WO2019031131A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

Info

Publication number
WO2019031131A1
WO2019031131A1 PCT/JP2018/025839 JP2018025839W WO2019031131A1 WO 2019031131 A1 WO2019031131 A1 WO 2019031131A1 JP 2018025839 W JP2018025839 W JP 2018025839W WO 2019031131 A1 WO2019031131 A1 WO 2019031131A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
unit
heat medium
refrigerant
heated
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/JP2018/025839
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
鈴木　聡
加藤　吉毅
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 CN201880050700.8A priority Critical patent/CN110998198B/zh
Priority to DE112018004104.2T priority patent/DE112018004104T5/de
Publication of WO2019031131A1 publication Critical patent/WO2019031131A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

Classifications

    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—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
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00885—Controlling the flow of heating or cooling liquid, e.g. valves or pumps
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00928—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising a secondary circuit
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00949—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising additional heating/cooling sources, e.g. second 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
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus.
  • Patent Document 1 discloses a refrigeration cycle apparatus that performs temperature control of a battery which is a heat generating portion accompanied by heat generation at the time of operation and temperature control of blowing air which is a fluid for heat exchange.
  • the heat of the heat generating portion is absorbed by the refrigerant on the low pressure side of the refrigeration cycle apparatus, and the absorbed heat is dissipated from the refrigerant on the high pressure side to the blast air to realize heating of the air conditioned space. ing.
  • the heat generated in the heat generating part can not be sufficiently absorbed by the refrigerant on the low pressure side sufficiently, and the refrigerant is generated in the heat generating part There was a problem that it was not possible to effectively use the heat.
  • the present disclosure aims to provide a refrigeration cycle apparatus capable of effectively utilizing the heat generated in a heat generating portion when heating a fluid to be heat-exchanged.
  • a refrigeration cycle apparatus is A compressor that compresses and discharges a refrigerant, a first heat exchange unit that uses the high-pressure refrigerant discharged from the compressor as a heat source to heat the fluid for heat exchange, and a decompressor that decompresses the refrigerant flowing out of the first heat exchange unit And a low temperature side heat medium circulation circuit for circulating the low temperature side heat medium, the low temperature side heat medium circulation circuit circulating the low temperature side heat medium and the low temperature side heat medium circulation circuit for circulating the low pressure side heat medium.
  • the heat generating part for heating the side heat medium, the second heat exchange part for heating the fluid for heat exchange with the low stage side heat medium heated by the heat generating part as a heat source, and the low stage side heat medium for the heat medium evaporator It has a flow volume adjustment part which adjusts the flow volume which flows in, and the flow volume which low stage side heat carrier flows in into the 2nd heat exchange part, and the flow volume control part which controls operation of a flow volume adjustment part.
  • the flow adjustment unit In the first heating mode in which the flow control unit heats the fluid to be heat exchanged in the first heat exchange unit, the flow adjustment unit is configured to cause the lower-stage heat medium heated in the heat generating unit to flow into the heat medium evaporator.
  • the second heating mode in which the second heat exchange unit heats the fluid to be heat exchanged in the second heat exchange unit, the flow rate of the lower stage heat medium heated in the heat generation unit is caused to flow into the second heat exchange unit. Control the operation of the adjustment unit.
  • the heat of the low-stage heat medium heated by the heat generating portion is absorbed by the refrigerant in the heat medium evaporator, and the heat absorbed by the refrigerant is used as the heat source to perform the first heat exchange
  • the heat exchange target fluid can be heated in the unit.
  • the heat exchange target fluid can be heated in the second heat exchange unit by using heat of the low-stage side heat medium heated in the heat generation unit as a heat source.
  • a refrigeration cycle apparatus includes a compressor that compresses and discharges a refrigerant, and a condenser that heats a heat medium by exchanging heat between a high pressure refrigerant discharged from the compressor and the heat medium.
  • a decompressor (13, 62, 63) for decompressing the refrigerant flowing out of the condenser, a heat medium evaporator for causing the refrigerant reduced in pressure by the decompressor to heat exchange with the heat medium, and heat generation for heating the heat medium
  • a heater core for heating the fluid to be heat exchanged using as a heat source at least one of the heat medium heated by the condenser and the heat medium heated by the heat generation part, and the heat medium heated by the heat It has a flow control part which adjusts a flow which flows into an evaporator, and a flow which a heat carrier heated by a heat generating part flows into a heater core, and a flow control part which controls operation of a flow control.
  • the flow control unit heats the fluid for heat exchange by using the heat medium heated by the condenser as a heat source
  • the flow rate is controlled so that the heat medium heated by the heat generation unit flows into the heat medium evaporator.
  • the heat source heating mode in which the heat exchange target fluid is heated by controlling the operation of the adjustment unit and using the heat medium heated by the heat generation unit as a heat source, the flow adjustment is performed so that the heat medium heated by the heat generation unit flows into the heater core. Control the operation of the unit.
  • the heat of the heat medium heated in the heat generating portion is absorbed by the refrigerant in the heat medium evaporator, and the heat absorbed by the refrigerant is used as the heat source in the first heat exchange portion
  • the heat exchange target fluid can be heated.
  • the heat exchange target fluid can be heated by the heater core using the heat of the heat medium heated by the heat generating portion as the heat source.
  • the heat generating part generates heat by switching from the refrigeration cycle heating mode to the heat source heating mode under an operating condition where the heat generation of the heat generating part increases and the pressure of the refrigerant discharged from the compressor unnecessarily increases. Heat can be effectively utilized to heat the heat exchange fluid.
  • FIG. 1 An air conditioner 1 equipped with the refrigeration cycle apparatus 10 according to the first embodiment will be described with reference to FIGS. 1 and 2.
  • the air conditioner 1 shown in FIG. 1 is applied to a vehicle air conditioner which adjusts the interior space of the vehicle to an appropriate temperature.
  • the air conditioner 1 of the present embodiment is mounted on a hybrid vehicle that obtains a driving force for vehicle traveling from an engine (in other words, an internal combustion engine) and a traveling electric motor.
  • the hybrid vehicle of the present embodiment is configured as a plug-in hybrid vehicle capable of charging a battery (in other words, an on-board battery) mounted on the vehicle with electric power supplied from an external power supply (in other words, a commercial power supply) It is done.
  • a battery in other words, an on-board battery
  • an external power supply in other words, a commercial power supply
  • a lithium ion battery can be used as the battery.
  • the driving force output from the engine is used not only for driving the vehicle but also for operating the generator.
  • the electric power generated by the generator and the electric power supplied from the external power supply can be stored in the battery, and the electric power stored in the battery is not only the electric motor for traveling but also the electric motor constituting the refrigeration cycle apparatus 10 It is supplied to various in-vehicle devices including formula components.
  • the air conditioner 1 heats the passenger compartment which is the space to be air conditioned (that is, heats the blowing air which is the fluid to be heat-exchanged).
  • the air conditioner 1 has a refrigeration cycle apparatus 10, a first heat exchange unit 20, a low-stage heat medium circulation circuit 30, and an indoor air conditioning unit 40.
  • the refrigeration cycle apparatus 10 includes a compressor 11, a condenser 12, a pressure reducing valve 13 (pressure reducing device), a refrigerant flow path adjusting valve 14, a heat medium evaporator 15, and an accumulator 16 (liquid storage unit).
  • the refrigeration cycle apparatus 10 further includes an external evaporator 18 and an outdoor heat exchanger blower 19.
  • a fluorocarbon-based refrigerant is used as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure refrigerant pressure does not exceed the critical pressure of the refrigerant is configured.
  • the compressor 11 is an electric compressor driven by electric power supplied from a battery, and sucks, compresses and discharges the refrigerant of the refrigeration cycle apparatus 10. The operation of the compressor 11 is controlled by a control signal output from the discharge capacity control unit 50a (shown in FIG. 2).
  • the refrigerant inlet side of the condenser 12 is connected to the discharge port of the compressor 11.
  • the condenser 12 performs heat exchange between the high-temperature and high-pressure refrigerant (hereinafter, abbreviated as high-pressure refrigerant) discharged from the compressor 11 and the cooling water as the high stage side heat medium to convert the heat of the high-pressure refrigerant into the cooling water.
  • high-pressure refrigerant high-pressure refrigerant
  • It is a radiator for heating which radiates heat and heats the cooling water.
  • the high pressure refrigerant condenses when the heat of the high pressure refrigerant is dissipated to the cooling water.
  • the first heat exchange unit 20 includes a high stage side heat medium circulation circuit 21, a high stage side pump 22, and a heater core 23.
  • the first heat exchange unit 20 heats the blown air by using the high pressure refrigerant discharged from the compressor 11 as a heat source.
  • the cooling water flowing in the high-stage side heat medium circulation circuit 21 and the cooling water flowing in the low-stage side heat medium circulation circuit 30 described later are a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid Is used.
  • the high stage side heat medium circulation circuit 21 is an annular flow path for circulating the cooling water between the condenser 12 and the heater core 23.
  • a condenser 12, a heater core 23, and a high stage side pump 22 are disposed in the high stage side heat medium circulation circuit 21.
  • the high stage side pump 22 circulates the cooling water in the high stage side heat medium circulation circuit 21 by sucking the cooling water and discharging it to the condenser 12 side.
  • the high stage side pump 22 is an electric pump, and is a high stage side flow rate adjustment unit that adjusts the flow rate of the cooling water circulating in the high stage side heat medium circulation circuit 21.
  • the heater core 23 is disposed in a casing 41 described later.
  • the heater core 23 heats the blowing air by heat exchange between the cooling water heated by the condenser 12 and the blowing air which is a fluid for heat exchange.
  • the condenser 12 heats the blowing air through the heater core 23.
  • the refrigerant inlet side of the pressure reducing valve 13 is connected to the refrigerant outlet side of the condenser 12.
  • the pressure reducing valve 13 is a pressure reducing device that reduces the pressure and expands the liquid phase refrigerant flowing out of the condenser 12. That is, the pressure reducing valve 13 reduces the pressure of the refrigerant downstream of the condenser 12.
  • the pressure reducing valve 13 is an electric variable throttle mechanism whose operation is controlled by a control signal output from the control device 50, and includes a valve body and an electric actuator.
  • the valve body is configured to be capable of changing the passage opening degree of the refrigerant passage (in other words, the throttle opening degree).
  • the electric actuator has a stepping motor that changes the throttle opening of the valve body.
  • the refrigerant flow path adjusting valve 14 branches the flow of the refrigerant flowing out of the pressure reducing valve 13 into the external evaporator 18 and the heat medium evaporator 15. For this reason, the external evaporator 18 and the heat medium evaporator 15 are disposed in parallel to the refrigerant flow.
  • the refrigerant flow path adjustment valve 14 adjusts the flow rate of the refrigerant flowing out of the pressure reducing valve 13 into the external evaporator 18 and the flow rate of the refrigerant flowing out of the pressure reducing valve 13 into the heat medium evaporator 15 It is a department.
  • the refrigerant flow control valve 14 is a three-way valve, and is a flow control valve of three types operated by supplying electric power, and its operation is controlled by a control signal output from the control device 50.
  • the refrigerant outlet side of the pressure reducing valve 13 is connected to the refrigerant inlet side of the external evaporator 18 via the refrigerant flow path adjusting valve 14.
  • the external evaporator 18 is an outside air evaporation unit that evaporates the low pressure refrigerant by heat exchange between the heat of the low pressure refrigerant decompressed by the pressure reducing valve 13 and the outside air blown by the outdoor heat exchanger blower 19. In the external evaporator 18, the low pressure refrigerant absorbs heat from the outside air and evaporates.
  • the outdoor heat exchanger blower 19 is an electric blower that drives a fan by an electric motor, and its operation is controlled by a control signal output from the control device 50.
  • the external evaporator 18 is disposed on the front side in the vehicle bonnet. Therefore, when the vehicle travels, the traveling wind can be applied to the external evaporator 18.
  • the refrigerant outlet side of the pressure reducing valve 13 is connected to the refrigerant inlet side of the heat medium evaporator 15 via the refrigerant flow path adjusting valve 14.
  • the heat medium evaporator 15 exchanges the heat of the low pressure refrigerant decompressed by the pressure reducing valve 13 with the cooling water which is the low stage side heat medium flowing in the low stage side heat medium circulation circuit 30, thereby converting the low pressure refrigerant.
  • the low-pressure refrigerant absorbs heat from the cooling water and is evaporated to cool the cooling water.
  • the lower stage heat medium circulation circuit 30 is an annular flow path, and cooling water which is a lower stage heat medium circulates.
  • the low-stage heat medium circulation circuit 30 includes a heat medium evaporator 15, a low-stage flow control valve 31, a low-stage radiator 32, a low-stage pump 33, a heating device 34, and a flow control valve 35 (flow control unit). Is arranged.
  • the low-stage-side heat medium circulation circuit 30 is connected to a radiator bypass flow path 37 for circulating the cooling water, which is the low-stage-side heat medium discharged by the low-stage pump 33, around the low-stage radiator 32. ing. Both ends of the radiator bypass flow path 37 are connected to the low stage side heat medium circulation circuit 30 on the inflow side and the outflow side of the low stage side radiator 32.
  • the low stage side flow rate adjustment valve 31 branches the flow of the cooling water flowing out of the heat medium evaporator 15 into the low stage side radiator 32 and the radiator bypass flow path 37.
  • the low stage side flow control valve 31 has a flow rate at which the cooling water flowing out of the heat medium evaporator 15 flows into the low stage side radiator 32 and the cooling water flowing out of the heat medium evaporator 15 flows into the radiator bypass flow path 37 It is a low stage side inflow adjustment part which adjusts with a flow.
  • the low-stage side flow control valve 31 is a three-way valve and is an electromagnetic valve that operates by being supplied with electric power, and its operation is controlled by a control signal output from the controller 50.
  • the low-stage radiator 32 absorbs heat by causing the cooling water cooled by the heat medium evaporator 15 to exchange heat with the outside air blown by the low-stage radiator blower 36.
  • the low-stage radiator blower 36 is an electric blower that drives a fan with an electric motor, and its operation is controlled by a control signal output from the control device 50.
  • the low-stage radiator 32 is disposed on the front side in the vehicle bonnet. Therefore, the traveling air can be applied to the low-stage radiator 32 when the vehicle travels.
  • the low stage side pump 33 is a low stage side heat medium pump which sucks in and discharges the cooling water.
  • the low stage side pump 33 is an electric pump, and is a low stage side flow rate adjustment unit that adjusts the flow rate of the cooling water circulating to the low stage side heat medium circulation circuit 30.
  • the heat generating device 34 is a heat generating portion that generates heat by operation and heats the cooling water discharged by the low-stage pump 33.
  • a PTC heater electric heater
  • the operation of the heating device 34 is controlled by a control signal output from the control device 50.
  • a second heat exchange flow path 38 Connected to the low stage side heat medium circulation circuit 30 is a second heat exchange flow path 38 through which the cooling water discharged by the low stage side pump 33 and heated by the heat generating device 34 flows. Both ends of the second heat exchange unit flow path 38 are connected to the low stage side heat medium circulation circuit 30 on the suction side of the low stage side pump 33 and the flow rate adjustment valve 35.
  • the second heat exchanger 39 is disposed in the second heat exchanger flow channel 38.
  • the second heat exchanger 39 is disposed in a casing 41 described later.
  • the second heat exchanger 39 heats the blown air by exchanging heat between the cooling water, which is discharged by the low-stage side pump 33 and heated by the heat generating device 34, and the blowing air, which is a heat exchange fluid. That is, the second heat exchanger 39 heats the blown air by using the cooling water heated by the heat generating device 34 as a heat source.
  • the flow rate adjustment valve 35 is discharged by the low-stage pump 33, and the flow rate of the cooling water heated by the heat generating device 34 flows into the heat medium evaporator 15, and the cooling water flows into the second heat exchanger 39. It is a flow rate adjustment unit that adjusts the flow rate.
  • the flow control valve 35 is a three-way valve, and is a three-type flow control valve operated by supplying power, and its operation is controlled by a control signal output from the controller 50.
  • the flow rate adjustment valve 35 is a heat medium flow rate to be introduced into the heat medium evaporator 15 out of the cooling water pressure-fed from the low-stage side pump 33 and heated by the heating device 34 and heat to be introduced into the second heat exchanger 39.
  • the flow rate ratio to the exchanger side flow rate can be adjusted continuously. Further, the entire amount of cooling water pressure-fed from the low-stage side pump 33 and heated by the heat generating device 34 can be made to flow into the heat medium evaporator 15, and the entire amount of this cooling water is added to the second heat exchanger 39. It can be made to flow.
  • the flow rate adjustment valve 35 is configured such that the entire amount of cooling water flows into the second heat exchanger 39 when it is not energized.
  • the refrigerant inlet side of the accumulator 16 is connected to the refrigerant outlet side of the heat medium evaporator 15. That is, the accumulator 16 is provided between the heat medium evaporator 15 and the compressor 11, that is, on the upstream side of the compressor 11.
  • the accumulator 16 is a gas-liquid separation unit that separates gas and liquid of the refrigerant that has flowed into the inside, and is a liquid storage unit that stores excess refrigerant in the cycle.
  • the suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 16. Therefore, the accumulator 16 suppresses the suction of the liquid-phase refrigerant into the compressor 11 and functions to prevent the liquid compression in the compressor 11.
  • the indoor air conditioning unit 40 is for blowing out the blowing air whose temperature has been adjusted by the refrigeration cycle apparatus 10 into the vehicle interior which is the space to be air conditioned.
  • the indoor air conditioning unit 40 is disposed inside the instrument panel at the foremost part of the vehicle interior.
  • the indoor air conditioning unit 40 is configured by housing the second heat exchanger 39, the heater core 23, and the like in a casing 41 forming the outer shell thereof.
  • the casing 41 is an air passage forming portion that forms an air passage for blowing air blown into the vehicle compartment, which is a space to be air conditioned.
  • the casing 41 has a certain degree of elasticity and is formed of a resin (for example, polypropylene) which is excellent in strength.
  • Inside / outside air switching as an inside / outside air switching unit to switch and introduce inside air (air within the air conditioned space) and outside air (air outside the air conditioned space) into the casing 41 on the most upstream side of the air flow inside the casing 41
  • a device 43 is arranged.
  • the inside / outside air switching device 43 can continuously change the air volume ratio between the air volume of the inside air and the air volume of the outside air.
  • an air conditioning blower 42 for directing the air drawn in via the inside / outside air switching device 43 into the space to be air-conditioned is arranged.
  • the air conditioning blower 42 is an electric blower that drives a centrifugal multi-blade fan (sirocco fan) by an electric motor, and the number of rotations (air flow amount) is controlled by the control voltage output from the control device 50.
  • a second heat exchanger 39 is disposed downstream of the air flow of the air conditioning blower 42 in the air passage formed in the casing 41.
  • the heater core 23 is disposed downstream of the second heat exchanger 39 in the flow of the blown air.
  • a plurality of opening holes are disposed at the most downstream portion of the flow of the blown air of the casing 41 for blowing the blown air (conditioned air) that has passed through the heater core 23 into the vehicle compartment, which is the space to be conditioned.
  • the control device 50 shown in FIG. 2 is composed of a known microcomputer including a CPU, a ROM, a RAM and the like, and peripheral circuits thereof.
  • the control device 50 performs various operations and processing based on the control program stored in the ROM.
  • Various control target devices are connected to the output side of the control device 50.
  • the control device 50 is a control unit that controls the operation of various control target devices.
  • the control target devices controlled by the control device 50 include the compressor 11, the pressure reducing valve 13, the refrigerant flow path adjusting valve 14, the outdoor heat exchanger fan 19, the high stage side pump 22, the low stage side flow rate adjusting valve 31, and the low stage They are the side pump 33, the heat generating device 34, the flow control valve 35, the low stage radiator blower 36, the air conditioning blower 42 and the like.
  • the control device 50 is integrally configured with a control unit that controls various control target devices connected to the output side.
  • operation of each control object apparatus among the control apparatuses 50 comprises the control part which controls the action
  • the configuration for controlling the refrigerant discharge capacity of the compressor 11 in the control device 50 is a discharge capacity control unit 50a.
  • the configuration for controlling the heat generation amount of the heat generation device 34 is a heat generation amount control unit 50b.
  • operation of the flow regulating valve 35 among the control apparatuses 50 is the flow control part 50c.
  • control sensor groups such as an inside air temperature sensor 51, an outside air temperature sensor 52, a solar radiation amount sensor 53, and an outdoor heat exchanger temperature sensor 54 are connected to the input side of the control device 50.
  • the inside air temperature sensor 51 detects a vehicle interior temperature Tr.
  • the outside air temperature sensor 52 detects an outside air temperature Tam.
  • the solar radiation amount sensor 53 detects the solar radiation amount Ts in the vehicle compartment.
  • the outdoor heat exchanger temperature sensor 54 detects the temperature of the refrigerant flowing in the external evaporator 18.
  • the controller 50 determines whether frosting has occurred in the external evaporator 18 or whether the operating condition is such that frosting can occur in the external evaporator 18 (hereinafter, the frosting on the external evaporator 18 is merely (Abbreviated to occur) is included in the frost formation determination unit 50d.
  • the frost formation determining unit 50d is configured such that, for example, the refrigerant evaporation temperature in the external evaporator 18 is predetermined based on the temperature of the refrigerant flowing in the external evaporator 18 detected by the outdoor heat exchanger temperature sensor 54. When the temperature falls below, it is determined that frost is formed on the external evaporator 18.
  • An operation unit 60 is connected to the input side of the control device 50.
  • the operating unit 60 is operated by the occupant.
  • the operation unit 60 is disposed in the vicinity of an instrument panel at the front of the vehicle interior.
  • An operation signal from the operation unit 60 is input to the control device 50.
  • the operation unit 60 is provided with an air conditioner switch, a temperature setting switch, and the like.
  • the air conditioner switch sets whether to cool the blowing air in the indoor air conditioning unit.
  • the temperature setting switch sets the set temperature of the vehicle interior.
  • the control device 50 calculates the target blowout temperature TAO of the air to be blown into the vehicle compartment based on the detection signal detected by the control sensor group and the operation signal from the operation unit 60, and the operation mode of the air conditioner 1 The first to third heating modes and the defrosting operation mode are determined. Each operation mode will be described below.
  • the first heating mode is an operation mode in which the blown air is heated by the heater core 23.
  • the control device 50 determines the operation states (control signals to be output to various control devices) of various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 50 operates the compressor 11, the high-stage pump 22, the outdoor heat exchanger blower 19, the low-stage pump 33, the heating device 34, and the low-stage radiator blower 36.
  • the controller 50 determines a control signal to be output to the pressure reducing valve 13 such that the throttle opening degree of the first heating mode set in advance is obtained.
  • the flow rate control unit 50 c controls the operation of the flow rate adjustment valve 35 so that the entire amount of the cooling water discharged by the low-stage pump 33 and heated by the heat generating device 34 flows into the heat medium evaporator 15.
  • the heat generation amount control unit 50b is configured such that the temperature of the air blown into the vehicle compartment does not reach the target blowing temperature TAO, or the number of revolutions of the compressor 11 is a preset rotation preset from the durability of the compressor 11. When the number is reached, or when the power consumption of the compressor 11 exceeds a predetermined value, the heat generating device 34 is operated. The heat generation amount control unit 50b controls the heat generation amount of the heat generating device 34 such that the blowing air blown into the vehicle compartment has the target blowing temperature TAO.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the high-pressure refrigerant flowing into the condenser 12 exchanges heat with the cooling water and condenses. At this time, the heat of the high pressure refrigerant is dissipated to the cooling water, and the cooling water is heated. Then, the cooling water heated by the condenser 12 and the blowing air are heat-exchanged by the heater core 23 to heat the blowing air.
  • the high pressure refrigerant flowing out of the condenser 12 is reduced in pressure by the pressure reducing valve 13 to be a low pressure refrigerant.
  • the low pressure refrigerant reduced in pressure by the pressure reducing valve 13 flows into the heat medium evaporator 15 and the external evaporator 18.
  • the low-pressure refrigerant flowing into the heat medium evaporator 15 absorbs heat from the cooling water circulating in the low-stage side heat medium circulation circuit 30 and is evaporated.
  • the cooling water circulating in the low-stage heat medium circulation circuit 30 is cooled.
  • the low pressure refrigerant flowing into the external evaporator 18 absorbs heat from the outside air and evaporates.
  • the low stage side flow rate adjustment valve 31 causes the cooling water to flow into the low stage side radiator 32. Therefore, the cooling water cooled by the heat medium evaporator 15 exchanges heat with the outside air in the low-stage radiator 32, absorbs heat, and is heated.
  • the cooling water flowing out of the low-stage radiator 32 is drawn into the low-stage pump 33.
  • the cooling water pressure-fed from the low-stage pump 33 is heated by the heat generating device 34 and flows into the heat medium evaporator 15 through the flow control valve 35.
  • the heat medium evaporator 15 the coolant and the cooling water heated by the heat generating device 34 exchange heat, and the refrigerant evaporates.
  • the refrigerant absorbs heat generated by the heat generating device 34 via the cooling water.
  • the refrigerant flowing out of the heat medium evaporator 15 flows into the accumulator 16 to be separated into gas and liquid.
  • the gas phase refrigerant separated by the accumulator 16 is sucked into the compressor 11 and compressed again.
  • the blowing air heated by the heater core 23 can be blown into the vehicle compartment. Thereby, heating of the vehicle interior can be realized.
  • the refrigerant condensation temperature in the condenser 12 is reduced by the compression work of the compressor 11, The temperature of the cooling water circulating through the circulation circuit 30 can be raised. Therefore, the blowing air can be heated in a temperature zone higher than the second heating mode described below.
  • the second heating mode is an operation mode in which the second heat exchanger 39 heats the blown air.
  • the control device 50 determines the operation states (control signals to be output to the various control devices) of the various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 50 operates the low-stage pump 33 and the heating device 34. In the second heating mode, the control device 50 stops the compressor 11, the high stage pump 22, the outdoor heat exchanger blower 19, and the low stage radiator blower 36.
  • the flow rate control unit 50 c controls the flow rate adjusting valve 35 so that the entire amount of the cooling water discharged by the low-stage pump 33 and heated by the heat generating device 34 flows into the second heat exchanger 39.
  • the heat generation amount control unit 50b controls the heat generation amount of the heat generating device 34 such that the blowing air blown into the vehicle compartment has the target blowing temperature TAO.
  • the entire amount of the cooling water discharged by the low-stage pump 33 and heated by the heat generator 34 flows into the second heat exchanger 39. Accordingly, the cooling water heated by the heat generating device 34 and the blowing air are heat-exchanged in the second heat exchanger 39, and the blowing air is heated.
  • the blown air heated by the second heat exchanger 39 can be blown into the vehicle compartment. Thereby, heating of the vehicle interior can be realized.
  • the third heating mode is an operation mode in which the blown air heated by the second heat exchanger 39 is heated by the heater core 23. In other words, this is an operation mode in which the blown air is heated stepwise by the second heat exchanger 39 and the heater core 23.
  • the control device 50 determines the operation states (control signals to be output to various control devices) of various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 50 operates the compressor 11, the outdoor heat exchanger blower 19, the high-stage pump 22, the low-stage pump 33, the heat generator 34, and the low-stage radiator blower 36. The control device 50 determines a control signal to be output to the pressure reducing valve 13 so as to have the predetermined throttle opening degree in the third heating mode.
  • the flow rate control unit 50 c controls the flow rate adjustment valve 35 so that the cooling water heated by the heat generating device 34 flows into both the heat medium evaporator 15 and the second heat exchanger 39. Further, the flow rate control unit 50 c controls the flow rate adjustment valve 35 based on the operation state of the refrigeration cycle apparatus 10 and the target blowing temperature TAO, so that the cooling water heated by the heating device 34 is the heat medium evaporator 15. And the flow rate of the cooling water heated by the heating device 34 to the second heat exchanger 39.
  • the heat generation amount control unit 50b controls the heat generation amount of the heat generating device 34 such that the blowing air blown into the vehicle compartment has the target blowing temperature TAO.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the high pressure refrigerant flowing into the condenser 12 exchanges heat with the cooling water and condenses. At this time, the heat of the high pressure refrigerant is dissipated to the cooling water, and the cooling water is heated. Then, the cooling water heated by the condenser 12 and the blowing air are heat-exchanged by the heater core 23 to heat the blowing air.
  • the high pressure refrigerant flowing out of the condenser 12 is reduced in pressure by the pressure reducing valve 13 to be a low pressure refrigerant.
  • the low pressure refrigerant reduced in pressure by the pressure reducing valve 13 flows into the heat medium evaporator 15 and the external evaporator 18.
  • the low-pressure refrigerant flowing into the heat medium evaporator 15 absorbs heat from the cooling water circulating in the low-stage side heat medium circulation circuit 30 and is evaporated.
  • the cooling water circulating in the low-stage heat medium circulation circuit 30 is cooled.
  • the low pressure refrigerant flowing into the external evaporator 18 absorbs heat from the outside air and evaporates.
  • the low stage side flow rate adjustment valve 31 causes the cooling water to flow into the low stage side radiator 32. Therefore, the cooling water cooled by the heat medium evaporator 15 exchanges heat with the outside air in the low-stage radiator 32, absorbs heat, and is heated.
  • the cooling water that has flowed out of the low-stage radiator 32 is heated by the heating device 34 and flows into the heat medium evaporator 15 and the second heat exchanger 39.
  • the coolant and the cooling water heated by the heat generating device 34 exchange heat, and the refrigerant absorbs heat from the cooling water and evaporates.
  • the cooling water heated by the heat generating device 34 exchanges heat with the blowing air to heat the blowing air.
  • the refrigerant flowing out of the heat medium evaporator 15 flows into the accumulator 16 to be separated into gas and liquid.
  • the gas phase refrigerant separated by the accumulator 16 is sucked into the compressor 11 and compressed again.
  • the blowing air heated by the second heat exchanger 39 and the heater core 23 can be blown into the vehicle compartment. Thereby, heating of the vehicle interior can be realized.
  • the refrigerant condensation temperature in the condenser 12 is reduced by the compression work of the compressor 11, The temperature of the cooling water circulating through the circulation circuit 30 can be raised. Accordingly, the blown air can be heated stepwise in the order of the second heat exchanger 39 ⁇ the heater core 23.
  • the heat generation amount control unit 50 b increases the heat generation amount of the heat generation device 34 to increase the heat amount of the cooling water flowing into the heat medium evaporator 15. Thereby, in the heat medium evaporator 15, the heat absorption amount that the refrigerant absorbs heat from the cooling water increases, the refrigerant temperature rises, the frost is melted in the external evaporator 18, and the frost formation is suppressed.
  • the flow rate control unit 50 c reduces the number of revolutions of the compressor 11 to reduce the discharge capacity of the compressor 11. Thereby, the amount of heat absorption from the outside air of the refrigerant in the external evaporator 18 is reduced, and frost formation in the external evaporator 18 is suppressed.
  • the amount of heat absorption of the refrigerant from the cooling water increases and the temperature of the refrigerant rises, so the pressure of the high-pressure refrigerant decreases with the decrease of the discharge capacity of the compressor 11. It is suppressed and the fall of the heating capability of the air conditioner 1 at the time of a defrost operation mode is suppressed.
  • the flow rate control unit 50 c controls the operation of the flow rate adjustment valve 35 so that the cooling water heated by the heat generating device 34 flows into the heat medium evaporator 15.
  • the operation of the flow control valve 35 is controlled so that the cooling water heated by the heating device 34 flows into the second heat exchanger 39.
  • the heat contained in the cooling water heated by the heat generating device 34 is absorbed by the refrigerant by the heat medium evaporator 15, and the heat absorbed by the refrigerant flows into the heater core 23 as a heat source
  • the cooling water can be heated.
  • the blown air can be heated by the heater core 23.
  • the second heating mode the blown air can be heated by the second heat exchanger 39 by using the heat of the cooling water heated by the heat generating device 34 as a heat source.
  • the low pressure side refrigerant absorbs heat of the cooling water circulating through the low stage side heat medium circulation circuit 30, so if the heat absorption amount of the low pressure side refrigerant increases, the high pressure side The pressure of the refrigerant may be unnecessarily increased. As described above, if the pressure of the refrigerant on the high pressure side unnecessarily increases, the durability life of the components of the refrigeration cycle apparatus 10 is adversely affected.
  • the refrigeration cycle apparatus 10 of the present embodiment in the state of being operated in the first heating mode, the amount of heat generation of the heat generating device 34 increases, and the pressure of the refrigerant discharged from the compressor 11 Can be switched from the first heating mode to the second heating mode at the time of an operating condition that may increase unnecessarily.
  • the pressure of the refrigerant on the high pressure side of the refrigeration cycle apparatus 10 can be reliably suppressed from being unnecessarily increased, and the heat generating device 34 is generated. Heat can be used effectively to heat the blast air.
  • the cooling heated by the heat generating device 34 can be performed by switching to the second heating mode.
  • the blown air can be heated by the second heat exchanger 39 using the heat of water as a heat source.
  • the flow rate control unit 50c of the present embodiment adjusts the flow rate so that the cooling water heated by the heat generating device 34 flows into both the heat medium evaporator 15 and the second heat exchanger 39.
  • the operation of the valve 35 is controlled.
  • the blown air can be heated by the second heat exchanger 39 as in the second heating mode, and furthermore, the blown air can be heated by the heater core 23 as in the first heating mode. More specifically, in the third heating mode, the blown air heated by the second heat exchanger 39 can be further heated by the heater core 23 with heat generated by the energy-efficient refrigeration cycle apparatus 10 as a heat source . Therefore, in the third heating mode, it is possible to achieve both the maintenance of the energy efficiency and the suppression of the decrease in the heating performance.
  • the calorific value of the heating device 34 increases, and the pressure of the refrigerant discharged from the compressor 11 unnecessarily increases. It is possible to switch from the first heating mode to the third heating mode at the time of an operating condition that may cause the failure.
  • the pressure of the refrigerant on the high pressure side of the refrigeration cycle apparatus 10 can be prevented from rising, and the temperature zone of the heated air is lowered. It can also be suppressed.
  • the first heat exchange unit 20 of the refrigeration cycle apparatus 10 of the present embodiment includes the high-stage heat medium circulation circuit 21 for circulating the cooling water, the condenser 12 for heat exchange between the high pressure refrigerant and the cooling water, and the cooling And a heater core 23 for exchanging heat between the water and the blowing air.
  • the heater core 23 the cooling water circulating in the high-stage-side heat medium circulation circuit 21 and the blowing air are heat-exchanged, and the blowing air can be heated.
  • the flow rate adjustment valve 35 is configured such that the entire amount of the cooling water flows into the second heat exchanger 39 when it is not energized. Thereby, for example, even if the flow control valve 35 is stuck due to freezing or the like, the switched air can be heated by the second heat exchanger 39 by switching the operation mode to the second heating mode. The room can be heated.
  • the heat generation amount control unit 50b increases the heat generation amount in the heat generation device 34 when the frost formation determination unit 50d determines the frost formation in the external evaporator 18.
  • the heat absorption amount that the refrigerant absorbs heat from the cooling water increases, the refrigerant temperature rises, and frost can be melted in the external evaporator 18, and frost formation in the external evaporator 18 Can be suppressed.
  • control device 50 reduces the number of rotations of the compressor 11 when the frost formation determination unit 50 d determines the formation of frost on the external evaporator 18. Thereby, the amount of heat absorption from the outside air of the refrigerant in the external evaporator 18 is reduced, and frost formation in the external evaporator 18 can be suppressed.
  • the air conditioner 2 of the second embodiment adds an indoor condenser 25 to the air conditioner 1 of the first embodiment, and the condenser 12, the high stage side heat medium circulation circuit 21, the high stage side pump 22, and The heater core 23 is eliminated.
  • the indoor condenser 25 is a first heat exchange unit 20 that uses the high pressure refrigerant discharged from the compressor 11 as a heat source to heat the blowing air.
  • the indoor condenser 25 is disposed in the casing 41 at the downstream side of the second heat exchanger 39.
  • the indoor condenser 25 exchanges heat between the high pressure refrigerant discharged from the compressor 11 and the blowing air, dissipates the heat of the high pressure refrigerant to the blowing air, and heats the blowing air.
  • the blown air is directly heated in the indoor condenser 25 by the heat possessed by the high-pressure refrigerant. According to this, compared with the structure which heats a blowing air with the heat
  • the air conditioner 3 of the third embodiment adds a first pressure reducing valve 55, a second pressure reducing valve 56, a first connection flow path 65, and a second connection flow path 66 to the air conditioning device 1 of the first embodiment.
  • the pressure reducing valve 13, the second heat exchanger flow path 38 and the second heat exchanger 39 are eliminated.
  • the first pressure reducing valve 55 and the second pressure reducing valve 56 are pressure reducers that decompress and expand the liquid phase refrigerant flowing out of the condenser 12. That is, the first pressure reducing valve 55 and the second pressure reducing valve 56 reduce the pressure of the refrigerant on the downstream side of the condenser 12.
  • the low pressure refrigerant reduced by the first pressure reducing valve 55 flows into the heat medium evaporator 15.
  • the low pressure refrigerant reduced by the second pressure reducing valve 56 flows into the external evaporator 18.
  • the first pressure reducing valve 55 and the second pressure reducing valve 56 are electric variable throttle mechanisms whose operations are controlled by a control signal output from the control device 50, and have a valve body and an electric actuator.
  • the valve body is configured to be capable of changing the passage opening degree of the refrigerant passage (in other words, the throttle opening degree).
  • the electric actuator has a stepping motor that changes the throttle opening of the valve body.
  • the first connection flow path 65 connects the flow rate adjustment valve 35 and the high-stage heat medium circulation circuit 21 on the upstream side of the heater core 23.
  • the first connection flow path 65 is a flow path for leading the cooling water of the low-stage heat medium circulation circuit 30 to the high-stage heat medium circulation circuit 21.
  • the second connection flow path 66 connects the high stage side heat medium circulation circuit 21 downstream of the heater core 23 and the high stage side pump 22 and the low stage side heat medium circulation circuit 30 upstream of the low stage side pump 33 doing.
  • the flow rate adjustment valve 35 is configured such that the flow rate of the cooling water heated by the heating device 34 flows into the heat medium evaporator 15 and the cooling water heated by the heating device 34 This flow rate adjustment unit adjusts the flow rate flowing into the heater core 23 via the 1 connection flow path 65.
  • the flow rate adjustment valve 35 can cause the entire amount of cooling water heated by the heat generating device 34 to flow into the heat medium evaporator 15 and can cause the entire amount of cooling water to flow into the heater core 23.
  • the flow rate adjustment valve 35 is configured such that the entire amount of cooling water flows into the heater core 23 when not energized.
  • the control device 50 calculates the target blowout temperature TAO of the air to be blown into the vehicle compartment based on the detection signal detected by the control sensor group and the operation signal from the operation unit 60, and the operation mode of the air conditioner 1
  • the system determines one of the refrigeration cycle heating mode, the heat source heating mode, the refrigeration cycle heat source heating mode, and the defrosting operation mode. Each operation mode will be described below.
  • the refrigeration cycle heating mode is an operation mode in which the blowing air is heated by using the cooling water heated by the condenser 12 as a heat source.
  • the control device 50 determines the operation states (control signals to be output to various control devices) of various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 50 operates the compressor 11, the high-stage pump 22, the low-stage pump 33, the heat generator 34, and the low-stage radiator blower 36.
  • the control device 50 determines control signals to be output to the first pressure reducing valve 55 and the second pressure reducing valve 56 so that the throttle opening degree of the predetermined refrigeration cycle heating mode is obtained.
  • the flow rate control unit 50 c controls the operation of the flow rate adjustment valve 35 so that the entire amount of cooling water discharged by the low-stage pump 33 and heated by the heat generating device 34 flows into the heat medium evaporator 15.
  • the calorific value control unit 50b does not meet the case where the temperature of the blown air blown into the vehicle compartment reaches the target blowing temperature TAO, or the rotation speed of the compressor 11 is
  • the heating device 34 is operated when, for example, the motor 11 has reached a predetermined rotational speed set in advance from the durability of the compressor 11, or when the power consumption of the compressor 11 exceeds a predetermined value.
  • the heat generation amount control unit 50b controls the heat generation amount of the heat generating device 34 such that the blowing air blown into the vehicle compartment has the target blowing temperature TAO.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the high-pressure refrigerant flowing into the condenser 12 exchanges heat with the cooling water and condenses. At this time, the heat of the high pressure refrigerant is dissipated to the cooling water, and the cooling water is heated. Then, the cooling water heated by the condenser 12 and the blowing air are heat-exchanged by the heater core 23 to heat the blowing air.
  • the high pressure refrigerant flowing out of the condenser 12 is reduced in pressure by the first pressure reducing valve 55 and the second pressure reducing valve 56 to be a low pressure refrigerant.
  • the low pressure refrigerant reduced in pressure by the first pressure reducing valve 55 flows into the heat medium evaporator 15.
  • the low-pressure refrigerant flowing into the heat medium evaporator 15 absorbs heat from the cooling water circulating in the low-stage side heat medium circulation circuit 30 and is evaporated. Thus, the cooling water circulating in the low-stage heat medium circulation circuit 30 is cooled.
  • the low pressure refrigerant is depressurized by the second pressure reducing valve 56 and flows into the external evaporator 18.
  • the low pressure refrigerant flowing into the external evaporator 18 absorbs heat from the outside air and evaporates.
  • the lower stage flow rate adjustment valve 31 causes the cooling water to flow into the lower stage radiator 32. Therefore, the cooling water cooled by the heat medium evaporator 15 exchanges heat with the outside air in the low-stage radiator 32, absorbs heat, and is heated.
  • the cooling water flowing out of the low-stage radiator 32 is drawn into the low-stage pump 33.
  • the cooling water pressure-fed from the low-stage pump 33 is heated by the heat generating device 34 and flows into the heat medium evaporator 15 through the flow control valve 35.
  • the heat medium evaporator 15 the coolant and the cooling water heated by the heat generating device 34 exchange heat, and the refrigerant evaporates.
  • the refrigerant absorbs heat generated by the heat generating device 34 via the cooling water.
  • the refrigerant flowing out of the heat medium evaporator 15 flows into the accumulator 16 to be separated into gas and liquid.
  • the gas phase refrigerant separated by the accumulator 16 is sucked into the compressor 11 and compressed again.
  • the blowing air heated by the heater core 23 can be blown into the vehicle compartment. Thereby, heating of the vehicle interior can be realized.
  • the refrigerant condenses the refrigerant condensation temperature in the condenser 12 by the compression work of the compressor 11 in addition to the heat absorbed by the refrigerant from the cooling water heated by the heat generating device 34.
  • the temperature of the cooling water circulating through the circulation circuit 30 can be raised. Therefore, the blowing air can be heated in a temperature zone higher than the heat source heating mode described below.
  • the heat source heating mode is an operation mode in which the blowing air is heated using the cooling water heated by the heat generating device 34 as a heat source.
  • the control device 50 determines the operation state (control signal to be output to various control devices) of various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 50 operates the low-stage pump 33 and the heating device 34. In the heat source heating mode, the control device 50 stops the compressor 11, the high stage pump 22, the outdoor heat exchanger blower 19, and the low stage radiator blower 36.
  • the flow rate control unit 50 c controls the flow rate adjusting valve 35 so that the entire amount of cooling water discharged by the low-stage pump 33 and heated by the heat generating device 34 flows into the heater core 23 via the first connection flow path 65. Do.
  • the heat generation amount control unit 50b controls the heat generation amount of the heat generating device 34 such that the blowing air blown into the vehicle compartment has the target blowing temperature TAO.
  • the entire amount of cooling water discharged by the low-stage pump 33 and heated by the heat generator 34 flows into the heater core 23.
  • the cooling water heated by the heat generating device 34 and the blowing air are heat-exchanged by the heater core 23 to heat the blowing air.
  • the blowing air heated by the heater core 23 can be blown into the vehicle compartment. Thereby, heating of the vehicle interior can be realized.
  • the refrigeration cycle heat source heating mode is an operation mode in which the blowing air is heated using the cooling water heated by the condenser 12 and the cooling water heated by the heating device 34 as a heat source.
  • the control device 50 determines the operation states (control signals to be output to various control devices) of various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 50 operates the compressor 11, the high-stage pump 22, the low-stage pump 33, the heat generator 34, and the low-stage radiator blower 36.
  • the control device 50 determines control signals to be output to the first pressure reducing valve 55 and the second pressure reducing valve 56 such that the throttle opening degree of the predetermined refrigeration cycle heat source heating mode is obtained.
  • the flow rate control unit 50 c controls the flow rate adjustment valve 35 so that the cooling water heated by the heat generating device 34 flows into both the heat medium evaporator 15 and the heater core 23. Further, the flow rate control unit 50 c controls the flow rate adjustment valve 35 based on the operation state of the refrigeration cycle apparatus 10 and the target blowing temperature TAO, so that the cooling water heated by the heating device 34 is the heat medium evaporator 15. And the flow rate of the cooling water heated by the heating device 34 into the heater core 23.
  • the heat generation amount control unit 50b controls the heat generation amount of the heat generating device 34 such that the blowing air blown into the vehicle compartment has the target blowing temperature TAO.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the high-pressure refrigerant flowing into the condenser 12 exchanges heat with the cooling water and condenses. At this time, the heat of the high pressure refrigerant is dissipated to the cooling water, and the cooling water is heated. Then, the cooling water heated by the condenser 12 and the blowing air are heat-exchanged by the heater core 23 to heat the blowing air.
  • the high pressure refrigerant flowing out of the condenser 12 is reduced in pressure by the first pressure reducing valve 55 and the second pressure reducing valve 56 to be a low pressure refrigerant.
  • the low pressure refrigerant reduced in pressure by the first pressure reducing valve 55 flows into the heat medium evaporator 15.
  • the low-pressure refrigerant flowing into the heat medium evaporator 15 absorbs heat from the cooling water circulating in the low-stage side heat medium circulation circuit 30 and is evaporated. Thus, the cooling water circulating in the low-stage heat medium circulation circuit 30 is cooled.
  • the low pressure refrigerant is depressurized by the second pressure reducing valve 56 and flows into the external evaporator 18.
  • the low pressure refrigerant flowing into the external evaporator 18 absorbs heat from the outside air and evaporates.
  • the low stage side flow rate adjustment valve 31 causes the cooling water to flow into the low stage side radiator 32. Therefore, the cooling water cooled by the heat medium evaporator 15 exchanges heat with the outside air in the low-stage radiator 32, absorbs heat, and is heated.
  • the cooling water which has flowed out of the low-stage radiator 32 is heated by the heat generating device 34 and flows into the heat medium evaporator 15 and the heater core 23.
  • the cooling water heated by the heat generating device 34 exchanges heat with the refrigerant in the heat medium evaporator 15, and the refrigerant is heated.
  • the heat generating device 34 heats the refrigerant.
  • the refrigerant flowing out of the heat medium evaporator 15 flows into the accumulator 16 to be separated into gas and liquid.
  • the gas phase refrigerant separated by the accumulator 16 is sucked into the compressor 11 and compressed again.
  • the blowing air heated by the heater core 23 can be blown out into the vehicle compartment. Thereby, heating of the vehicle interior can be realized.
  • the discharge capacity control unit 50 a reduces the rotation speed of the compressor 11 to reduce the discharge capacity of the compressor 11. Thereby, the amount of heat absorption from the outside air of the refrigerant in the external evaporator 18 is reduced, and frost formation in the external evaporator 18 is suppressed.
  • the flow rate control unit 50 c controls the flow rate adjustment valve 35 such that the amount of inflow to the heater core 23 of the cooling water heated by the heat generating device 34 is increased.
  • the heat generation amount control unit 50 b increases the heat generation amount of the heat generation device 34. Thereby, the amount of heat of the cooling water flowing into the heater core 23 is increased. For this reason, even if the amount of heat release to the cooling water in the condenser 12 decreases due to the decrease in the discharge capacity of the compressor 11, the decrease in the temperature of the cooling water flowing into the heater core 23 is suppressed, and the heating capacity of the air conditioner 3 Is maintained.
  • the flow rate control unit 50 c controls the operation of the flow rate adjustment valve 35 so that the cooling water heated by the heat generating device 34 flows into the heat medium evaporator 15.
  • the operation of the flow control valve 35 is controlled so that the cooling water heated by the heating device 34 flows into the heater core 23.
  • the heat of the cooling water heated by the heat generating device 34 is absorbed by the refrigerant by the heat medium evaporator 15, and the heat absorbed by the refrigerant flows into the heater core 23 as a heat source
  • the cooling water can be heated.
  • the heat exchange target fluid can be heated by the heater core 23.
  • the blown air can be heated by the heater core 23 using the heat of the cooling water heated by the heat generating device 34 as a heat source.
  • the cooling water heated by the heat generating device 34 can be switched by switching to the heat source heating mode.
  • the blown air can be heated by the heater core 23 using the heat of the heat source as a heat source.
  • the flow rate control unit 50c determines that the amount of inflow to the heater core 23 of the cooling water heated by the heating device 34 is The flow control valve 35 is controlled to increase.
  • the flow rate adjustment valve 35 is configured such that the entire amount of the cooling water flows into the heater core 23 when not energized. Thus, for example, even if the flow rate adjustment valve 35 is stuck due to freezing or the like, the blown air can be heated by the heater core 23 by executing the operation of the heat source heating mode, and heating of the vehicle interior can be reliably performed. It can be performed.
  • the air conditioner 4 of the fourth embodiment adds an outdoor heat exchanger 61, a first pressure reducing valve 62, a second pressure reducing valve 63, and an outdoor heat exchanger blower 64 to the air conditioner 1 of the first embodiment.
  • the refrigerant flow path adjusting valve 14, the external evaporator 18, and the outdoor heat exchanger blower 19 are eliminated.
  • the refrigeration cycle apparatus 10 of the air conditioner 4 includes the compressor 11, the condenser 12, the first pressure reducing valve 62 (first pressure reducing device), the outdoor heat exchanger 61, the second pressure reducing valve 63, and the heat medium evaporation. And an accumulator 16 (liquid reservoir).
  • the refrigerant inlet side of the first pressure reducing valve 62 is connected to the refrigerant outlet side of the condenser 12.
  • the first pressure reducing valve 62 is a first pressure reducing device that reduces the pressure and expands the liquid phase refrigerant flowing out of the condenser 12. That is, the first pressure reducing valve 62 reduces the pressure of the refrigerant downstream of the condenser 12.
  • the first pressure reducing valve 62 is configured as a variable throttle mechanism with a fully open function that functions as a simple refrigerant passage without exerting the refrigerant pressure reducing function by fully opening the throttle opening degree.
  • the first pressure reducing valve 62 is an electric variable throttle mechanism whose operation is controlled by a control signal output from the control device 50, and includes a valve body and an electric actuator.
  • the valve body is configured to be capable of changing the passage opening degree of the refrigerant passage (in other words, the throttle opening degree).
  • the refrigerant outlet side of the first pressure reducing valve 62 is connected to the refrigerant inlet side of the outdoor heat exchanger 61.
  • the outdoor heat exchanger 61 condenses the high pressure refrigerant by heat exchange between the high pressure refrigerant and the outside air blown by the outdoor heat exchanger blower 64 when the throttle opening degree of the first pressure reducing valve 62 is fully open. Can.
  • the outdoor heat exchanger 61 reduces the pressure of the low pressure medium reduced by the first pressure reducing valve 62 by the outdoor heat exchanger blower 64. Heat can be absorbed and evaporated by exchanging heat with the blown outside air.
  • the outdoor heat exchanger blower 64 is an electric blower that drives a fan by an electric motor, and its operation is controlled by a control signal output from the control device 50.
  • the outdoor heat exchanger 61 and the outdoor heat exchanger blower 64 are disposed forward in the vehicle bonnet. Therefore, the traveling wind can be applied to the outdoor heat exchanger blower 64 when the vehicle travels.
  • the refrigerant inlet side of the second pressure reducing valve 63 is connected to the refrigerant outlet side of the outdoor heat exchanger 61.
  • the second pressure reducing valve 63 is a second pressure reducing device that reduces and expands the liquid phase refrigerant flowing out of the outdoor heat exchanger 61. That is, the second pressure reducing valve 63 reduces the pressure of the refrigerant on the downstream side of the outdoor heat exchanger 61.
  • the second pressure reducing valve 63 is configured as a variable throttle mechanism with a fully open function that functions as a mere refrigerant passage without exerting the refrigerant pressure reducing function by fully opening the throttle opening degree.
  • the second pressure reducing valve 63 is an electric variable throttle mechanism whose operation is controlled by a control signal output from the control device 50, and includes a valve body and an electric actuator.
  • the valve body is configured to be capable of changing the passage opening degree of the refrigerant passage (in other words, the throttle opening degree).
  • the control device 50 calculates the target blowout temperature TAO of the air to be blown into the vehicle compartment based on the detection signal detected by the control sensor group and the operation signal from the operation unit 60, and the operation mode of the air conditioner 1 The first heating mode to the third heating mode, the defrosting operation mode, or the cooling mode is determined.
  • the control device 50 squeezes the opening degree of at least one of the first pressure reducing valve 62 and the second pressure reducing valve 63, and the outdoor heat exchanger 61 and the heat medium
  • the low pressure refrigerant exchanges heat with the outside air or cooling water, absorbs heat and evaporates.
  • the other operations are similar to the first heating mode to the third heating mode and the defrosting operation mode of the air conditioner 1 of the first embodiment.
  • the cooling mode is an operation mode in which the second heat exchanger 39 cools the blown air.
  • the control device 50 determines the operation states (control signals to be output to various control devices) of the various control target devices based on the detection signal and the target blowing temperature TAO and the like. Specifically, the control device 50 operates the compressor 11, the low-stage pump 33, and the outdoor heat exchanger blower 64. On the other hand, the control device 50 stops the high-stage pump 22 and the low-stage radiator blower 36 and stops the heat generation of the heat generator 34.
  • the control device 50 fully opens the throttle opening degree of the first pressure reducing valve 62 and determines a control signal to be output to the second pressure reducing valve 63 so as to attain the predetermined throttle opening degree of the cooling mode.
  • the flow rate control unit 50 c controls the operation of the flow rate adjustment valve 35 such that the cooling water discharged by the low-stage pump 33 flows into the heat medium evaporator 15 and the second heat exchanger 39.
  • the controller 50 is configured such that the flow rate of the cooling water flowing out of the heat medium evaporator 15 flows into the lower stage radiator 32 and the total amount of the cooling water flowing out of the heat medium evaporator 15 flows into the radiator bypass flow path 37. And control the operation of the low-stage flow rate adjustment valve 31
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12. Since the high-stage pump 22 is stopped, the high-pressure refrigerant flowing into the condenser 12 hardly exchanges heat with the cooling water. Therefore, the high pressure refrigerant flowing into the condenser 12 flows out with little condensation.
  • the high pressure refrigerant flowing out of the condenser 12 flows into the outdoor heat exchanger 61 without being reduced in pressure by the first pressure reducing valve 62.
  • the high-pressure refrigerant flowing into the outdoor heat exchanger 61 is condensed by heat exchange with the outside air blown by the outdoor heat exchanger blower 64.
  • the high pressure refrigerant flowing out of the outdoor heat exchanger 61 is reduced in pressure by the second pressure reducing valve 63 to be a low pressure refrigerant.
  • the low pressure refrigerant decompressed by the second pressure reducing valve 63 flows into the heat medium evaporator 15.
  • the low-pressure refrigerant flowing into the heat medium evaporator 15 absorbs heat from the cooling water circulating in the low-stage side heat medium circulation circuit 30 and is evaporated. Thus, the cooling water circulating in the low-stage heat medium circulation circuit 30 is cooled.
  • the lower stage flow rate adjustment valve 31 causes the coolant to flow into the radiator bypass flow path 37.
  • the cooling water cooled by the heat medium evaporator 15 is prevented from exchanging heat with the outside air at the low-stage radiator 32.
  • the cooling water that has flowed out of the low-stage radiator 32 and discharged by the low-stage pump 33 flows into the heat medium evaporator 15 and the second heat exchanger 39.
  • the cooling water cooled by the heat medium evaporator 15 exchanges heat with the blowing air in the second heat exchanger 39. Thereby, the blowing air is cooled.
  • the refrigerant flowing out of the heat medium evaporator 15 flows into the accumulator 16 to be separated into gas and liquid.
  • the gas phase refrigerant separated by the accumulator 16 is sucked into the compressor 11 and compressed again.
  • the blowing air cooled by the second heat exchanger 39 can be blown into the vehicle compartment. Thereby, cooling of the vehicle interior can be realized.
  • the air conditioner 5 of the fifth embodiment will be described below with reference to FIG. 6 in terms of differences from the air conditioner 1 of the first embodiment.
  • the air conditioner 5 of the fifth embodiment adds a first connection channel 71, a second connection channel 72, and an introduction amount adjustment valve 73 to the air conditioner 1 of the first embodiment.
  • the first connection flow path 71 connects the second heat exchange flow path 38 downstream of the flow rate adjustment valve 35 and the high-stage heat medium circulation circuit 21 upstream of the heater core 23.
  • the second connection flow path 72 is a flow path for leading the cooling water of the low-stage heat medium circulation circuit 30 to the high-stage heat medium circulation circuit 21.
  • the second connection flow path 72 connects the high stage side heat medium circulation circuit 21 downstream of the heater core 23 and the high stage side pump 22 and the low stage side heat medium circulation circuit 30 upstream of the low stage side pump 33 doing.
  • the introduction amount adjustment valve 73 is an introduction amount adjustment portion that adjusts the introduction amount of the cooling water introduced from the second heat exchange portion flow path 38 to the high-stage heat medium circulation circuit 21 via the first connection flow path 71. is there.
  • Software and hardware for controlling the operation of the introduction amount adjustment valve 73 in the control device 50 of the air conditioner 5 of the fifth embodiment are an introduction amount control unit 50e.
  • the control device 50 calculates the target blowout temperature TAO of the air to be blown into the vehicle compartment based on the detection signal detected by the control sensor group and the operation signal from the operation unit 60, and the operation mode of the air conditioner 1 The first to third heating modes and the defrosting operation mode are determined.
  • the first to third heating modes of the air conditioner 5 of the fifth embodiment are the same as the first to third heating modes of the air conditioner 1 of the first embodiment.
  • the discharge capacity control unit 50 a reduces the rotation speed of the compressor 11 to reduce the discharge capacity of the compressor 11.
  • the introduction amount control unit 50 e controls the introduction amount adjustment valve 73 so that the amount of introduction of the cooling water heated by the heat generating device 34 into the heater core 23 is increased.
  • the heat generation amount control unit 50 b increases the heat generation amount of the heat generation device 34.
  • the discharge capacity control unit 50a reduces the number of rotations of the compressor 11, and the compressor Reduce the 11 discharge capacity. Thereby, the amount of heat absorption from the outside air of the refrigerant in the external evaporator 18 is reduced, and frost formation in the external evaporator 18 is suppressed.
  • the introduction amount control unit 50e causes the amount of inflow to the heater core 23 of the cooling water heated by the heating device 34. Control the introduction amount adjustment valve 73 so as to increase.
  • a liquid storage part is not limited to this.
  • a receiver may be disposed downstream of the condenser 12 to separate the gas and liquid of the refrigerant flowing out of the outdoor condenser and store the excess liquid phase refrigerant.
  • the accumulator 16 and the receiver may be arranged at the same time.
  • Each component apparatus which comprises the refrigerating cycle apparatus 10 is not limited to what was disclosed by the above-mentioned embodiment.
  • the above-mentioned embodiment explained the example which adopted an electric compressor as compressor 11, when applied to a vehicle travel engine, the vehicle travels via a pulley, a belt, etc. as compressor 11.
  • An engine driven compressor driven by a rotational driving force transmitted from an engine may be employed.
  • the heat generating device 34 is an electric heater such as a PTC heater.
  • the heat generating device 34 may be an on-vehicle device that generates heat when activated.
  • a battery, an inverter which is a frequency conversion unit, and a traveling electric motor for outputting a driving force for traveling can be adopted. These on-vehicle devices are cooled by radiating heat to the cooling water of the low-stage heat medium circulation circuit 30.
  • the outside temperature Tam detected by the outside air temperature sensor 52 is 0 ° C. or less, and further, the outside detected by the outdoor heat exchanger temperature sensor 54 from the outside temperature Tam.
  • the refrigerant flow path adjusting valve 14 From the air conditioner 1 of the first embodiment, the air conditioner 2 of the second embodiment, the air conditioner 3 of the third embodiment, and the air conditioner 5 of the fifth embodiment, the refrigerant flow path adjusting valve 14, An embodiment in which the external evaporator 18 and the outdoor heat exchanger blower 19 are eliminated may be used.
  • the first connection channel 71, the second connection channel 72, and the introduction amount adjustment valve 73 may be added to the air conditioner 4 of the fourth embodiment described in the air conditioner 5 of the fifth embodiment.
  • an outdoor condenser may be provided downstream of the indoor condenser 25 so that the high pressure refrigerant flowing out of the indoor condenser 25 exchanges heat with the outside air and condenses.
  • the high pressure refrigerant flowing out of the indoor condenser 25 exchanges heat with the outside air, condenses, and excess heat of the high pressure refrigerant is outside air. Exhausted.
  • the refrigerant flow path adjusting valve 14 and the external evaporator 18 may be added to execute the defrosting operation mode described in the air conditioner 1 of the first embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
PCT/JP2018/025839 2017-08-10 2018-07-09 冷凍サイクル装置 Ceased WO2019031131A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201880050700.8A CN110998198B (zh) 2017-08-10 2018-07-09 制冷循环装置
DE112018004104.2T DE112018004104T5 (de) 2017-08-10 2018-07-09 Kühlkreislaufvorrichtung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-155679 2017-08-10
JP2017155679A JP6733625B2 (ja) 2017-08-10 2017-08-10 冷凍サイクル装置

Publications (1)

Publication Number Publication Date
WO2019031131A1 true WO2019031131A1 (ja) 2019-02-14

Family

ID=65272237

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/025839 Ceased WO2019031131A1 (ja) 2017-08-10 2018-07-09 冷凍サイクル装置

Country Status (4)

Country Link
JP (1) JP6733625B2 (https=)
CN (1) CN110998198B (https=)
DE (1) DE112018004104T5 (https=)
WO (1) WO2019031131A1 (https=)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11724570B2 (en) * 2020-03-10 2023-08-15 Toyota Jidosha Kabushiki Kaisha Vehicle-mounted temperature control system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3163899A1 (fr) * 2024-06-28 2026-01-02 Valeo Systemes Thermiques Système de conditionnement thermique

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010260449A (ja) * 2009-05-07 2010-11-18 Nippon Soken Inc 車両用空調装置
JP2012181005A (ja) * 2011-02-11 2012-09-20 Denso Corp ヒートポンプサイクル
JP2012232730A (ja) * 2011-04-18 2012-11-29 Denso Corp 車両用温度調整装置、および車載用熱システム
WO2017038677A1 (ja) * 2015-08-28 2017-03-09 株式会社デンソー 空調システム
JP2017081560A (ja) * 2016-12-21 2017-05-18 パナソニックＩｐマネジメント株式会社 車両用空調装置の構成ユニット

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6201434B2 (ja) 2012-07-18 2017-09-27 株式会社デンソー 冷凍サイクル装置
JP6304578B2 (ja) * 2013-03-06 2018-04-04 パナソニックＩｐマネジメント株式会社 車両用空調装置
JP6277888B2 (ja) * 2014-06-27 2018-02-14 株式会社デンソー 冷凍サイクル装置
JP6278049B2 (ja) 2016-03-03 2018-02-14 マツダ株式会社 エンジンのオイル供給装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010260449A (ja) * 2009-05-07 2010-11-18 Nippon Soken Inc 車両用空調装置
JP2012181005A (ja) * 2011-02-11 2012-09-20 Denso Corp ヒートポンプサイクル
JP2012232730A (ja) * 2011-04-18 2012-11-29 Denso Corp 車両用温度調整装置、および車載用熱システム
WO2017038677A1 (ja) * 2015-08-28 2017-03-09 株式会社デンソー 空調システム
JP2017081560A (ja) * 2016-12-21 2017-05-18 パナソニックＩｐマネジメント株式会社 車両用空調装置の構成ユニット

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11724570B2 (en) * 2020-03-10 2023-08-15 Toyota Jidosha Kabushiki Kaisha Vehicle-mounted temperature control system
US12083862B2 (en) 2020-03-10 2024-09-10 Toyota Jidosha Kabushiki Kaisha Vehicle-mounted temperature control system

Also Published As

Publication number Publication date
JP2019035520A (ja) 2019-03-07
DE112018004104T5 (de) 2020-05-20
JP6733625B2 (ja) 2020-08-05
CN110998198A (zh) 2020-04-10
CN110998198B (zh) 2021-09-14

Similar Documents

Publication Publication Date Title
US12344075B2 (en) Battery heating device for vehicle
US11186141B2 (en) Vehicle-mounted temperature controller
US11180000B2 (en) Vehicle-mounted temperature controller
US11413931B2 (en) Vehicle-mounted temperature controller
JP6708099B2 (ja) 冷凍サイクル装置
JP6884028B2 (ja) 車両用空気調和装置
JP6015636B2 (ja) ヒートポンプシステム
US20190111756A1 (en) Refrigeration cycle device
JP5799924B2 (ja) 冷凍サイクル装置
CN104853942B (zh) 车辆用空调装置
US10899198B2 (en) Air conditioner for vehicle
CN110997369B (zh) 制冷循环装置
JP2013217631A (ja) 冷凍サイクル装置
US11241930B2 (en) Vehicle-mounted temperature controller
JP2014228190A (ja) 冷凍サイクル装置
WO2017104588A1 (ja) 車両用空気調和装置
JP6963405B2 (ja) 車両用空気調和装置
JP2020142789A (ja) 熱管理システム
CN107735626A (zh) 车用空调装置
JP2013203221A (ja) 車両用の空調装置
JP7655710B2 (ja) 空調装置
WO2019065013A1 (ja) 冷凍サイクル装置
CN110998209A (zh) 复合型热交换器
WO2019031131A1 (ja) 冷凍サイクル装置
CN114025977B (zh) 制冷循环装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18844871

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 18844871

Country of ref document: EP

Kind code of ref document: A1