 18. Have been. Thereby, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be made lower than the refrigerant evaporation temperature in the indoor evaporator 18.
  • the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased and the amount of heat released by the refrigerant in the water-refrigerant heat exchanger 12 can be increased as compared with the in-series dehumidifying and heating mode. .
  • the blown air can be reheated with a higher heating capacity than in the serial dehumidifying and heating mode.
  • step S900 similarly to the parallel dehumidification heating mode, the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined.
  • step S910 the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is determined as in the parallel dehumidifying / heating mode.
  • step S920 the target supercooling degree SCO2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is determined.
  • the target degree of supercooling SCO2 is determined by referring to a control map based on the suction temperature of the air blown into the indoor evaporator 18 or the outside temperature Tam.
  • the target degree of supercooling SCO2 is determined such that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • step S930 an increase / decrease amount ⁇ EVH of the throttle opening of the heating expansion valve 14a is determined.
  • the increase / decrease amount ⁇ EVH is determined based on a deviation between the target supercooling degree SCO2 and the supercooling degree SC2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 by a feedback control method.
  • the supercooling degree SC2 of the refrigerant flowing out of the refrigerant passage is determined so as to approach the target supercooling degree SCO2.
  • the supercooling degree SC2 of the refrigerant flowing out of the refrigerant passage 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. Is done.
  • step S940 similarly to the cooling mode, the opening degree SW of the air mix door 34 is calculated.
  • the target outlet temperature TAO is higher than in the cooling mode, so that the opening degree SW of the air mix door 34 approaches 100%. Therefore, in the heating mode, the opening of the air mix door 34 is determined such that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.
  • step S950 in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the heating mode, the cooling expansion valve 14b is fully closed, the cooling expansion valve 14c is fully closed, the dehumidifying on-off valve 15a is closed, and heating is performed.
  • the on-off valve 15b is opened. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S910, S930, and S940 is obtained, and the process returns to step S10.
  • the refrigerant flows in the order of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the compressor 11.
  • a circulating vapor compression refrigeration cycle is configured.
  • a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a radiator and the outdoor heat exchanger 16 functions as an evaporator is configured.
  • the water-refrigerant heat exchanger 12 can heat the high-temperature side heat medium. Therefore, in the vehicle air conditioner 1 in the heating mode, the air in the vehicle compartment can be heated by blowing the blast air heated by the heater core 42 into the vehicle compartment.
  • Cooling cooling mode In the cooling cooling mode, the control device 60 executes a control flow in the cooling cooling mode shown in FIG. First, in steps S1100 to S1140, similarly to steps S600 to S640 in the cooling mode, the target evaporator temperature TEO, the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11, the increase / decrease amount ⁇ EVC of the throttle opening of the cooling expansion valve 14b, The opening degree SW of the air mix door 34 is determined.
  • step S1150 the target superheat degree SHCO of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 is determined.
  • the target degree of superheat SHCO a predetermined constant (5 ° C. in the present embodiment) can be adopted.
  • step S1160 an increase / decrease amount ⁇ EVB of the throttle opening of the cooling expansion valve 14c is determined.
  • the increase / decrease amount ⁇ EVB is based on a deviation between the target superheat degree SHCO and the superheat degree SHC of the refrigerant flowing out of the refrigerant passage of the chiller 19, and is based on a feedback control method.
  • the superheat degree SHC is determined so as to approach the target superheat degree SHCO.
  • the superheat degree SHC of the refrigerant flowing out of the refrigerant passage 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.
  • step S1170 the target low-temperature-side heat medium temperature TWLO of the low-temperature side heat medium flowing out of the water passage of the chiller 19 is determined.
  • the target low-temperature side heat transfer medium temperature TWLO is determined to be a first fixed value TWLO1 stored in the control device 60 in advance.
  • step S1180 it is determined whether the first low-temperature heat medium temperature TWL1 detected by the first low-temperature heat medium temperature sensor 67a is higher than the target low-temperature heat medium temperature TWLO.
  • step S1180 If it is determined in step S1180 that the first low-temperature-side heat medium temperature TWL1 is higher than the target low-temperature-side heat medium temperature TWLO, the process proceeds to step S1200. If it is determined in step S1180 that the first low-temperature heat medium temperature TWL1 is not higher than the target low-temperature heat medium temperature TWLO, the process proceeds to step S1190. In step S1190, the cooling expansion valve 14c is fully closed, and the process proceeds to step S1200.
  • step S1200 the refrigeration cycle device 10 is switched to the refrigerant circuit in the cooling cooling mode. Specifically, the heating expansion valve 14a is fully opened, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S1110, S1130, S1140, S1160, and S1190 is obtained, and the process returns to step S10.
  • the compressor 11 the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14b, the indoor evaporator
  • the refrigerant circulates in the order of 18, an evaporation pressure adjusting valve 20, an accumulator 21, and a compressor 11, and a compressor 11, a water-refrigerant heat exchanger 12, a heating expansion valve 14a, an outdoor heat exchanger 16, a check valve 17 ,
  • the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as radiators, and the indoor evaporator 18 and the chiller 19 function as evaporators.
  • a cycle is configured.
  • the blown air can be cooled by the indoor evaporator 18 and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the chiller 19 can cool the low-pressure side heat medium.
  • the vehicle air conditioner 1 in the cooling cooling mode, by adjusting the opening of the air mix door 34, a part of the blast air cooled by the indoor evaporator 18 is reheated by the heater core 42, and the target outlet temperature TAO is set. Blowing air whose temperature has been adjusted so as to approach the vehicle is blown into the vehicle interior. Thereby, cooling of the vehicle interior can be performed.
  • the battery 80 can be cooled by flowing the low-temperature side heat medium cooled by the chiller 19 into the cooling heat exchange unit 52.
  • the control device 60 executes the control flow in the series dehumidification heating / cooling mode shown in FIG. First, in steps S1300 to S1340, similarly to steps S700 to S740 in the series dehumidifying and heating mode, the target evaporator temperature TEO, the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11, the change amount ⁇ KPN1 of the opening degree pattern KPN1, the air mixing door The opening degree SW of No. 34 is determined.
  • steps S1350 to S1370 similarly to steps S1150 to S1170 in the cooling / cooling mode, the target superheat degree SHCO, the increase / decrease amount ⁇ EVB of the throttle opening of the cooling expansion valve 14c, and the target low-temperature side heat medium temperature TWLO are determined.
  • step S1380 when it is determined that the first low-temperature heat medium temperature TWL1 is higher than the target low-temperature heat medium temperature TWLO, similarly to the cooling mode, the process proceeds to step S1400. If it is not determined in step S1380 that first low-temperature-side heat medium temperature TWL1 is higher than target low-temperature-side heat medium temperature TWLO, the process proceeds to step S1390. In step S1390, the cooling expansion valve 14c is fully closed, and the process proceeds to step S1400.
  • step S1400 the refrigeration cycle apparatus 10 is switched to the refrigerant circuit in the in-line dehumidifying heating / cooling mode. Specifically, the on-off valve 15a for dehumidification is closed, and the on-off valve 15b for heating is closed. Furthermore, a control signal or a control voltage is output to each control target device so that the control state determined in steps S1310, S1330, S1340, S1360, and S1390 is obtained, and the process returns to step S10.
  • the refrigerant circulates in the order of the pressure control valve 20, the accumulator 21, and the compressor 11, and the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the expansion valve 14c, the chiller 19, the evaporation pressure adjusting valve 20, the accumulator 21, and the compressor 11 is configured.
  • a water-refrigerant heat exchanger 12 functions as a radiator, and a vapor compression refrigeration cycle in which the indoor evaporator 18 and the chiller 19 function as an evaporator is configured.
  • the blown air can be cooled by the indoor evaporator 18 and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the chiller 19 can cool the low-pressure side heat medium.
  • the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, thereby dehumidifying and heating the vehicle interior. It can be performed.
  • the opening degree pattern KPN1 it is possible to improve the heating capability of the blower air in the heater core 42, as in the serial dehumidifying and heating mode.
  • the battery 80 can be cooled by flowing the low-temperature side heat medium cooled by the chiller 19 into the cooling heat exchange unit 52.
  • the control device 60 executes a control flow in the parallel dehumidification heating / cooling mode shown in FIG.
  • steps S1500 to S1540 similarly to steps S800 to S840 in the parallel dehumidifying and heating mode, the target high-temperature-side heat medium temperature TWHO, the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11, the target superheat degree SHEO, and the opening degree pattern KPN1 are determined.
  • the change amount ⁇ KPN1 and the opening degree SW of the air mix door 34 are determined.
  • steps S1550 to S1570 similarly to steps S1150 to S1170 in the cooling / cooling mode, the target superheat degree SHCO, the increase / decrease amount ⁇ EVB of the throttle opening of the cooling expansion valve 14c, and the target low-temperature side heat medium temperature TWLO are determined.
  • step S1580 when it is determined that the first low-temperature heat medium temperature TWL1 is higher than the target low-temperature heat medium temperature TWLO, as in the cooling cooling mode, the process proceeds to step S1600. If it is determined in step S1580 that the first low-temperature heat medium temperature TWL1 is not higher than the target low-temperature heat medium temperature TWLO, the process proceeds to step S1590. In step S1590, the cooling expansion valve 14c is fully closed, and the process proceeds to step S1600.
  • step S1600 the refrigeration cycle device 10 is switched to the refrigerant circuit in the parallel dehumidification heating / cooling mode. Specifically, the on-off valve 15a for dehumidification is opened, and the on-off valve 15b for heating is opened. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S1510, S1530, S1540, S1560, and S1590 is obtained, and the process returns to step S10.
  • the compressor 11 in the refrigerating cycle device 10 in the parallel dehumidifying heating cooling mode, 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 While the refrigerant circulates in this order, the refrigerant flows in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • Vapor compression in which the refrigerant circulates and the refrigerant further circulates in the order of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • the refrigerating cycle of the formula is constituted.
  • the water-refrigerant heat exchanger 12 functions as a radiator, and the outdoor heat exchanger 16, the indoor evaporator 18, and the outdoor heat exchanger 16 are connected in parallel to the refrigerant flow.
  • a refrigeration cycle in which the chiller 19 functions as an evaporator is configured.
  • the blown air can be cooled by the indoor evaporator 18 and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the chiller 19 can cool the low-pressure side heat medium.
  • the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle interior, thereby dehumidifying the vehicle interior. Heating can be performed.
  • the blown air can be reheated with a higher heating capacity than in the serial dehumidifying heating / cooling mode.
  • the battery 80 can be cooled by flowing the low-temperature side heat medium cooled by the chiller 19 into the cooling heat exchange unit 52.
  • the control device 60 executes the control flow of the heating / cooling mode shown in FIG. First, in step S300, the target low-temperature-side heat medium temperature TWLO of the low-temperature side heat medium is determined so that the cooling heat exchange unit 52 can cool the battery 80.
  • the target low-temperature-side heat medium temperature TWLO of the low-temperature side heat medium is determined to be higher than in the cooling / cooling mode.
  • the target low-temperature-side heat medium temperature TWLO is determined to be the second fixed value TWLO2 stored in the control device 60 in advance.
  • the second fixed value TWLO2 is a value larger than the first fixed value TWLO1.
  • step S310 the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is determined.
  • the increase / decrease amount ⁇ IVO is determined based on the difference between the target low-temperature side heat medium temperature TWLO and the first low-temperature side heat medium temperature TWL1, and the first low-temperature side heat medium temperature TWL1 is changed to the target low-temperature side by a feedback control method. It is determined to approach the heating medium temperature TWLO.
  • step S320 the target supercooling degree SCO1 of the refrigerant flowing out of the outdoor heat exchanger 16 is determined.
  • the target supercooling degree SCO1 in the heating / cooling mode is determined by referring to the control map based on the outside air temperature Tam.
  • the target degree of supercooling SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.
  • step S330 an increase / decrease amount ⁇ EVB of the throttle opening of the cooling expansion valve 14c is determined.
  • the increase / decrease amount ⁇ EVB is based on a deviation between the target degree of supercooling SCO1 and the degree of supercooling SC1 of the refrigerant on the outlet side of the outdoor heat exchanger 16, and is based on a feedback control method.
  • SC1 is determined so as to approach target supercooling degree SCO1.
  • the degree of supercooling SC1 is calculated in the same manner as in the cooling mode.
  • step S340 the opening degree SW of the air mix door 34 is calculated as in the cooling mode.
  • step S350 the refrigeration cycle device 10 is switched to the refrigerant circuit in the heating / cooling mode. Specifically, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each control target device so that the control state determined in steps S310, S330, and S340 is obtained, and the process returns to step S10.
  • the compressor 11 the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14c, the chiller 19,
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
  • a vapor compression refrigeration cycle in which the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator and the chiller 19 functions as an evaporator is configured.
  • the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12, and the low-temperature side heat medium can be cooled by the chiller 19.
  • the vehicle air conditioner 1 in the heating / cooling mode can heat the vehicle interior by blowing out the blast air heated by the heater core 42 into the vehicle interior. Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.
  • step S400 the target low-temperature-side heat medium temperature TWLO is determined as in the cooling cooling mode. That is, the target low-temperature-side heat medium temperature TWLO is determined to be the first fixed value TWLO1 stored in the control device 60 in advance.
  • step S410 the amount of increase or decrease ⁇ IVO of the rotation speed of the compressor 11 is determined as in the heating / cooling mode.
  • step S420 the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined in the same manner as in the series dehumidifying and heating mode.
  • step S430 the variation ⁇ KPN2 of the opening degree pattern KPN2 is determined.
  • the opening pattern KPN2 is a parameter for determining a combination of the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14c.
  • the opening degree pattern KPN2 increases. Then, as the opening degree pattern KPN2 increases, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14c increases.
  • step S440 the opening degree SW of the air mix door 34 is calculated as in the cooling mode.
  • step S450 the refrigeration cycle apparatus 10 is switched to the refrigerant circuit in the heating series cooling mode. Specifically, the cooling expansion valve 14b is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each control target device so that the control state determined in steps S310, S330, and S340 is obtained, and the process returns to step S10.
  • the compressor 11 the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14c, and the chiller 19
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
  • a water-refrigerant heat exchanger 12 functions as a radiator
  • a chiller 19 functions as a vapor compression refrigeration cycle as an evaporator.
  • the high-temperature-side heat medium can be heated by the water-refrigerant heat exchanger 12, and the low-temperature-side heat medium can be cooled by the chiller 19.
  • the inside of the vehicle cabin can be heated by blowing the blast air heated by the heater core 42 into the vehicle cabin. Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.
  • the outdoor heat exchanger 16 increases the opening degree pattern KPN2 in accordance with the increase in the target outlet temperature TAO.
  • the refrigerant saturation temperature at 16 decreases, and the difference from the outside air temperature Tam decreases.
  • the heat radiation amount of the refrigerant in the outdoor heat exchanger 16 can be reduced, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased.
  • the outdoor heat exchanger 16 increases the opening degree pattern KPN2 as the target outlet temperature TAO increases.
  • the mild temperature of the refrigerant at 16 decreases, and the temperature difference from the outside air temperature Tam increases. Thereby, the heat absorption amount of the refrigerant in the outdoor heat exchanger 16 can be increased, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased.
  • the heating series cooling mode it is possible to increase the amount of heat released from the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 12 by increasing the opening degree pattern KPN2 with an increase in the target outlet temperature TAO. it can. Therefore, in the heating series cooling mode, the heating capacity of the blower air in the heater core 42 can be improved as the target outlet temperature TAO increases.
  • step S500 the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined so that the air blown by the heater core 42 can be heated, similarly to the serial dehumidifying and heating mode.
  • step S510 the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is determined.
  • the increase / decrease amount ⁇ IVO is calculated by the feedback control method based on the deviation between the target high-temperature heat medium temperature TWHO and the high-temperature heat medium temperature TWH, as in the parallel dehumidifying / heating mode.
  • TWH is determined so as to approach the target high-temperature side heat medium temperature TWHO.
  • step S520 the target superheat degree SHCO of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 is determined.
  • a predetermined constant 5 ° C. in the present embodiment
  • step S530 the amount of change ⁇ KPN2 in the opening degree pattern KPN2 is determined.
  • the superheat degree SHC is determined so as to approach the target superheat degree SHCO by a feedback control method based on a deviation between the target superheat degree SHCO and the superheat degree SHC of the refrigerant on the outlet side of the refrigerant passage of the chiller 19.
  • the opening degree pattern KPN2 increases, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14c increases. Become. Therefore, when the opening degree pattern KPN2 increases, the flow rate of the refrigerant flowing into the refrigerant passage of the chiller 19 increases, and the superheat degree SHC of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 decreases.
  • step S540 the opening degree SW of the air mix door 34 is calculated as in the cooling mode.
  • step S550 the target low-temperature-side heat medium temperature TWLO of the low-temperature side heat medium is determined as in the cooling / cooling mode. That is, the target low-temperature side heat medium temperature TWLO is determined to be the first fixed value TWLO1 stored in the control device 60 in advance.
  • step S560 it is determined whether the first low-temperature heat medium temperature TWL1 detected by the first low-temperature heat medium temperature sensor 67a is higher than the target low-temperature heat medium temperature TWLO.
  • step S560 If it is determined in step S560 that the first low-temperature heat medium temperature TWL1 is higher than the target low-temperature heat medium temperature TWLO, the process proceeds to step S580, where the first low-temperature heat medium temperature TWL1 is set to the target low temperature. If it is not determined that the temperature is higher than the side heat medium temperature TWLO, the process proceeds to step S570. In step S570, the cooling expansion valve 14c is fully closed, and the process proceeds to step S580.
  • step S580 in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the heating parallel cooling mode, the cooling expansion valve 14b is fully closed, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S510, S530, S540, and S570 is obtained, and the process returns to step S10.
  • 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 arranged in this order.
  • the vapor circulates in the order of the refrigerant, the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the compressor 11.
  • a compression refrigeration cycle is configured.
  • the water-refrigerant heat exchanger 12 functions as a radiator, and the outdoor heat exchanger 16 and the chiller 19 connected in parallel to the refrigerant flow function as evaporators.
  • a functioning refrigeration cycle is configured.
  • the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12, and the low-temperature side heat medium can be cooled by the chiller 19.
  • the inside of the vehicle cabin can be heated by blowing the blast air heated by the heater core 42 into the vehicle cabin. Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.
  • the outdoor heat exchanger 16 and the chiller 19 are connected in parallel to the refrigerant flow, and the evaporation pressure regulating valve 20 is disposed downstream of the refrigerant passage of the chiller 19. ing.
  • the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be made lower than the refrigerant evaporation temperature in the refrigerant passage of the chiller 19.
  • the heating parallel cooling mode the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased and the amount of heat released by the refrigerant in the water-refrigerant heat exchanger 12 can be increased compared to the heating series cooling mode. .
  • the blown air can be reheated with a higher heating capacity than in the heating serial cooling mode.
  • Cooling Mode In the cooling mode, the control device 60 executes the control flow of the cooling mode shown in FIG. First, in steps S1000 to S1040, similarly to steps S300 to S340 in the heating / cooling mode, the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11, the target supercooling degree SCO1, and the increase / decrease amount ⁇ EVB of the throttle opening degree of the cooling expansion valve 14c. , The opening degree SW of the air mix door 34 is determined.
  • the target low-temperature-side heat medium temperature TWLO of the low-temperature-side heat medium is determined in the same manner as in the cooling / cooling mode. That is, the target low-temperature-side heat medium temperature TWLO is determined to be the second fixed value TWLO2 stored in the control device 60 in advance. As shown in FIG. 23, the second fixed value TWLO2 is a value larger than the first fixed value TWLO1.
  • the opening degree SW of the air mix door 34 approaches 0%. For this reason, in the cooling mode, the opening of the air mix door 34 is determined so that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the cool air bypass passage 35.
  • step S1050 the refrigeration cycle apparatus 10 is switched to the refrigerant circuit in the cooling mode. Specifically, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each control target device so that the control state determined in steps S1010, S1030, and S1040 is obtained, and the process returns to step S10.
  • the compressor 11 the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, the cooling expansion valve 14c, the chiller 19, the evaporator A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the pressure regulating valve 20, the accumulator 21, and the compressor 11 is configured.
  • a vapor compression refrigeration cycle in which the outdoor heat exchanger 16 functions as a radiator and the chiller 19 functions as an evaporator is configured.
  • the chiller 19 can cool the low-temperature side heat medium. Therefore, in the vehicle air conditioner 1 in the cooling mode, the battery 80 can be cooled by flowing the low-temperature side heat medium cooled by the chiller 19 into the cooling heat exchange unit 52.
  • the target low-temperature-side heat medium temperature TWLO is set higher than in the other operation modes.
  • power saving can be achieved as shown in FIG.
  • the reason will be described.
  • the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is a deviation between the target low-temperature side heat medium temperature TWLO and the first low-temperature side heat medium temperature TWL1. Is determined based on the feedback control method so that the first low-temperature side heat medium temperature TWL1 approaches the target low-temperature side heat medium temperature TWLO.
  • the target low-temperature-side heat medium temperature TWLO to be high, the number of revolutions of the compressor 11 can be kept low, so that the power consumption of the compressor 11 can be kept low.
  • the cooling capacity of the chiller 19 for the low-temperature side heat medium can be secured. In other words, the cooling capacity of the battery 80 can be secured.
  • the increase / decrease amount ⁇ IVO of the rotation speed of the compressor 11 is determined based on a deviation between the target evaporator temperature TEO and the evaporator temperature Tefin by a feedback control method. It is determined to approach the evaporator temperature TEO.
  • the chiller 19 cools the low-temperature heat medium and the water-refrigerant heat exchanger 12 heats the high-temperature heat medium to perform heating.
  • the outdoor heat exchanger 16 absorbs heat from outside air as a heat source for heating.
  • the control device 60 sets the target low-temperature-side heat medium temperature TWLO higher than in the other operation modes.
  • the compressor 11 is controlled so that the temperature of the chiller 19 increases. Therefore, power consumption of the compressor 11 can be reduced.
  • the chiller 19 absorbs heat from the heat medium circulating between the battery cell 81 and evaporates the refrigerant, even if the temperature of the chiller 19 increases, the temperature difference between the refrigerant of the chiller 19 and the heat medium or the battery cell 81 is increased. And the cooling capacity of the heat medium or the battery cells 81 can be ensured.
  • the target low-temperature side heat transfer medium temperature TWLO is set lower than in (8) the heating / cooling mode and (11) the cooling mode.
  • the deterioration of the power can be suppressed (see FIGS. 25 and 26 described above).
  • the control device 60 radiates heat from at least one of the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16, and
  • the cooling expansion valve 14b, the cooling expansion valve 14c, the heating expansion valve 14a, the heating on-off valve 15b, and the dehumidification on-off valve 15a are controlled so that the refrigerant evaporates and the refrigerant does not evaporate in the indoor evaporator 18.
  • control device 60 operates the cooling expansion valve 14b and the cooling expansion valve so that the refrigerant evaporates in the chiller 19 and the refrigerant evaporates in at least one of the outdoor heat exchanger 16 and the evaporator 18. It controls the valve 14c, the heating expansion valve 14a, the heating on-off valve 15b, and the dehumidification on-off valve 15a.
  • the heating / cooling mode is a heating / cooling mode in which the refrigerant radiates heat in the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16, the refrigerant evaporates in the chiller 19, and the refrigerant does not flow in the evaporator 18. Mode.
  • the refrigerant does not radiate heat in the water-refrigerant heat exchanger 12
  • the refrigerant radiates heat in the outdoor heat exchanger 16
  • the refrigerant evaporates in the chiller 19, and the refrigerant does not flow in the evaporator 18. It is a cooling mode. Thereby, power consumption can be reliably reduced.
  • control device 60 controls the operations of the compressor 11 and the cooling expansion valve 14c such that the temperature of the heat medium absorbed by the chiller 19 approaches the target low-temperature side heat medium temperature TWLO. Thereby, the battery cell 81 can be cooled well.
  • the inlet side of the cooling heat exchange unit 52a is connected to the outlet of the cooling expansion valve 14c.
  • the cooling heat exchange section 52a is a so-called direct cooling type cooler that cools the battery 80 by evaporating the refrigerant flowing through the refrigerant passage and exerting an endothermic effect. Therefore, in the present embodiment, a cooling unit is configured by the cooling heat exchange unit 52a.
  • the cooling heat exchanging section 52a has a plurality of refrigerant flow paths connected in parallel with each other so that the entire area of the battery 80 can be uniformly cooled.
  • the other inlet side of the sixth three-way joint 13f is connected to the outlet of the cooling heat exchange section 52a.
  • a cooling heat exchange unit inlet temperature sensor 64g is connected to the input side of the control device 60 of the present embodiment.
  • the cooling heat exchange unit entrance temperature sensor 64g is a cooling heat exchange unit entrance temperature detection unit that detects the temperature of the refrigerant flowing into the refrigerant passage of the cooling heat exchange unit 52a.
  • the fifth refrigerant temperature sensor 64e of the present embodiment detects the temperature T5 of the refrigerant flowing out of the refrigerant passage of the cooling heat exchange unit 52a.
  • the second refrigerant pressure sensor 65b of the present embodiment detects the pressure P2 of the refrigerant flowing out of the refrigerant passage of the cooling heat exchange unit 52a.
  • the cooling heat exchange unit inlet temperature sensor 64g When the detected temperature T7 is equal to or lower than the reference inlet-side temperature, the cooling expansion valve 14c is closed. As a result, it is possible to prevent the battery 80 from being unnecessarily cooled and the output of the battery 80 from being reduced.
  • the battery evaporator 55 evaporates the refrigerant by exchanging heat between the refrigerant depressurized by the cooling expansion valve 14c and the cooling air blown from the battery blower 56, and evaporates the refrigerant.
  • This is a cooling heat exchanger that cools the cooling air by exerting an endothermic effect.
  • One inlet side of the sixth three-way joint 13f is connected to the refrigerant outlet of the battery evaporator 55.
  • the battery blower 56 blows the cooling air cooled by the battery evaporator 55 toward the battery 80.
  • the battery blower 56 is an electric blower whose rotation speed (blowing capacity) is controlled by a control voltage output from the control device 60.
  • the battery case 57 contains the battery evaporator 55, the battery blower 56, and the battery 80 therein, and forms an air passage for guiding the cooling air blown from the battery blower 56 to the battery 80.
  • the air passage is a circulation passage that guides the cooling air blown to the battery 80 to the suction side of the battery blower 56.
  • the battery blower 56 blows the cooling air cooled by the battery evaporator 55 onto the battery 80, thereby cooling the battery 80. That is, in the present embodiment, a cooling unit is configured by the battery evaporator 55, the battery blower 56, and the battery case 57.
  • an input side of the control device 60 of the present embodiment is connected to a battery evaporator temperature sensor 64h.
  • the battery evaporator temperature sensor 64h is a battery evaporator temperature detector that detects a refrigerant evaporation temperature (battery evaporator temperature) T7 in the battery evaporator 55.
  • the battery evaporator temperature sensor 64h of the present embodiment specifically detects the heat exchange fin temperature of the battery evaporator 55.
  • control device 60 of the present embodiment controls the operation of the battery blower 56 so as to exhibit a predetermined reference blowing capacity for each of the operation modes, regardless of the operation mode.
  • the temperature T8 detected by the battery evaporator temperature sensor 64h in the operation mode in which the cooling of the battery 80 is required that is, in the operation mode in which the cooling expansion valve 14c is in the throttled state.
  • the cooling expansion valve 14c is closed. As a result, it is possible to prevent the battery 80 from being unnecessarily cooled and the output of the battery 80 from being reduced.
  • the indoor condenser 12a is a heating unit that exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 11 and the blast air to condense the refrigerant and heat the blast air.
  • the indoor condenser 12a is arranged in the air-conditioning case 31 of the indoor air-conditioning unit 30 similarly to the heater core 42 described in the first embodiment.
  • the indoor condenser 12a described in the fourth embodiment may be adopted as the heating unit of the refrigeration cycle device 10 described in the second and third embodiments.
  • the refrigeration cycle apparatus 10 that can be switched to a plurality of operation modes has been described, but the switching of the operation mode of the refrigeration cycle apparatus 10 is not limited to this.
  • the operation mode can be switched between (1) a cooling mode and (8) a heating / cooling mode.
  • the second cooling reference temperature ⁇ 2 is determined to be higher than the dehumidifying reference temperature ⁇ 1 has been described.
  • the second cooling reference temperature ⁇ 2 is equal to the dehumidifying reference temperature ⁇ 1. It may be.
  • each operation mode is not limited to the one disclosed in the above embodiment.
  • the blowing mode described in step S260 may be a stop mode for stopping not only the compressor 11 but also the blower 32.
  • the components of the refrigeration cycle device are not limited to those disclosed in the above embodiment.
  • a plurality of cycle components may be integrated or the like so as to exert the above-described effects.
  • a four-way joint structure in which the second three-way joint 13b and the fifth three-way joint 13e are integrated may be employed.
  • the cooling expansion valve 14b and the cooling expansion valve 14c those in which an electric expansion valve having no fully closed function and an on-off valve may be directly connected may be employed.
  • 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 obtained by mixing a plurality of types of these refrigerants may be employed.
  • a supercritical refrigeration cycle in which carbon dioxide is used as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.
  • the configuration of the heating unit is not limited to the configuration disclosed in the above embodiment.
  • a three-way valve 53 and a high-temperature-side radiator similar to the three-way valve 53 and the low-temperature-side radiator 54 of the low-temperature-side heat medium circuit 50 are added to the high-temperature-side heat medium circuit 40 described in the first embodiment, and excess heat is added. May be radiated to the outside air.
  • engine cooling water may be circulated through the high-temperature side heat medium circuit 40.
  • the configuration of the cooling unit is not limited to the configuration disclosed in the above embodiment.
  • a thermosiphon that makes the chiller 19 of the low-temperature side heating medium circuit 50 described in the first embodiment a condensing unit and makes the cooling heat exchanging unit 52 function as an evaporating unit may be employed. According to this, the low-temperature side heat medium pump 51 can be eliminated.
  • the thermosiphon has an evaporating section for evaporating the refrigerant and a condensing section for condensing the refrigerant, and is configured by connecting the evaporating section and the condensing section in a closed loop (that is, in a ring). Then, a temperature difference between the temperature of the refrigerant in the evaporating section and the temperature of the refrigerant in the condensing section causes a difference in specific gravity of the refrigerant in the circuit, and the refrigerant naturally circulates by the action of gravity to transport heat with the refrigerant. Circuit.
  • An inverter that converts direct current and alternating current, a charger that charges the battery 80 with electric power, a motor generator that outputs driving power for traveling by being supplied with electric power, and generates regenerative electric power during deceleration and the like It may be an electric device that generates heat during operation as described above.
  • the refrigeration cycle device 10 is applied to the vehicle air conditioner 1, but the application of the refrigeration cycle device 10 is not limited thereto.
  • the present invention may be applied to an air conditioner with a server cooling function for performing indoor air conditioning while appropriately adjusting the temperature of a computer server.
  • the target low-temperature-side heat medium temperature TWLO is determined to be the second fixed value TWLO2 stored in the control device 60 in advance.
  • the target low-temperature-side heat medium temperature TWLO may be determined to be lower by a predetermined temperature than the outside air temperature.
  • the outdoor heat exchanger 16 can reliably release heat to the outside air.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Transportation (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
PCT/JP2019/023461 2018-06-21 2019-06-13 冷凍サイクル装置 Ceased WO2019244765A1 (ja)

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DE112019003105.8T DE112019003105T5 (de) 2018-06-21 2019-06-13 Kühlkreislaufvorrichtung
CN201980041462.9A CN112334715B (zh) 2018-06-21 2019-06-13 制冷循环装置
US17/125,387 US20210101451A1 (en) 2018-06-21 2020-12-17 Refrigeration cycle device

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JP2018117742A JP7151206B2 (ja) 2018-06-21 2018-06-21 冷凍サイクル装置
JP2018-117742 2018-06-21

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FR3097807B1 (fr) * 2019-06-28 2021-07-09 Valeo Systemes Thermiques Procédé de gestion d’un dispositif de gestion thermique pour véhicule automobile
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JP2022146159A (ja) * 2021-03-22 2022-10-05 株式会社デンソー 冷凍サイクル装置
JP7632363B2 (ja) * 2022-03-22 2025-02-19 株式会社デンソー 熱交換システム
JP7838450B2 (ja) * 2022-11-09 2026-04-01 トヨタ自動車株式会社 車両用空気調和装置
DE102023112304A1 (de) * 2023-05-10 2024-11-14 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kühlsystem für ein elektrisch oder teilelektrisch angetriebenes Kraftfahrzeug
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DE102024110816B3 (de) * 2024-04-17 2025-07-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Verfahren zum Betrieb eines Kraftfahrzeugs, Kraftfahrzeug
CN118912763B (zh) * 2024-08-19 2025-04-11 无锡冠亚恒温制冷技术有限公司 一种温控设备及其电子膨胀阀的控制方法和控制装置

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JP2019219122A (ja) 2019-12-26
CN112334715B (zh) 2023-03-28
US20210101451A1 (en) 2021-04-08
CN112334715A (zh) 2021-02-05
DE112019003105T5 (de) 2021-04-22

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