WO2019044353A1 - 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
WO2019044353A1
WO2019044353A1 PCT/JP2018/028966 JP2018028966W WO2019044353A1 WO 2019044353 A1 WO2019044353 A1 WO 2019044353A1 JP 2018028966 W JP2018028966 W JP 2018028966W WO 2019044353 A1 WO2019044353 A1 WO 2019044353A1
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WIPO (PCT)
Prior art keywords
refrigerant
heat
cooling
pressure
evaporator
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/JP2018/028966
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English (en)
French (fr)
Japanese (ja)
Inventor
直也 牧本
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 DE112018004831.4T priority Critical patent/DE112018004831T5/de
Priority to CN201880055683.7A priority patent/CN111065866A/zh
Publication of WO2019044353A1 publication Critical patent/WO2019044353A1/ja
Priority to US16/799,467 priority patent/US11787258B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00914—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is a bypass of the condenser
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00007—Combined heating, ventilating, or cooling devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00885—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 [HVAC] devices
    • B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • B60H1/3214—Control means therefor for improving the lubrication of a refrigerant compressor in a vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, evaporator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
    • B60H1/32281—Cooling devices using compression characterised by refrigerant circuit configurations comprising a single secondary circuit, e.g. at evaporator or 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • 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 [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3248—Cooling devices information from a variable is obtained related to pressure
    • B60H2001/325—Cooling devices information from a variable is obtained related to pressure of the refrigerant at a compressing unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
    • B60H2001/3263—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 [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3269—Cooling devices output of a control signal
    • B60H2001/328—Cooling devices output of a control signal related to an evaporating unit
    • B60H2001/3283—Cooling devices output of a control signal related to an evaporating unit to control the refrigerant flow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3269—Cooling devices output of a control signal
    • B60H2001/3285—Cooling devices output of a control signal related to an expansion unit

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus and is effective when applied to an air conditioner.
  • Patent Document 1 discloses a vapor compression refrigeration cycle apparatus applied to a vehicle air conditioner.
  • the refrigeration cycle apparatus of Patent Document 1 includes a refrigerant circuit in a cooling mode that cools air blown into a vehicle compartment that is an air conditioning target space, a refrigerant circuit in a heating mode that heats blast air, and air that has been cooled and dehumidified. It is comprised so that switch of the refrigerant circuit of the dehumidification heating mode which reheats, etc. is possible.
  • the refrigeration cycle apparatus of Patent Document 1 includes a plurality of heat exchangers such as an indoor condenser, an outdoor heat exchanger, and an indoor evaporator.
  • the indoor condenser is a heat exchanger that exchanges heat between the high pressure refrigerant discharged from the compressor and the blowing air.
  • the outdoor heat exchanger is a heat exchanger that exchanges heat between the refrigerant and the outside air.
  • the indoor evaporator is a heat exchanger that exchanges heat between the low pressure refrigerant decompressed by the decompression unit and the blown air.
  • the outdoor heat exchanger functions as a radiator, and the indoor evaporator is switched to a refrigerant circuit functioning as an evaporator.
  • the indoor condenser functions as a radiator and the outdoor heat exchanger is switched to a refrigerant circuit functioning as an evaporator.
  • the indoor condenser functions as a radiator, and both the indoor evaporator and the outdoor heat exchanger are switched to a refrigerant circuit functioning as an evaporator.
  • Patent Document 1 a plurality of heat exchangers are provided, and according to the operation mode, the high pressure refrigerant is caused to flow into the same heat exchanger (in Patent Document 1, the outdoor heat exchanger)
  • the cycle configuration is likely to be complicated.
  • the state of the refrigerant on the outlet side of the heat exchanger functioning as the evaporator must be appropriately adjusted according to the operation mode.
  • the outlet of the heat exchanger in Patent Document 1, the indoor evaporator
  • the outdoor evaporator functioning as an evaporator so that the blowing air can be efficiently cooled by the latent heat of vaporization of the refrigerant. It is desirable to adjust the side refrigerant to be in the gas phase.
  • the refrigerant evaporation pressure in the heat exchanger (in Patent Document 1, the outdoor heat exchanger) functioning as an evaporator is lower than in the cooling mode, and the flow rate of the circulating refrigerant circulating in the cycle decreases. Refrigerant oil tends to stay in the outdoor heat exchanger. For this reason, in the heating mode, it is desirable to adjust the refrigerant on the outlet side of the outdoor heat exchanger to be in a gas-liquid two-phase state.
  • the refrigeration cycle apparatus configured to be able to switch the operation mode, not only is the cycle configuration easily complicated, but also the control mode of the pressure reducing portion disposed upstream of the refrigerant flow of the heat exchanger functioning as an evaporator is also complicated. It is easy to
  • the present disclosure properly adjusts the state of refrigerant on the outlet side of each evaporator without causing complication of the cycle configuration in a refrigeration cycle apparatus configured to be able to switch the operation mode, including a plurality of evaporators.
  • the aim is to provide a possible refrigeration cycle device.
  • a refrigeration cycle apparatus applied to an air conditioner includes, as a heat source, a heat of a refrigerant discharged from the compressor and a compressor that compresses and discharges a refrigerant mixed with refrigerant oil.
  • the refrigerant circuit can be switched. Specifically, the refrigerant can be made to flow into the cooling evaporator, and the refrigerant circuit can be switched to the operation mode in which the blowing air is cooled by the cooling evaporator. Further, the refrigerant is allowed to flow into the heat absorption evaporator without flowing the refrigerant into the cooling evaporator, and the air heated by the heating unit is heated using the heat absorbed from the heat source fluid by the heat absorption evaporator as a heat source The mode can be switched to the refrigerant circuit.
  • the circuit switching unit when the circuit switching unit is switching to a refrigerant circuit that does not allow the refrigerant to flow into the cooling evaporator, as in the operation mode of heating the blown air, and when a predetermined condition is satisfied. Adjusts the throttling degree of the heat absorbing decompressor so that the heat absorbing refrigerant is in a gas-liquid two-phase state. Therefore, even in the operation mode in which the flow rate of the circulating refrigerant that circulates the cycle is likely to decrease, such as the operation mode for heating the blown air, the refrigerant oil can be prevented from staying in the heat absorption evaporator. .
  • the circuit switching unit is switching to the refrigerant circuit that causes the refrigerant to flow into the cooling evaporator, cooling air is efficiently cooled by the cooling evaporator regardless of the throttle opening degree of the heat absorption reducing unit.
  • the pressure reducing portion for cooling can appropriately adjust the state of the refrigerant flowing out of the cooling evaporator.
  • a refrigeration cycle apparatus applied to an air conditioner includes, as a heat source, heat from a compressor that compresses and discharges a refrigerant mixed with refrigeration oil and the refrigerant discharged from the compressor.
  • a heating unit for heating the blown air a branching unit for branching the flow of high-pressure refrigerant flowing out of the heating unit, a cooling decompression unit for decompressing the refrigerant flowing out from one refrigerant outlet of the branching unit, and a cooling decompression unit
  • the heat absorption pressure reducing portion is an outlet of the internal heat exchanger when the circuit switching portion is switching to a refrigerant circuit that does not allow the refrigerant to flow into the cooling evaporator, and a predetermined condition is satisfied.
  • the throttle opening is adjusted so that the low pressure refrigerant on the side is in a gas-liquid two-phase state.
  • the refrigerant circuit in the operation mode for cooling the air and the refrigerant circuit in the operation mode for heating the air with a simple configuration without causing the complication of the cycle configuration It can be switched.
  • the circuit switching unit when the circuit switching unit is switching to a refrigerant circuit that does not allow the refrigerant to flow into the cooling evaporator, as in the operation mode of heating the blown air, and when a predetermined condition is satisfied. Adjusts the throttling degree of the heat absorbing pressure reducing portion so that the low pressure refrigerant on the outlet side of the internal heat exchanger is in a gas-liquid two-phase state. Therefore, even in the operation mode in which the flow rate of the circulating refrigerant that circulates the cycle is likely to decrease, such as the operation mode for heating the blown air, the refrigeration oil stagnates in the heat absorption evaporator and the internal heat exchanger Can be suppressed.
  • the circuit switching unit is switching to the refrigerant circuit that causes the refrigerant to flow into the cooling evaporator
  • cooling air is efficiently cooled by the cooling evaporator regardless of the throttle opening degree of the heat absorption reducing unit.
  • the cooling pressure reducing section can appropriately adjust the state of the refrigerant flowing out of the cooling evaporator.
  • the internal heat exchanger since the internal heat exchanger is provided, the enthalpy of the refrigerant flowing into the cooling evaporator or the heat absorption evaporator can be reduced. Therefore, the coefficient of performance of the refrigeration cycle apparatus can be improved.
  • a refrigeration cycle apparatus applied to an air conditioner includes, as a heat source, heat from a compressor that compresses and discharges a refrigerant mixed with refrigeration oil and refrigerant discharged from the compressor.
  • a heating unit for heating the blown air a branching unit for branching the flow of high-pressure refrigerant flowing out of the heating unit, a cooling decompression unit for decompressing the refrigerant flowing out from one refrigerant outlet of the branching unit, and a cooling decompression unit
  • the evaporator for cooling the refrigerant which has been depressurized in the heat exchange with the blast air and evaporates, the heat absorbing decompressor for decompressing the refrigerant flowing out from the other refrigerant outlet of the branching unit, and the heat absorbing decompressor A heat absorbing evaporator that causes the heat source fluid to exchange heat with the heat source fluid, and a circuit switching unit that switches between a refrigerant circuit that causes the refriger
  • a line indicating a change in heat absorption pressure of the heat absorption refrigerant corresponding to a change in heat absorption temperature of the heat absorption refrigerant on the outlet side of the heat absorption evaporator approaches a predetermined heat absorption characteristic line
  • the cooling characteristic line and the heat absorption characteristic line are different from each other. Furthermore, in the range where the temperature for cooling and the temperature for heat absorption are lower than a predetermined reference temperature, the pressure for heat absorption is higher than the pressure for cooling and the saturation pressure of the refrigerant.
  • the refrigerant circuit in the operation mode for cooling the air and the refrigerant circuit in the operation mode for heating the air with a simple configuration without causing the complication of the cycle configuration It can be switched.
  • the state of the cooling refrigerant and the state of the heat absorption refrigerant can be adjusted to appropriate states.
  • the heat absorption pressure is set to a value higher than the saturation pressure of the refrigerant by setting the heat absorption temperature to be lower than a predetermined reference temperature. be able to. That is, in the operation mode for heating the blowing air, the heat absorption refrigerant can be brought into a gas-liquid two-phase state.
  • the refrigerant oil can be prevented from staying in the heat absorption evaporator.
  • the cooling pressure reducing portion is connected to the cooling evaporator so that the blowing air can be efficiently cooled by the cooling evaporator regardless of the throttle opening of the heat absorption pressure reducing portion. It is possible to appropriately adjust the state of the refrigerant that has flowed out.
  • the refrigeration cycle apparatus applied to the air conditioner uses the heat of the refrigerant discharged from the compressor as a heat source as a heat source, and a compressor that compresses and discharges the refrigerant mixed with refrigerant oil.
  • a heating portion for heating air a branch portion for branching the flow of high-pressure refrigerant flowing out from the heating portion, a cooling decompression portion for decompressing the refrigerant flowing out from one refrigerant outlet of the branching portion, and a cooling decompression portion Of the refrigerant that has been depressurized by exchanging heat with the blast air and evaporating it, the heat absorption decompression section which decompresses the refrigerant flowing out from the other refrigerant outlet of the branching section, and the heat absorption decompression section.
  • Heat-exchanging the heat source fluid with the heat source fluid to evaporate, an internal heat exchanger for heat exchanging heat between the high pressure refrigerant and the low pressure refrigerant flowing out of the heat absorption evaporator, and causing the refrigerant to flow into the cooling evaporator Refrigerant circuit and evaporator for cooling Comprising a circuit switching unit for switching a refrigerant circuit which does not flow into the refrigerant, the.
  • a line indicating a change in the cooling pressure of the cooling refrigerant corresponding to a change in the cooling temperature of the cooling refrigerant on the outlet side of the cooling evaporator approaches a predetermined cooling characteristic line In addition, it is intended to change the aperture.
  • a line indicating a change in the low pressure side pressure of the low pressure refrigerant corresponding to a change of the low pressure side temperature of the low pressure refrigerant on the outlet side of the internal heat exchanger approaches a predetermined low pressure side characteristic line It is intended to change the throttle opening.
  • the cooling characteristic line and the low pressure side characteristic line are different from each other. Furthermore, in the range where the temperature for cooling and the temperature for heat absorption are lower than a predetermined reference temperature, the low pressure side pressure is higher than the pressure for cooling and the saturation pressure of the refrigerant.
  • the refrigerant circuit in the operation mode for cooling the air and the refrigerant circuit in the operation mode for heating the air with a simple configuration without causing the complication of the cycle configuration It can be switched.
  • the state of the cooling refrigerant and the state of the low pressure refrigerant can be adjusted to appropriate states.
  • the low pressure side pressure is set to a value higher than the saturation pressure of the refrigerant by setting the low pressure side temperature to be lower than a predetermined reference temperature.
  • the low pressure refrigerant can be brought into the gas-liquid two-phase state.
  • the cooling pressure reducing portion is connected to the cooling evaporator so that the blowing air can be efficiently cooled by the cooling evaporator regardless of the throttle opening of the heat absorption pressure reducing portion. It is possible to appropriately adjust the state of the refrigerant that has flowed out.
  • the internal heat exchanger since the internal heat exchanger is provided, the enthalpy of the refrigerant flowing into the cooling evaporator or the heat absorption evaporator can be reduced. Therefore, the coefficient of performance of the refrigeration cycle apparatus can be improved.
  • each heat exchanger such as a cooling evaporator, an endothermic evaporator, an internal heat exchanger, etc. does not mean only the refrigerant at the moment of passing through the refrigerant outlet of each heat exchanger.
  • the refrigerant on the outlet side of each heat exchanger includes the refrigerant just before flowing out from the refrigerant outlet of each heat exchanger, and the refrigerant immediately after flowing out from the refrigerant outlet of each heat exchanger.
  • the refrigeration cycle apparatus 10 of the present embodiment is applied to a vehicle air conditioner 1 mounted on an electric vehicle that obtains driving power for traveling a vehicle from a traveling electric motor.
  • the refrigeration cycle apparatus 10 has a function of adjusting the temperature of the blowing air blown into the vehicle compartment, which is a space to be air conditioned, in the vehicle air conditioner 1.
  • the cooling mode is an operation mode for cooling the inside of the vehicle by cooling the blown air.
  • the heating mode is an operation mode in which the blowing air is heated to heat the vehicle interior.
  • the dehumidifying and heating mode is an operation mode for reheating the cooled and dehumidified air to dehumidify and heat the passenger compartment.
  • the refrigeration cycle apparatus 10 can switch the refrigerant circuit according to each operation mode.
  • an HFC refrigerant (specifically, R134a) is employed as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured.
  • Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant.
  • PAG oil polyalkylene glycol oil
  • a portion of the refrigeration oil circulates in the cycle with the refrigerant.
  • each component which comprises the refrigerating-cycle apparatus 10 is demonstrated using the whole block diagram of FIG.
  • the compressor 11 sucks, compresses and discharges the refrigerant in the refrigeration cycle apparatus 10.
  • the compressor 11 is disposed in a vehicle bonnet.
  • the compressor 11 is an electric compressor which rotationally drives, by an electric motor, a fixed displacement type compression mechanism whose discharge displacement is fixed.
  • the rotation speed (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from an air conditioning control device 60 described later.
  • the outlet side of the compressor 11 is connected to the inlet side of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12.
  • the high temperature side water-refrigerant heat exchanger 12 performs heat exchange between the high pressure refrigerant discharged from the compressor 11 and the high temperature side heat medium circulating in the high temperature side heat medium circuit 20 to heat the high temperature side heat medium. It is As the high temperature side heat medium, a solution containing ethylene glycol, an antifreeze liquid, etc. can be adopted.
  • the high temperature side heat medium circuit 20 is a high temperature side water circuit that circulates the high temperature side heat medium.
  • the water passage of the high temperature side water-refrigerant heat exchanger 12, the high temperature side heat medium pump 21, the heater core 22, the high temperature side radiator 23, the high temperature side flow rate adjustment valve 24 and the like are arranged.
  • the high temperature side heat medium pump 21 is a high temperature side water pump that pumps the high temperature side heat medium to the inlet side of the water passage of the high temperature side water-refrigerant heat exchanger 12 in the high temperature side heat medium circuit 20.
  • the high temperature side heat medium pump 21 is an electric pump whose rotational speed (that is, water pressure transfer capacity) is controlled by a control voltage output from the air conditioning controller 60.
  • the heater core 22 is disposed in a casing 51 of an indoor air conditioning unit 50 described later.
  • the heater core 22 is a heat exchanger that heats the blown air by heat exchange between the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 16 described later. is there.
  • the high temperature side radiator 23 performs heat exchange between the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 and the outside air blown from the outside air fan (not shown) to obtain the heat of the high temperature side heat medium as the outside air. Is a heat exchanger that dissipates heat.
  • the high temperature side radiator 23 is disposed on the front side in the vehicle bonnet. For this reason, when the vehicle is traveling, the high-temperature side radiator 23 can also be exposed to the traveling wind.
  • the high temperature side radiator 23 may be integrally formed with the high temperature side water-refrigerant heat exchanger 12 or the like.
  • the heater core 22 and the high temperature side radiator 23 are connected in parallel to the flow of the high temperature side heat medium in the high temperature side heat medium circuit 20, as shown in FIG.
  • the high temperature side flow rate adjustment valve 24 flows the high temperature side heat medium flowed into the heater core 22 and the high temperature introduced into the high temperature side radiator 23. It is an electric three-way flow control valve that continuously adjusts the high temperature side flow ratio with the flow rate of the side heat transfer medium. The operation of the high temperature side flow control valve 24 is controlled by a control signal output from the air conditioning controller 60.
  • the high temperature side flow control valve 24 is disposed at the connection between the heat medium inlet side of the heater core 22 and the heat medium inlet side of the high temperature side radiator 23. More specifically, the inlet side of the high temperature side flow control valve 24 is connected to the outlet of the water passage of the high temperature side water-refrigerant heat exchanger 12. The heat medium inlet side of the heater core 22 is connected to one outlet of the high temperature side flow control valve 24. The heat medium inlet side of the high temperature side radiator 23 is connected to the other outlet of the high temperature side flow control valve 24.
  • the high temperature side flow rate adjustment valve 24 adjusts the high temperature side flow rate ratio
  • the flow rate of the high temperature side heat medium flowing into the heater core 22 changes.
  • the amount of heat radiation to the blast air of the high temperature side heat medium in heater core 22, ie, the amount of heating of the blast air in heater core 22, is adjusted.
  • the high temperature side heat medium pump 21 disposed in the high temperature side heat medium circuit 20, the high temperature side water-refrigerant heat exchanger 12, the heater core 22, the high temperature side radiator 23, the high temperature side flow control valve 24 and the like The heating part which heats blowing air by using the refrigerant
  • the branch portion 13 a branches the flow of the high pressure refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12.
  • the branch portion 13a is a three-way joint structure having three refrigerant inlets and outlets communicating with each other, one of the three inlets and outlets being a refrigerant inlet and the remaining two being a refrigerant outlet.
  • the refrigerant inlet side of the indoor evaporator 16 is connected to one refrigerant outlet of the branch portion 13a via the cooling on-off valve 14a and the cooling expansion valve 15a.
  • the refrigerant inlet side of the outdoor evaporator 18 is connected to the other refrigerant outlet of the branch portion 13a via the heat absorption on-off valve 14b and the heat absorption expansion valve 15b.
  • the cooling on-off valve 14a is an electromagnetic valve that opens and closes a refrigerant passage from one refrigerant outlet of the branch portion 13a to the inlet of the cooling expansion valve 15a.
  • the on-off operation of the cooling on-off valve 14 a is controlled by the control voltage output from the air conditioning control device 60.
  • the cooling on-off valve 14a constitutes a circuit switching unit that switches between a refrigerant circuit that causes the refrigerant to flow into the indoor evaporator 16 and a refrigerant circuit that prevents the refrigerant from flowing into the indoor evaporator 16 by opening and closing the refrigerant passage.
  • the cooling expansion valve 15a is a cooling decompression unit that decompresses the refrigerant that has flowed out from one refrigerant outlet of the branch unit 13a at least in the cooling mode and the dehumidifying and heating mode. Furthermore, the cooling expansion valve 15 a is a cooling flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the indoor evaporator 16.
  • the expansion valve 15a for cooling is squeezed open by a mechanical mechanism according to the temperature and pressure of the refrigerant at the outlet side of the indoor evaporator 16 (in the present embodiment, the refrigerant flowing out from the indoor evaporator 16).
  • a thermal expansion valve that changes the degree is adopted.
  • the cooling expansion valve 15 a has a temperature sensing portion 151 a that detects the temperature and pressure of the refrigerant on the outlet side of the indoor evaporator 16.
  • Temperature sensing portion 151a is an enclosed space forming member forming an enclosed space in which the temperature sensitive medium is enclosed, and a pressure difference between the pressure of the temperature sensitive medium and the pressure of the refrigerant on the outlet side of indoor evaporator 16 It is comprised by the diaphragm which is a pressure response member to deform
  • the temperature sensitive medium is a medium whose pressure changes according to the temperature of the refrigerant at the outlet side of the indoor evaporator 16.
  • the throttle opening degree is changed by transmitting the displacement of the diaphragm to the valve body that changes the passage cross-sectional area of the throttle passage. The throttle opening degree characteristic of the cooling expansion valve 15a will be described later.
  • the refrigerant inlet side of the indoor evaporator 16 is connected to the outlet of the cooling expansion valve 15a.
  • the indoor evaporator 16 performs a heat exchange between the low pressure refrigerant decompressed by the cooling expansion valve 15a and the blowing air at least in the cooling mode and the dehumidifying heating mode to evaporate the low pressure refrigerant and cool the blowing air. It is an evaporator.
  • the indoor evaporator 16 is disposed in the casing 51 of the indoor air conditioning unit 50.
  • the inlet side of the evaporation pressure control valve 17 is connected to the refrigerant outlet of the indoor evaporator 16.
  • the evaporation pressure adjustment valve 17 is an evaporation pressure adjustment unit that maintains the refrigerant evaporation pressure in the indoor evaporator 16 at or above a predetermined reference pressure.
  • the evaporation pressure control valve 17 is configured by a mechanical variable throttle mechanism that increases the valve opening degree as the refrigerant pressure on the outlet side of the indoor evaporator 16 increases.
  • the evaporation pressure adjusting valve 17 maintains the refrigerant evaporation temperature in the indoor evaporator 16 at a frost formation suppression reference temperature (1.degree. C. in the present embodiment) capable of suppressing frost formation in the indoor evaporator 16.
  • One refrigerant inlet side of the merging portion 13 b is connected to the outlet of the evaporation pressure adjusting valve 17.
  • the merging portion 13 b merges the flow of the refrigerant flowing out of the evaporation pressure adjusting valve 17 and the flow of the refrigerant flowing out of the outdoor evaporator 18.
  • the merging portion 13b has a three-way joint structure similar to that of the branching portion 13a, in which two of the three inlets and outlets are used as a refrigerant inlet and the remaining one is used as a refrigerant outlet.
  • the heat absorption on-off valve 14b is an electromagnetic valve that opens and closes a refrigerant passage from the other refrigerant outlet of the branch portion 13a to the inlet of the heat absorption expansion valve 15b.
  • the basic configuration of the heat absorption on-off valve 14b is the same as that of the cooling on-off valve 14a.
  • the heat absorbing on-off valve 14b constitutes a circuit switching unit together with the cooling on-off valve 14a.
  • the heat absorption expansion valve 15 b is a heat absorption decompression unit that decompresses the refrigerant that has flowed out from the other refrigerant outlet of the branch unit 13 a at least in the heating mode. Furthermore, the heat absorption expansion valve 15 b is a heat absorption flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the outdoor evaporator 18.
  • the heat absorption expansion valve 15b is squeezed open by a mechanical mechanism according to the temperature and pressure of the refrigerant on the outlet side of the outdoor evaporator 18 (in the present embodiment, the refrigerant flowing out of the outdoor evaporator 18).
  • a thermal expansion valve that changes the degree is adopted.
  • the basic configuration of the heat absorption expansion valve 15b is the same as that of the cooling expansion valve 15a. Therefore, the heat absorption expansion valve 15 b has a temperature sensing portion 151 b that detects the temperature and pressure of the refrigerant on the outlet side of the outdoor evaporator 18.
  • the temperature sensitive medium sealed in the temperature sensitive part 151b of the heat absorption expansion valve 15b is a medium which changes its pressure according to the temperature of the refrigerant at the outlet side of the outdoor evaporator 18.
  • the throttle opening degree characteristic of the heat absorption expansion valve 15b will be described later.
  • the refrigerant inlet side of the outdoor evaporator 18 is connected to the outlet of the heat absorption expansion valve 15b.
  • the outdoor evaporator 18 exchanges heat between the low pressure refrigerant depressurized by the heat absorption expansion valve 15b and the open air blown from an external air fan (not shown) at least in the heating mode and the dehumidifying heating mode to evaporate the low pressure refrigerant.
  • an external air fan not shown
  • the heat-source fluid of this embodiment is external air.
  • the outdoor evaporator 18 is disposed on the front side in the vehicle bonnet.
  • the outdoor evaporator 18 may be integrally formed with the high temperature side radiator 23 and the like.
  • the other refrigerant inlet side of the merging portion 13 b is connected to the refrigerant outlet of the outdoor evaporator 18.
  • the suction port side of the compressor 11 is connected to the refrigerant outlet of the merging portion 13b.
  • the refrigerant at the outlet side of the indoor evaporator 16 is defined as a cooling refrigerant
  • the temperature of the cooling refrigerant is defined as a cooling temperature T1
  • the pressure of the cooling refrigerant is defined as a cooling pressure P1.
  • the change in the cooling pressure P1 corresponding to the change in the cooling temperature T1 is more specific as the cooling characteristic line CL1 shown by the thick solid line in FIG. Specifically, the throttle opening is changed so as to approach the cooling characteristic line CL1.
  • the cooling characteristic line CL1 of the present embodiment is set to a line substantially parallel to a saturated vapor pressure line SL indicated by a thin one-dot chain line in FIG.
  • the saturated vapor pressure line SL is determined by the physical properties of the refrigerant circulating in the cycle (in the present embodiment, R134a).
  • the cooling pressure P1 has a value lower than the saturation vapor pressure regardless of the cooling temperature T1.
  • the throttle opening degree characteristic of the cooling expansion valve 15a of the present embodiment is changed so that the cooling refrigerant is in the gas phase having the degree of superheat regardless of the cooling temperature T1. More specifically, in the throttle opening characteristic of the cooling expansion valve 15a, the throttle opening is changed so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 is approximately 3 ° C. during normal operation of the cycle. .
  • Such a throttle opening degree characteristic can be realized by adopting a medium containing a refrigerant that circulates a cycle as a main component, as a temperature sensitive medium sealed in the temperature sensing portion 151a of the cooling expansion valve 15a. . That is, it can be realized by adopting a so-called normal charge type thermal expansion valve as the cooling expansion valve 15a.
  • the refrigerant on the outlet side of the outdoor evaporator 18 is defined as an endothermic refrigerant
  • the temperature of the endothermic refrigerant is defined as an endothermic temperature T2
  • the pressure of the endothermic refrigerant is defined as an endothermic pressure P2.
  • the change of the pressure P2 for heat absorption corresponding to the change of the temperature T2 for heat absorption is more concrete so that the characteristic line CL2 for heat absorption shown in the thick broken line of FIG.
  • the throttle opening is changed so as to approach the heat absorption characteristic line CL2.
  • the cooling characteristic line CL1 and the heat absorption characteristic line CL2 are different from each other. More specifically, in the present embodiment, the inclination of the heat absorption characteristic line CL2 is smaller than the inclination of the cooling characteristic line CL1.
  • the inclination of the cooling characteristic line CL1 can adopt a differential value of a mathematical expression representing the cooling characteristic line CL1 as a function of the cooling pressure P1 as the cooling temperature T1.
  • a derivative value of a mathematical expression representing the cooling characteristic line CL1 can be adopted as a function of the heat absorption pressure P2 as the heat absorption temperature T2.
  • the heat absorption pressure P2 is higher than the saturation pressure determined by the cooling pressure P1 and the saturated vapor pressure line of the refrigerant. It's getting higher.
  • the heat absorption refrigerant is squeezed so as to be in a gas-liquid two-phase state in a range where the heat absorption temperature T2 is lower than the reference temperature KT2. Change the degree. Furthermore, in the range where the temperature T2 for heat absorption is higher than the reference temperature KT2, the degree of throttle opening is changed so that the heat absorption refrigerant is in a gas phase having the degree of superheat.
  • Such a throttle opening characteristic is obtained by mixing an inert gas with a refrigerant having a component different from that of the refrigerant circulating in the cycle as a temperature sensitive medium sealed in the temperature sensing portion 151b of the heat absorption expansion valve 15b. It can be realized by adopting. That is, it can be realized by adopting a so-called cross charge type thermal expansion valve as the heat absorption expansion valve 15b.
  • the reference temperature KT2 of the present embodiment is set to a value (specifically, 1 ° C.) higher than the value that can be taken by the heat absorption temperature T2 when the operation in the heating mode is performed. Therefore, in the heating mode, the heat absorption expansion valve 15b changes the throttle opening degree so that the heat absorption refrigerant flowing out of the outdoor evaporator 18 is in a gas-liquid two-phase state.
  • the refrigerant on the outlet side of each evaporator does not mean only the refrigerant at the moment when it passes through the refrigerant outlet of each evaporator, and the refrigerant on the outlet side of each evaporator is the refrigerant of the indoor evaporator 16
  • the refrigerant immediately before flowing out from the outlet and the refrigerant immediately after flowing out from the refrigerant outlet of the indoor evaporator 16 are also included.
  • the indoor air conditioning unit 50 forms an air passage for blowing out the blowing air whose temperature has been adjusted by the refrigeration cycle apparatus 10 to an appropriate place in the vehicle compartment in the vehicle air conditioner 1.
  • the indoor air conditioning unit 50 is disposed inside the instrument panel (i.e., the instrument panel) at the front of the vehicle interior.
  • the indoor air conditioning unit 50 accommodates the blower 52, the indoor evaporator 16, the heater core 22 and the like in an air passage formed inside a casing 51 forming an outer shell thereof.
  • the casing 51 forms an air passage for blowing air blown into the vehicle compartment, and is molded of a resin (specifically, polypropylene) which has a certain degree of elasticity and is excellent in strength.
  • An internal / external air switching device 53 is disposed on the most upstream side of the blowing air flow of the casing 51. The inside / outside air switching device 53 switches and introduces inside air (air in the vehicle interior) and outside air (air outside the vehicle) into the casing 51.
  • the inside / outside air switching device 53 continuously adjusts the opening area of the inside air introduction port for introducing inside air into the casing 51 and the outside air introduction port for introducing outside air by means of the inside / outside air switching door.
  • the introduction rate with the introduction air volume can be changed.
  • the inside and outside air switching door is driven by an electric actuator for the inside and outside air switching door. The operation of the electric actuator is controlled by a control signal output from the air conditioning controller 60.
  • a blower 52 is disposed downstream of the inside / outside air switching device 53 in the flow of the blown air.
  • the blower 52 has a function of blowing the air taken in via the inside / outside air switching device 53 toward the vehicle interior and blowing it.
  • the blower 52 is an electric blower that drives a centrifugal multiblade fan by an electric motor.
  • the rotation speed (that is, the blowing capacity) of the blower 52 is controlled by the control voltage output from the air conditioning control device 60.
  • the indoor evaporator 16 and the heater core 22 are disposed in this order with respect to the flow of the air, on the downstream side of the air flow of the fan 52. That is, the indoor evaporator 16 is disposed upstream of the heater core 22 in the flow of the blown air.
  • a cold air bypass passage 55 is formed, in which the blown air having passed through the indoor evaporator 16 is allowed to bypass the heater core 22 and flow downstream.
  • An air mix door 54 is disposed on the downstream side of the air flow of the indoor evaporator 16 and on the upstream side of the air flow of the heater core 22.
  • the air mix door 54 adjusts the air volume ratio of the air volume passing through the heater core 22 and the air volume passing through the cold air bypass passage 55 in the blown air after passing through the indoor evaporator 16.
  • the air mix door 54 is driven by an electric actuator for driving the air mix door.
  • the operation of the electric actuator is controlled by a control signal output from the air conditioning controller 60.
  • a mixing space 56 for mixing the air heated by the heater core 22 and the air not passing through the cold air bypass passage 55 and not heated by the heater core 22.
  • a mixing space 56 for mixing the air heated by the heater core 22 and the air not passing through the cold air bypass passage 55 and not heated by the heater core 22.
  • an opening for blowing out the air (air-conditioned air) mixed in the mixing space into the vehicle compartment.
  • the face opening hole is an opening hole for blowing the conditioned air toward the upper body of the occupant in the vehicle compartment.
  • the foot opening hole is an opening hole for blowing the conditioned air toward the feet of the occupant.
  • the defroster opening hole is an opening hole for blowing the conditioned air toward the inner side surface of the vehicle front windshield.
  • These face opening holes, foot opening holes, and defroster opening holes are respectively provided in the vehicle compartment via a duct that forms an air passage, face outlet, foot outlet, and defroster outlet (all not shown) )It is connected to the.
  • the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air volume ratio of the air volume passing the heater core 22 and the air volume passing the cold air bypass passage 55 by the air mix door 54.
  • the temperature of the air (air-conditioned air) blown out from the outlets into the vehicle compartment is also adjusted.
  • a face door for adjusting the opening area of the face opening hole
  • a foot door for adjusting the opening area of the foot opening hole
  • a defroster opening on the upstream side of the air flow of the face opening hole, the foot opening hole and the defroster opening hole.
  • a defroster door (not shown) is arranged to adjust the opening area of the hole.
  • These face door, foot door, and defroster door constitute an air outlet mode switching device that switches the air outlet from which the conditioned air is blown out.
  • the face door, the foot door, and the defroster door are connected to an electric actuator for driving the air outlet mode door via a link mechanism and the like, and are operated to rotate in conjunction with each other.
  • the operation of the electric actuator is controlled by a control signal output from the air conditioning controller 60.
  • the air conditioning control device 60 is configured of a known microcomputer including a CPU, a ROM, a RAM, and the like, and peripheral circuits thereof. Then, various calculations and processing are performed based on the air conditioning control program stored in the ROM, and the operation of various control target devices 11, 14a, 14b, 21, 24, 52, etc. connected to the output side is controlled. Do.
  • an inside air temperature sensor 62a on the input side of the air conditioning control device 60, an inside air temperature sensor 62a, an outside air temperature sensor 62b, a solar radiation sensor 62c, a high pressure sensor 62d, an evaporator temperature sensor 62e, and an air conditioning air temperature sensor A sensor group for air conditioning control such as 62f is connected.
  • the air conditioning control device 60 receives detection signals of these air conditioning control sensors.
  • the inside air temperature sensor 62a is an inside air temperature detection unit that detects a vehicle room temperature (inside air temperature) Tr.
  • the outside air temperature sensor 62b is an outside air temperature detection unit that detects the temperature outside the vehicle (outside air temperature) Tam.
  • the solar radiation sensor 62c is a solar radiation amount detection unit that detects the solar radiation amount As emitted to the vehicle interior.
  • the high pressure sensor 62 d is a refrigerant pressure detection unit that detects the high pressure refrigerant pressure Pd of the refrigerant flow path from the discharge port side of the compressor 11 to the inlet side of the cooling expansion valve 15 a or the heat absorption expansion valve 15 b.
  • the evaporator temperature sensor 62 e is an evaporator temperature detection unit that detects a refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 16.
  • the air conditioning air temperature sensor 62f is an air conditioning air temperature detection unit that detects a temperature of a blown air TAV which is blown into the vehicle compartment from the first mixing space 56a and the second mixing space 56b.
  • an operation panel 61 disposed in the vicinity of the instrument panel at the front of the vehicle compartment is connected to the input side of the air conditioning control device 60.
  • Various operation switches provided on the operation panel 61 The operation signal of is input.
  • an auto switch for setting or canceling the automatic control operation of the air conditioning system for a vehicle
  • a cooling switch for requesting cooling of the vehicle interior
  • an air volume of the blower 52 There are an air volume setting switch for manually setting the temperature setting switch and a temperature setting switch for setting the target temperature Tset in the vehicle compartment.
  • the air-conditioning control apparatus 60 of this embodiment controls the operation
  • movement of each control object apparatus constitute a control unit that controls the operation of each control target device.
  • the configuration that controls the operation of the compressor 11 is the discharge capacity control unit 60a.
  • the operation mode can be switched.
  • the switching of these operation modes is performed by executing the air conditioning control program stored in advance in the air conditioning control device 60.
  • the target blowout temperature TAO of the air to be blown into the vehicle compartment is calculated. calculate. Then, the operation mode is switched based on the target blowout temperature TAO and the detection signal. The operation of each operation mode will be described below.
  • (A) Cooling Mode In the cooling mode, the air-conditioning control device 60 opens the cooling on-off valve 14a and closes the heat-absorbing on-off valve 14b.
  • the compressor 11 high temperature side water-refrigerant heat exchanger 12 ⁇ branching portion 13a ⁇ cooling on-off valve 14a ⁇ cooling expansion valve 15a ⁇ interior evaporator 16 ⁇ evaporation pressure regulating valve
  • a vapor compression type refrigeration cycle in which the refrigerant circulates in the order of 17 ⁇ merging portion 13 b ⁇ compressor 11 is configured.
  • the refrigerant circuit in the cooling mode, is switched to the refrigerant circuit that causes the refrigerant to flow into the indoor evaporator 16.
  • the refrigerant circuit in the cooling mode, is switched to a refrigerant circuit that allows the refrigerant to flow into the cooling evaporator.
  • the air conditioning control device 60 controls the operation of various control target devices connected to the output side.
  • the air conditioning control device 60 controls the operation of the compressor 11 such that the refrigerant evaporation temperature Tefin detected by the evaporator temperature sensor 62e becomes the target evaporation temperature TEO.
  • the target evaporation temperature TEO is determined based on the target blowing temperature TAO with reference to the control map for the cooling mode stored in advance in the air conditioning control device 60.
  • the target evaporation temperature TEO is raised along with the rise of the target blowout temperature TAO so that the blown air temperature TAV detected by the air conditioning air temperature sensor 62f approaches the target blowout temperature TAO. Furthermore, the target evaporation temperature TEO is determined to be a value in a range (specifically, 1 ° C. or more) in which frost formation of the indoor evaporator 16 can be suppressed.
  • the air conditioning control device 60 operates the high temperature side heat medium pump 21 so as to exert the water pressure transfer capability in the cooling mode set in advance. Further, the air conditioning control device 60 operates the high temperature side flow control valve 24 so that the total flow rate of the high temperature side heat medium flowing out from the water passage of the high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side radiator 23 Control.
  • the air conditioning control device 60 determines the control voltage (blowing capacity) of the blower 52 with reference to the control map stored in advance in the air conditioning control device 60 based on the target blowing temperature TAO. Specifically, in this control map, the air flow of the blower 52 is maximized in the cryogenic temperature range (maximum cooling area) and the extremely high temperature area (maximum heating area) of the target blowout temperature TAO, and as the intermediate temperature range is approached. Reduce air flow.
  • the air conditioning control device 60 controls the operation of the air mix door 54 so that the cold air bypass passage 55 is fully opened and the air passage on the heater core 22 side is closed. Further, the air conditioning control device 60 appropriately controls the operation of other various control target devices.
  • the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12.
  • the high temperature side heat medium pump 21 since the high temperature side heat medium pump 21 operates, the high pressure refrigerant and the high temperature side heat medium exchange heat, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium Is heated.
  • the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 flows into the high temperature side radiator 23 through the high temperature side flow rate adjustment valve 24.
  • the high temperature side heat medium flowing into the high temperature side radiator 23 exchanges heat with the outside air and radiates heat. Thereby, the high temperature side heat medium is cooled.
  • the high temperature side heat medium cooled by the high temperature side radiator 23 is drawn into the high temperature side heat medium pump 21 and is pressure-fed again to the water passage of the high temperature side water-refrigerant heat exchanger 12.
  • the throttle opening degree of the cooling expansion valve 15a is adjusted so that the cooling pressure P1 with respect to the cooling temperature T1 approaches the cooling characteristic line CL1 shown in FIG. That is, the throttle opening degree of the cooling expansion valve 15a is adjusted so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 is approximately 3 ° C.
  • the low pressure refrigerant reduced in pressure by the cooling expansion valve 15 a flows into the indoor evaporator 16.
  • the refrigerant flowing into the indoor evaporator 16 absorbs heat from the air blown from the fan 52 and evaporates. Thereby, the blowing air is cooled.
  • the refrigerant flowing out of the indoor evaporator 16 is sucked into the compressor 11 via the evaporation pressure adjusting valve 17 and the merging portion 13 b and compressed again.
  • the blowing air cooled by the indoor evaporator 16 can be blown into the vehicle compartment to perform cooling of the vehicle compartment.
  • (B) Heating mode In the heating mode, the air-conditioning control device 60 closes the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b.
  • the compressor 11 in the refrigeration cycle apparatus 10 in the heating mode, the compressor 11 ⁇ high temperature side water-refrigerant heat exchanger 12 ⁇ branching portion 13a ⁇ heat absorption on-off valve 14b ⁇ heat absorption expansion valve 15b ⁇ outside evaporator 18 ⁇ merging portion 13b ⁇
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the compressor 11 is configured.
  • the refrigerant circuit in the heating mode, can be switched to a refrigerant circuit in which the refrigerant does not flow into the indoor evaporator 16.
  • the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant is prohibited from flowing into the cooling evaporator.
  • the air conditioning control device 60 controls the operation of various control target devices connected to the output side.
  • the air-conditioning control device 60 controls the operation of the compressor 11 such that the high-pressure refrigerant pressure Pd detected by the high-pressure sensor 62d becomes the target high-pressure PCO.
  • the target high pressure PCO is determined based on the target blowout temperature TAO with reference to the control map for the heating mode stored in advance in the air conditioning control device 60.
  • the target high pressure PCO is raised with the rise of the target blowing temperature TAO so that the blowing air temperature TAV approaches the target blowing temperature TAO.
  • the air conditioning control device 60 operates the high temperature side heat medium pump 21 so as to exert the water pressure transfer capability in the predetermined heating mode. Further, the air conditioning controller 60 controls the operation of the high temperature side flow control valve 24 so that the total flow rate of the high temperature side heat medium flowing out of the water passage of the high temperature side water-refrigerant heat exchanger 12 flows into the heater core 22. .
  • the air conditioning control device 60 determines the control voltage (blower capability) of the blower 52, as in the cooling mode. Further, the air conditioning control device 60 controls the operation of the air mix door 54 so as to close the cold air bypass passage 55 by fully opening the air passage on the heater core 22 side. Further, the air conditioning control device 60 appropriately controls the operation of other various control target devices.
  • the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12.
  • the high temperature side heat medium pump 21 since the high temperature side heat medium pump 21 operates, the high pressure refrigerant and the high temperature side heat medium exchange heat, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium Is heated.
  • the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 flows into the heater core 22 via the high temperature side flow rate adjustment valve 24.
  • the high temperature side heat medium having flowed into the heater core 22 exchanges heat with the air that has passed through the indoor evaporator 16 and radiates heat since the air mix door 54 fully opens the air passage on the heater core 22 side.
  • the blowing air is heated, and the temperature of the blowing air approaches the target blowing temperature TAO.
  • the high temperature side heat medium flowing out of the heater core 22 is sucked into the high temperature side heat medium pump 21 and is pressure-fed again to the water passage of the high temperature side water-refrigerant heat exchanger 12.
  • the high pressure refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 flows into the heat absorption expansion valve 15b via the branch portion 13a and the heat absorption opening / closing valve 14b, and is decompressed.
  • the throttle opening degree of the heat absorption expansion valve 15b is adjusted so that the heat absorption pressure P2 with respect to the heat absorption temperature T2 approaches the heat absorption characteristic line CL2 shown in FIG.
  • the temperature T2 for heat absorption when the operation of the heating mode is performed becomes a value lower than the reference temperature KT2. Therefore, the heat absorption pressure P2 becomes higher than the saturation pressure of the refrigerant. That is, the throttle opening degree of the heat absorption expansion valve 15b is adjusted so that the refrigerant on the outlet side of the outdoor evaporator 18 is in a gas-liquid two-phase state.
  • the low pressure refrigerant reduced in pressure by the heat absorption expansion valve 15 b flows into the outdoor evaporator 18.
  • the refrigerant flowing into the outdoor evaporator 18 absorbs heat from the outside air, which is a heat source fluid blown from the outside air fan, and evaporates.
  • the refrigerant flowing out of the outdoor evaporator 18 is sucked into the compressor 11 via the merging portion 13 b and compressed again.
  • the heating mode the blowing air heated by the heater core 22 can be blown into the passenger compartment to heat the passenger compartment.
  • the heating mode is switched to a refrigerant circuit that does not allow the refrigerant to flow into the indoor evaporator 16, and an operation that satisfies a predetermined condition that the temperature T2 for heat absorption is lower than the reference temperature KT2 It is a mode.
  • (C) Dehumidifying and Heating Mode In the dehumidifying and heating mode, the air conditioning control device 60 opens the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b.
  • the compressor 11 ⁇ high temperature side water-refrigerant heat exchanger 12 ⁇ branching portion 13a ⁇ cooling on-off valve 14a ⁇ cooling expansion valve 15a ⁇ interior evaporator 16 ⁇ evaporation pressure adjustment
  • the refrigerant circulates in the order of valve 17 ⁇ junction 13b ⁇ compressor 11, and the compressor 11 ⁇ high temperature side water-refrigerant heat exchanger 12 ⁇ branch 13a ⁇ heat absorption on-off valve 14b ⁇ heat absorption expansion valve 15b ⁇ outside
  • a vapor compression type refrigeration cycle in which the refrigerant circulates in the order of the evaporator 18 ⁇ the merging portion 13b ⁇ the compressor 11 is configured.
  • the indoor evaporator 16 and the outdoor evaporator 18 are switched to the refrigerant circuit connected in parallel to the refrigerant flow. Furthermore, in the cooling mode, the refrigerant circuit is switched to the refrigerant circuit that causes the refrigerant to flow into the indoor evaporator 16.
  • the air conditioning control device 60 controls the operation of various control target devices connected to the output side.
  • the air conditioning controller 60 controls the operation of the compressor 11 as in the heating mode. Further, the air conditioning control device 60 operates the high temperature side heat medium pump 21 so as to exert the water pressure transfer capability in the predetermined dehumidifying and heating mode. In the same manner as in the heating mode, the air conditioning controller 60 also controls the high temperature side flow control valve so that the total flow rate of the high temperature side heat medium flowing out of the water passage of the high temperature side water-refrigerant heat exchanger 12 flows into the heater core 22. Control the operation of 24.
  • the air conditioning control device 60 determines the control voltage (blower capability) of the blower 52, as in the cooling mode and the heating mode. Further, the air-conditioning control device 60 controls the operation of the air mix door 54 so as to fully open the air passage on the heater core 22 side and close the cold air bypass passage 55 as in the heating mode. In addition, the air conditioning control device 60 appropriately determines control signals to be output to other various control target devices.
  • the high temperature and high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12.
  • the high temperature side heat medium pump 21 since the high temperature side heat medium pump 21 operates, the high pressure refrigerant and the high temperature side heat medium exchange heat, the high pressure refrigerant is cooled and condensed, and the high temperature side heat medium Is heated.
  • the high temperature side heat medium heated by the high temperature side water-refrigerant heat exchanger 12 flows into the heater core 22 through the high temperature side flow rate adjustment valve 24 as in the heating mode.
  • the high temperature side heat medium that has flowed into the heater core 22 exchanges heat with the air that has passed through the indoor evaporator 16 and radiates heat, as in the heating mode.
  • blowing air which passed indoor evaporator 16 is heated, and the temperature of blowing air approaches target blowing temperature TAO.
  • the high temperature side heat medium flowing out of the heater core 22 is sucked into the high temperature side heat medium pump 21 and is pressure-fed again to the water passage of the high temperature side water-refrigerant heat exchanger 12.
  • the high pressure refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 is branched at the branch portion 13a.
  • One of the refrigerants branched by the branch portion 13a flows into the cooling expansion valve 15a and is decompressed as in the cooling mode.
  • the throttle opening degree of the cooling expansion valve 15a is adjusted so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 is 3 ° C.
  • the low pressure refrigerant reduced in pressure by the cooling expansion valve 15 a flows into the indoor evaporator 16.
  • the refrigerant flowing into the indoor evaporator 16 absorbs heat from the air blown from the fan 52 and evaporates. Thereby, the blast air is cooled and dehumidified.
  • coolant evaporation temperature in the indoor evaporator 16 is maintained by 1 degreeC or more by the effect
  • the refrigerant that has flowed out of the indoor evaporator 16 flows into one of the refrigerant inlets of the merging portion 13 b via the evaporation pressure adjusting valve 17.
  • the other refrigerant branched by the branch portion 13a flows into the heat absorption expansion valve 15b and is decompressed, as in the heating mode.
  • the throttle opening degree of the heat absorption expansion valve 15b is adjusted so that the refrigerant on the outlet side of the outdoor evaporator 18 is in a gas-liquid two-phase state.
  • the low pressure refrigerant reduced in pressure by the heat absorption expansion valve 15 b flows into the outdoor evaporator 18.
  • the refrigerant flowing into the outdoor evaporator 18 absorbs heat from the outside air blown from the outside air fan and evaporates.
  • coolant which flowed out out of the outdoor evaporator 18 flows in into the other refrigerant
  • the refrigerant in the gas phase having the degree of superheating that has flowed out of the indoor evaporator 16 and the refrigerant in the gas-liquid two-phase state that flows out of the outdoor evaporator 18 merge.
  • the flow coefficients in the respective passages of the branch portion 13a, the heat exchange performance of the indoor evaporator 16, and the heat exchange performance of the outdoor evaporator 18 are set such that the merged refrigerant approaches the saturated gas phase refrigerant.
  • the refrigerant flowing out of the merging portion 13b is sucked into the compressor 11 and compressed again.
  • the dehumidified heating of the vehicle interior can be performed by reheating the blown air cooled and dehumidified by the indoor evaporator 16 by the heater core 22 and blowing it out into the vehicle interior.
  • the refrigeration cycle apparatus 10 can switch between the cooling mode, the heating mode, and the dehumidifying heating mode by switching the refrigerant circuit, and the air conditioning in the vehicle interior can be comfortable. Can be realized.
  • the cycle configuration tends to be complicated.
  • the refrigeration cycle apparatus 10 of the present embodiment there is no switching between the refrigerant circuit that causes the high pressure refrigerant to flow into the same heat exchanger and the refrigerant circuit that causes the low pressure refrigerant to flow. That is, since it is not necessary to cause the high pressure refrigerant to flow into the indoor evaporator 16 and the outdoor evaporator 18 even when switching to any refrigerant circuit, the refrigerant circuit can be switched with a simple configuration without causing complication of the cycle configuration. .
  • the state of the refrigerant on the outlet side of the heat exchanger functioning as the evaporator has to be appropriately adjusted according to the operation mode.
  • the heat-absorbing characteristic line CL1 indicating the throttling opening characteristic of the cooling expansion valve 15 a and the heat absorption for showing the throttling opening characteristic of the heat absorption expansion valve 15 b Characteristic lines CL2 are different from one another. Accordingly, the state of the cooling refrigerant flowing out of the indoor evaporator 16 and the state of the heat absorption refrigerant flowing out of the outdoor evaporator 18 can be adjusted to appropriate states.
  • the reference temperature KT2 is set so that the temperature T2 for heat absorption becomes lower than the reference temperature KT2 in the heating mode in which the refrigerant circuit is switched not to allow the refrigerant to flow into the indoor evaporator 16. It is done. Therefore, in the heating mode, the heat absorption pressure P2 can be set to a value higher than the saturation pressure of the refrigerant, and the heat absorption refrigerant can be brought into a gas-liquid two-phase state.
  • the refrigerant evaporation temperature in the outdoor evaporator 18 needs to be lower than the outside air temperature, and even in the operation mode in which the flow rate of the circulating refrigerant circulating the cycle tends to decrease, the inside of the outdoor evaporator 18 is It is possible to suppress the accumulation of refrigeration oil.
  • the cooling pressure P1 can be set to a value lower than the saturation pressure of the refrigerant, and the cooling refrigerant can be brought into the gas phase having the degree of superheat. Therefore, when switching to the refrigerant circuit that causes the refrigerant to flow into the indoor evaporator 16 as in the cooling mode or the dehumidifying heating mode, the indoor evaporator 16 efficiently cools the blowing air by the latent heat of vaporization. be able to.
  • the refrigerant circuit can be switched without causing the complication of the cycle configuration. Furthermore, according to the operation mode, the state of the refrigerant on the outlet side of the indoor evaporator 16 that is a cooling evaporator and the outdoor evaporator 18 that is a heat absorption evaporator can be appropriately adjusted.
  • a thermal expansion valve of the normal charge system is adopted as the cooling expansion valve 15a
  • a thermal expansion valve of the cross charge system is adopted as the heat absorption expansion valve 15b. Therefore, without complicating the control mode of the cooling expansion valve 15a and the heat absorption expansion valve 15b, the state of the refrigerant having flowed out of the indoor evaporator 16 and the outdoor evaporator 18 can be appropriately made extremely easily by a mechanical mechanism. It can be adjusted.
  • the heater core 22 is disposed in the high temperature side heat medium circuit 20 including the water-refrigerant heat exchanger 12 and circulating the high temperature side heat medium. Therefore, in the heating mode and the dehumidifying heating mode, the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 can be made to flow into the heater core 22 to heat the blowing air.
  • the high pressure side heat medium of uniform temperature can be made to flow into heater core 22, and it can control that temperature distribution arises in blowing air heated by heater core.
  • the high temperature side radiator 23 is disposed in the high temperature side heat medium circuit 20. Therefore, the heat absorbed from the blown air can be dissipated to the outside air, and the interior of the vehicle can be cooled.
  • the internal heat exchanger 19 is a heat exchanger that exchanges heat between the refrigerant flowing in the high pressure side refrigerant passage and the refrigerant flowing in the low pressure side refrigerant passage.
  • the refrigerant flowing through the high pressure side refrigerant passage is a high pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the refrigerant flowing through the low pressure side refrigerant passage is the refrigerant flowing out of the outdoor evaporator 18, and is the low pressure refrigerant flowing out from the refrigerant outlet of the merging portion 13b.
  • the throttle opening degree characteristic of the heat absorption expansion valve 15b is determined.
  • the temperature of the low pressure refrigerant on the outlet side of the internal heat exchanger 19 is defined as the low pressure side temperature T3, and the pressure of the low pressure refrigerant is defined as the low pressure side pressure P3.
  • the change of the low pressure side pressure P3 corresponding to the change of the low pressure side temperature T3 is more specific as the low pressure side characteristic line CL3 shown by the thick broken line in FIG. Specifically, the throttle opening is changed so as to approach the low-pressure side characteristic line CL3.
  • the low-pressure side characteristic line CL3 draws a line similar to the heat-absorbing characteristic line CL2 described in FIG. 2 of the first embodiment. Therefore, the cooling characteristic line CL1 and the low-pressure side characteristic line CL3 are different from each other. Furthermore, the inclination of the low-pressure side characteristic line CL3 is smaller than the inclination of the cooling characteristic line CL1.
  • the low pressure side pressure P3 is higher than the cooling pressure P1 and the saturation pressure of the refrigerant.
  • the heat absorption refrigerant is squeezed so as to be in a gas-liquid two-phase state in the range where the low pressure side temperature T3 is lower than the reference temperature KT3. Change the degree. Furthermore, in the range where the low pressure side temperature T3 is higher than the reference temperature KT3, the degree of throttle opening is changed so that the heat absorption refrigerant is in the gas phase having the degree of superheat.
  • the reference temperature KT3 of the present embodiment is set to a value (specifically, 1 ° C.) higher than the value that can be obtained by the low pressure side temperature T3 when the operation in the heating mode is performed. Therefore, in the heating mode, the heat absorption expansion valve 15b changes the throttle opening degree so that the low pressure refrigerant at the outlet side of the internal heat exchanger 19 is in a gas-liquid two-phase state.
  • the thin single-dotted line in FIG. 5 is the saturated vapor pressure line SL of the refrigerant, and the thin two-dotted line is the heat-absorbing temperature T2 and heat-absorbing pressure P2 of the heat-absorbing refrigerant immediately after flowing out from the outdoor evaporator 18. It is a characteristic line which showed a relation.
  • the other configuration is the same as that of the first embodiment.
  • the operation mode is switched by executing the air conditioning control program.
  • the operation of each operation mode will be described below.
  • (A) Cooling Mode In the cooling mode, the air-conditioning control device 60 opens the cooling on-off valve 14a and closes the heat-absorbing on-off valve 14b, as in the first embodiment.
  • the compressor 11 high temperature side water-refrigerant heat exchanger 12 ⁇ high pressure side refrigerant passage of the internal heat exchanger 19 ⁇ branching portion 13a ⁇ cooling on-off valve 14a ⁇ cooling expansion valve 15a ⁇ indoor evaporator 16 ⁇ evaporation pressure adjusting valve 17 ⁇ merging section 13b ⁇ low pressure side refrigerant passage of internal heat exchanger 19 ⁇ compressor 11
  • a vapor compression type refrigeration cycle in which the refrigerant circulates is configured in this order.
  • the air conditioning control device 60 controls the operation of various control target devices connected to the output side, as in the cooling mode of the first embodiment. Accordingly, in the cooling mode, cooling of the vehicle interior can be performed by blowing out the blowing air cooled by the indoor evaporator 16 into the vehicle interior substantially as in the first embodiment.
  • (B) Heating mode In the heating mode, the air-conditioning control device 60 closes the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b as in the first embodiment.
  • the compressor 11 high temperature side water-refrigerant heat exchanger 12 ⁇ high pressure side refrigerant passage of the internal heat exchanger 19 ⁇ branch portion 13a ⁇ heat absorption on-off valve 14b ⁇ heat absorption expansion valve 15b ⁇ outdoor evaporator 18 ⁇ merging portion 13b ⁇ low pressure side refrigerant passage of internal heat exchanger 19 ⁇ compressor 11
  • a vapor compression type refrigeration cycle in which the refrigerant circulates is configured.
  • the air conditioning control device 60 controls the operation of various control target devices connected to the output side, as in the heating mode of the first embodiment.
  • the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12.
  • the blown air is heated by the heater core 22, and the temperature of the blown air approaches the target blowing temperature TAO.
  • the throttle opening degree of the heat absorption expansion valve 15b is adjusted so that the low pressure side pressure P3 with respect to the low pressure side temperature T3 approaches the low pressure side characteristic line CL3 shown in FIG.
  • the low pressure refrigerant reduced in pressure by the heat absorption expansion valve 15 b flows into the outdoor evaporator 18.
  • the refrigerant flowing into the outdoor evaporator 18 absorbs heat from the outside air, which is a heat source fluid blown from the outside air fan, and evaporates.
  • the refrigerant which has flowed out of the outdoor evaporator 18 flows into the low pressure side refrigerant passage of the internal heat exchanger 19 via the junction 13b.
  • the low pressure refrigerant flowing into the low pressure side refrigerant passage of the internal heat exchanger 19 exchanges heat with the high pressure refrigerant flowing through the high pressure side refrigerant passage of the internal heat exchanger 19 to raise the enthalpy.
  • the low pressure refrigerant flowing out of the low pressure side refrigerant passage of the internal heat exchanger 19 is sucked into the compressor 11 and compressed again.
  • the blowing air heated by the heater core 22 can be blown into the passenger compartment to heat the passenger compartment.
  • the air-conditioning control device 60 opens the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b as in the first embodiment.
  • the compressor 11 high temperature side water-refrigerant heat exchanger 12 ⁇ high pressure side refrigerant passage of the internal heat exchanger 19 ⁇ branching portion 13a ⁇ cooling on-off valve 14a ⁇ cooling expansion
  • the refrigerant circulates in the order of the valve 15a ⁇ the indoor evaporator 16 ⁇ the evaporation pressure adjusting valve 17 ⁇ the merging portion 13b ⁇ the low pressure side refrigerant passage of the internal heat exchanger 19 ⁇ the compressor 11, and the compressor 11 ⁇ high temperature side water-refrigerant Heat exchanger 12 ⁇ high pressure side refrigerant passage of internal heat exchanger 19 ⁇ branching portion 13a ⁇ heat absorption on-off valve 14b ⁇ heat absorption expansion valve 15b ⁇ outdoor evaporator 18 ⁇ joining portion 13b ⁇ low pressure side refrigerant of internal heat exchanger 19
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the passage and
  • the air conditioning control device 60 controls the operation of various control target devices connected to the output side, as in the dehumidifying and heating mode of the first embodiment.
  • the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12.
  • the blown air that has passed through the indoor evaporator 16 is heated by the heater core 22, and the temperature of the blown air approaches the target blowing temperature TAO.
  • the high pressure refrigerant flowing out of the high pressure side refrigerant passage of the internal heat exchanger 19 is branched at the branch portion 13a.
  • One of the refrigerants branched by the branch portion 13a flows into the cooling expansion valve 15a and is decompressed as in the cooling mode.
  • the throttle opening degree of the cooling expansion valve 15a is adjusted so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 16 is 3 ° C.
  • the low pressure refrigerant reduced in pressure by the cooling expansion valve 15 a flows into the indoor evaporator 16.
  • the refrigerant flowing into the indoor evaporator 16 absorbs heat from the air blown from the fan 52 and evaporates. Thus, as in the first embodiment, the blown air is cooled and dehumidified.
  • the refrigerant that has flowed out of the indoor evaporator 16 flows into one of the refrigerant inlets of the merging portion 13 b via the evaporation pressure adjusting valve 17.
  • the other refrigerant branched by the branch portion 13a flows into the heat absorption expansion valve 15b and is decompressed, as in the heating mode.
  • the throttle opening degree of the heat absorption expansion valve 15b is adjusted so that the refrigerant on the outlet side of the low pressure side refrigerant passage of the internal heat exchanger 19 is in a gas-liquid two-phase state.
  • the low pressure refrigerant reduced in pressure by the heat absorption expansion valve 15 b flows into the outdoor evaporator 18.
  • the refrigerant flowing into the outdoor evaporator 18 absorbs heat from the outside air blown from the outside air fan and evaporates.
  • coolant which flowed out out of the outdoor evaporator 18 flows in into the other refrigerant
  • the low pressure refrigerant flowing into the low pressure side refrigerant passage of the internal heat exchanger 19 exchanges heat with the high pressure refrigerant flowing through the high pressure side refrigerant passage of the internal heat exchanger 19 to raise the enthalpy.
  • the low pressure refrigerant flowing out of the low pressure side refrigerant passage of the internal heat exchanger 19 is sucked into the compressor 11 and compressed again.
  • the dehumidified heating of the vehicle interior can be performed by reheating the blown air cooled and dehumidified by the indoor evaporator 16 by the heater core 22 and blowing it out into the vehicle interior.
  • the operation mode can be switched to realize comfortable air conditioning of the vehicle interior.
  • the refrigerant circuit can be switched with a simple configuration without causing complication of the cycle configuration.
  • the reference temperature KT3 is set so that the low pressure side temperature T3 is lower than the reference temperature KT3 in the heating mode in which the refrigerant circuit is switched not to flow the refrigerant into the indoor evaporator 16. It is done. Therefore, in the heating mode, the low pressure side pressure P3 can be set to a value higher than the saturation pressure of the refrigerant, and the low pressure refrigerant flowing out from the low pressure side refrigerant passage of the internal heat exchanger 19 can be brought into a gas-liquid two-phase state. it can.
  • the cooling refrigerant can be brought into a gas phase state having a degree of superheat. Therefore, when switching to the refrigerant circuit that causes the refrigerant to flow into the indoor evaporator 16 as in the cooling mode or the dehumidifying heating mode, the indoor evaporator 16 efficiently cools the blowing air by the latent heat of vaporization. be able to.
  • the coefficient of performance (COP) of the refrigeration cycle apparatus 10 can be improved by increasing the cooling capacity of the refrigerant in the heat exchanger functioning as the evaporator.
  • the refrigeration cycle apparatus 10 of the present embodiment there is no switching between the refrigerant circuit that causes the high-pressure refrigerant to flow into the same heat exchanger and the refrigerant circuit that causes the low-pressure refrigerant to flow. Therefore, in the refrigerant circuit of any operation mode, the COP improvement effect by providing the internal heat exchanger 19 can be obtained.
  • the chiller 18a is a low temperature side water-refrigerant that exchanges heat between the low pressure refrigerant decompressed by the heat absorption expansion valve 15b and the low temperature heat medium circulating in the low temperature heat medium circuit 30 at least in the heating mode and the dehumidifying heating mode. It is a heat exchanger. Furthermore, the chiller 18a is a heat absorption evaporator that evaporates the low pressure refrigerant to exhibit a heat absorption function. Therefore, the heat source fluid of the present embodiment is a low temperature side heat medium. The chiller 18a is disposed on the front side in the vehicle bonnet.
  • the chiller 18a has a refrigerant passage through which the low pressure refrigerant decompressed by the heat absorption expansion valve 15b flows.
  • merging part 13b is connected to the exit of the refrigerant
  • the chiller 18 a also has a water passage for circulating the low temperature side heat medium circulating in the low temperature side heat medium circuit 30.
  • As the low temperature side heat medium a solution containing ethylene glycol, an antifreeze liquid, etc. can be adopted.
  • the low temperature side heat medium circuit 30 is a low temperature side water circuit for circulating the low temperature side heat medium.
  • the water passage of the chiller 18a, the low temperature side heat medium pump 31, the cooling unit of the in-vehicle device 32, the low temperature side radiator 33, the low temperature side flow rate adjustment valve 34 and the like are arranged.
  • the low temperature side heat medium pump 31 is a low temperature side water pump that pumps the low temperature side heat medium to the inlet side of the water passage of the chiller 18 a in the low temperature side heat medium circuit 30.
  • the basic configuration of the low temperature side heat medium pump 31 is an electric pump similar to the high temperature side heat medium pump 21. Therefore, the low temperature side heat medium pump 31 has its rotation speed (that is, water pressure feeding capacity) controlled by the control voltage output from the air conditioning controller 60.
  • the in-vehicle device 32 is a heat generating device that generates heat when it is activated, and the in-vehicle device of the present embodiment is a battery that supplies an electric quantity to the traveling electric motor. Further, the cooling unit of the on-vehicle device 32 means a heat medium passage formed in the battery in order to absorb the heat generated by the battery at the time of operation such as charging and discharging to the low-pressure side heat medium. .
  • the low temperature side radiator 33 is a heat exchanger which causes the low temperature side heat medium to absorb the heat of the outside air by heat exchange between the low temperature side heat medium cooled by the chiller 18a and the outside air blown from an outside air fan not shown. is there.
  • the low temperature side radiator 33 is disposed on the front side in the vehicle bonnet.
  • the low temperature side radiator 33 may be integrally formed with the chiller 18 a and the like.
  • the cooling unit of the on-vehicle device 32 and the low temperature side radiator 33 are connected in parallel to the flow of the low temperature side heat medium in the low temperature side heat medium circuit 30, as shown in FIG.
  • the low temperature side flow control valve 34 continuously adjusts the low temperature side flow ratio of the flow rate of the low temperature side heat medium flowing into the cooling unit of the in-vehicle device 32 and the flow rate of the low temperature side heat medium flowing into the low temperature side radiator 33 It is a three-way flow control valve of the formula.
  • the basic configuration of the low temperature side flow control valve 34 is similar to that of the high temperature side flow control valve 24.
  • the operation of the low temperature side flow control valve 34 is controlled by a control signal output from the air conditioning controller 60.
  • the low temperature side flow control valve 34 is disposed at a connection portion between the heat medium inlet side of the cooling unit of the on-vehicle device 32 and the heat medium inlet side of the low temperature side radiator 33. That is, the inlet side of the low temperature side flow control valve 34 is connected to the outlet of the water passage of the chiller 18 a.
  • the heat medium inlet side of the cooling unit of the on-vehicle device 32 is connected to one outlet of the low temperature side flow rate adjustment valve 34.
  • the heat medium inlet side of the low temperature side radiator 33 is connected to the other outlet of the low temperature side flow rate adjustment valve 34.
  • the low temperature side flow adjustment valve 34 adjusts the low temperature side flow ratio, whereby the heat absorption amount from the in-vehicle device 32 of the low temperature side heat medium in the cooling unit of the in-vehicle device 32 The heat absorption amount from the outside air of the low temperature side heat medium in the radiator 33 can be adjusted.
  • a battery temperature sensor 62 g that detects the temperature BT of the battery that is the on-vehicle device 32 is connected to the input side of the air conditioning control device 60 of the present embodiment.
  • the other configuration is the same as that of the first embodiment.
  • the operation mode is switched by executing the air conditioning control program.
  • the operation of each operation mode will be described below.
  • (A) Cooling Mode In the cooling mode, the air-conditioning control device 60 opens the cooling on-off valve 14a and closes the heat-absorbing on-off valve 14b, as in the first embodiment. Therefore, a refrigeration cycle identical to the cooling mode of the first embodiment is configured.
  • the air conditioning control device 60 stops the low temperature side heat medium pump 31.
  • the other control target devices are controlled in the same manner as the cooling mode of the first embodiment. Therefore, cooling of the vehicle interior can be performed just as in the first embodiment.
  • (B) Heating mode In the heating mode, the air-conditioning control device 60 closes the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b as in the first embodiment.
  • the compressor 11 high temperature side water-refrigerant heat exchanger 12 ⁇ branching portion 13a ⁇ heat absorbing on-off valve 14b ⁇ heat absorbing expansion valve 15b ⁇ chiller 18a ⁇ merging portion 13b ⁇ compressor
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of 11 is configured.
  • the air conditioning control device 60 operates the low temperature side heat medium pump 31 so as to exert the water pressure transfer capability in the predetermined heating mode.
  • the air conditioning control device 60 refers to the battery temperature BT detected by the battery temperature sensor 62g, and adjusts the low temperature side flow rate so that the battery is maintained within a temperature range in which the battery can exhibit appropriate charge / discharge performance. Control the operation of the valve 34. About other control object apparatus, it controls similarly to the heating mode of 1st Embodiment.
  • the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12.
  • the blown air is heated by the heater core 22, and the temperature of the blown air approaches the target blowing temperature TAO.
  • the low pressure refrigerant decompressed by the heat absorption expansion valve 15b flows into the refrigerant passage of the chiller 18a.
  • the low temperature side heat medium pump 31 since the low temperature side heat medium pump 31 operates, the low pressure refrigerant and the low temperature side heat medium exchange heat, and the low pressure refrigerant absorbs heat from the low temperature side heat medium and evaporates. Thereby, the low temperature side heat medium is cooled. Therefore, the heat source fluid of the present embodiment is the low pressure side heat medium.
  • part of the low temperature side heat medium cooled by the chiller 18a flows into the low temperature side radiator 33 via the low temperature side flow rate adjustment valve 34.
  • the low temperature side heat medium flowing into the low temperature side radiator 33 exchanges heat with the outside air and is heated.
  • the remaining low-temperature side heat medium cooled by the chiller 18 a flows into the cooling unit of the battery, which is the on-vehicle device 32, via the low-temperature side flow rate adjustment valve 34 and is heated.
  • the low temperature side flow control valve 34 adjusts the low temperature side flow ratio so that the temperature at which the battery which is the on-vehicle device 32 can exhibit appropriate charge and discharge performance.
  • the low temperature side heat medium flowing out of the low temperature side radiator 33 and the low temperature side heat medium flowing out of the cooling portion of the in-vehicle apparatus 32 are drawn into the high temperature side heat medium pump 21 and pumped again to the water passage of the chiller 18a.
  • the refrigerant which has flowed out of the refrigerant passage of the chiller 18a is sucked into the compressor 11 via the junction 13b and compressed again.
  • the blowing air heated by the heater core 22 can be blown into the passenger compartment to heat the passenger compartment.
  • (C) Dehumidifying / heating mode In the dehumidifying / heating mode, the air-conditioning control device 60 opens the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b as in the first embodiment.
  • the compressor 11 ⁇ high temperature side water-refrigerant heat exchanger 12 ⁇ branching portion 13a ⁇ cooling on-off valve 14a ⁇ cooling expansion valve 15a ⁇ interior evaporator 16 ⁇ evaporation pressure adjustment
  • the refrigerant circulates in the order of valve 17 ⁇ junction 13b ⁇ compressor 11, and the compressor 11 ⁇ high temperature side water-refrigerant heat exchanger 12 ⁇ branch 13a ⁇ heat absorption on-off valve 14b ⁇ heat absorption expansion valve 15b ⁇ chiller
  • a vapor compression type refrigeration cycle in which the refrigerant circulates in the order of 18a ⁇ the merging portion 13b ⁇ the compressor 11 is configured.
  • the air conditioning control device 60 operates the low temperature side heat medium pump 31 so as to exert the water pressure transfer capability in the predetermined heating mode. Further, as in the heating mode, the air conditioning control device 60 controls the operation of the low temperature side flow control valve 34 so that the battery is maintained within a temperature range in which the battery can exhibit appropriate charge and discharge performance. About other control object apparatus, it controls similarly to the dehumidification heating mode of 1st Embodiment.
  • the high pressure refrigerant discharged from the compressor 11 flows into the high temperature side water-refrigerant heat exchanger 12.
  • the blown air that has passed through the indoor evaporator 16 is heated by the heater core 22, and the temperature of the blown air approaches the target blowing temperature TAO.
  • the flow of the high pressure refrigerant flowing out of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 is branched at the branch portion 13a.
  • One of the refrigerants branched by the branch portion 13a flows into the cooling expansion valve 15a and is decompressed as in the cooling mode.
  • the low pressure refrigerant reduced in pressure by the cooling expansion valve 15 a flows into the indoor evaporator 16.
  • the refrigerant flowing into the indoor evaporator 16 absorbs heat from the air blown from the fan 52 and evaporates. This cools the blowing air.
  • coolant evaporation temperature in the indoor evaporator 16 is maintained by 1 degreeC or more by the effect
  • the other refrigerant branched by the branch portion 13a flows into the heat absorption expansion valve 15b and is decompressed, as in the heating mode.
  • the low pressure refrigerant decompressed by the cooling expansion valve 15a flows into the refrigerant passage of the chiller 18a.
  • the chiller 18a as in the heating mode, since the low temperature side heat medium pump 31 operates, the low pressure refrigerant and the low temperature side heat medium exchange heat, and the low pressure refrigerant absorbs heat from the low temperature side heat medium and evaporates.
  • the low temperature side heat medium absorbs heat from the outside air and the battery as the on-vehicle device 32.
  • the refrigerant flowing out of the refrigerant passage of the chiller 18a merges with the refrigerant flowing out of the evaporation pressure adjusting valve 17 at the joining portion 13b, and is drawn into the compressor 11 and compressed again.
  • dehumidifying and heating the passenger compartment can be performed by reheating the air cooled and dehumidified by the indoor evaporator 16 with the heater core 22 and blowing it out into the passenger compartment.
  • the refrigeration cycle apparatus 10 can switch between the cooling mode, the heating mode, and the dehumidifying heating mode by switching the refrigerant circuit, and the air conditioning in the vehicle interior can be comfortable. Can be realized.
  • the refrigerant circuit can be switched with a simple configuration without causing complication of the cycle configuration.
  • the low temperature side heat medium circuit 30 including the chiller 18a and circulating the low temperature side heat medium is disposed with the battery cooling unit as the on-vehicle device 32 and the low temperature side radiator 33. ing. Then, in the heating mode and in the dehumidifying and heating mode, the refrigerant decompressed by the heat absorption expansion valve 15b is caused to flow into the chiller 18a.
  • the heat of the low temperature side heat medium heated by the waste heat of the on-vehicle device 32 or the outside air is absorbed by the refrigerant, and the heat absorbed by the refrigerant is used as the heat source.
  • the blowing air can be heated.
  • the in-vehicle device 32 can also be cooled.
  • the high-temperature side water-refrigerant heat exchanger 12 the high-temperature side heat medium circuit 20, and the like are eliminated as shown in the overall configuration diagram of FIG.
  • An example in which the indoor condenser 12a and the outdoor heat exchanger 12b are adopted will be described.
  • the indoor condenser 12 a is a heat exchanger that heats the blown air by heat exchange between the high-temperature and high-pressure refrigerant discharged from the compressor 11 and the blown air.
  • the indoor condenser 12 a is disposed in the casing 51 of the indoor air conditioning unit 50 and at the same position as the heater core 22 described in the first embodiment.
  • the outdoor heat exchanger 12b is a heat exchanger that causes the refrigerant flowing out of the indoor condenser 12a and the outside air blown from an outside air fan (not shown) to exchange heat, thereby radiating the heat of the refrigerant to the outside air.
  • the outdoor heat exchanger 12b is disposed on the front side in the vehicle bonnet. Further, on the upstream side of the outdoor heat exchanger 12b at the outdoor air flow side, a shutter mechanism 12c for opening and closing an outdoor air flow path for circulating the outdoor air in the outdoor heat exchanger 12b is disposed.
  • the shutter mechanism 12c closes the outside air passage, heat exchange between the refrigerant and the outside air is not performed in the outdoor heat exchanger 12b.
  • the operation of the shutter mechanism 12 c is controlled by a control signal output from the air conditioning control device 60.
  • the other configuration is the same as that of the first embodiment.
  • the operation mode is switched by executing the air conditioning control program.
  • the operation of each operation mode will be described below.
  • (A) Cooling Mode In the cooling mode, the air-conditioning control device 60 opens the cooling on-off valve 14a and closes the heat-absorbing on-off valve 14b, as in the first embodiment.
  • the compressor 11 ⁇ the indoor condenser 12a ⁇ the outdoor heat exchanger 12b ⁇ the branch portion 13a ⁇ the cooling on-off valve 14a ⁇ the cooling expansion valve 15a ⁇ the indoor evaporator 16 ⁇ evaporation pressure adjustment
  • a vapor compression type refrigeration cycle in which the refrigerant circulates in the order of valve 17 ⁇ junction 13 b ⁇ compressor 11 is configured.
  • the air conditioning control device 60 controls the operation of the shutter mechanism 12c so as to open the outdoor air passage of the outdoor heat exchanger 12b.
  • the other control target devices are controlled in the same manner as the cooling mode of the first embodiment.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12a.
  • the air mix door 54 fully opens the cold air bypass passage 55 to close the air passage on the indoor condenser 12 a side. For this reason, the refrigerant which has flowed into the indoor condenser 12a flows out from the indoor condenser 12a and flows into the outdoor heat exchanger 12b with little heat being released to the blown air.
  • the shutter mechanism 12c opens the outdoor air passage of the outdoor heat exchanger 12b
  • the refrigerant flowing into the outdoor heat exchanger 12b radiates heat and condenses in the outdoor air.
  • the refrigerant that has flowed out of the outdoor heat exchanger 12b flows into the cooling expansion valve 15a via the branch part 13a and the cooling on-off valve 14a and is decompressed.
  • the subsequent operation is the same as that of the cooling mode of the first embodiment.
  • the blowing air cooled by the indoor evaporator 16 can be blown into the vehicle compartment to perform cooling of the vehicle compartment.
  • (B) Heating mode In the heating mode, the air-conditioning control device 60 closes the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b.
  • the compressor 11 ⁇ the indoor condenser 12a ⁇ the outdoor heat exchanger 12b ⁇ the branch portion 13a ⁇ the heat absorption on-off valve 14b ⁇ the heat absorption expansion valve 15b ⁇ the outdoor evaporator 18 ⁇ the junction 13b
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the compressor 11 is configured.
  • the air conditioning control device 60 controls the operation of the shutter mechanism 12c so as to close the outdoor air passage of the outdoor heat exchanger 12b.
  • the air conditioning control device 60 controls similarly to the heating mode of 1st Embodiment.
  • the high temperature / high pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12a.
  • the air mix door 54 closes the cold air bypass passage 55, and the air passage on the indoor condenser 12a side is fully opened.
  • the refrigerant which has flowed into the indoor condenser 12a releases heat to the blown air and condenses.
  • the blowing air is heated, and the temperature of the blowing air approaches the target blowing temperature TAO.
  • the refrigerant flowing out of the indoor condenser 12a flows into the outdoor heat exchanger 12b. Since the shutter mechanism 12c blocks the outdoor air passage of the outdoor heat exchanger 12b, the refrigerant flowing into the outdoor heat exchanger 12b flows out of the outdoor heat exchanger 12b with little heat release to the outside air.
  • the refrigerant that has flowed out of the outdoor heat exchanger 12b flows into the heat absorption expansion valve 15b via the branch portion 13a and the heat absorption opening / closing valve 14b, and is decompressed.
  • the subsequent operation is the same as the heating mode of the first embodiment.
  • the heating mode it is possible to heat the vehicle interior by blowing the blown air heated by the indoor condenser 12a into the vehicle interior.
  • (C) Dehumidifying and Heating Mode In the dehumidifying and heating mode, the air conditioning control device 60 closes the cooling on-off valve 14a and opens the heat-absorbing on-off valve 14b.
  • the compressor 11 ⁇ the indoor condenser 12a ⁇ the outdoor heat exchanger 12b ⁇ the branch portion 13a ⁇ the cooling open / close valve 14a ⁇ the cooling expansion valve 15a ⁇ the indoor evaporator 16 ⁇ evaporation pressure
  • the refrigerant circulates in the order of the adjustment valve 17, the junction 13b, and the compressor 11, and the compressor 11, the indoor condenser 12a, the outdoor heat exchanger 12b, the branch 13a, the heat absorption on-off valve 14b, the heat absorption expansion valve 15b.
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the outdoor evaporator 18, the merging portion 13b, and the compressor 11 is configured.
  • the air conditioning control device 60 controls the operation of the shutter mechanism 12c so as to close the outdoor air passage of the outdoor heat exchanger 12b.
  • the air conditioning control device 60 controls similarly to the dehumidification heating mode of 1st Embodiment.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12a.
  • the high-temperature and high-pressure refrigerant flowing into the indoor condenser 12 a exchanges heat with the air that has passed through the indoor evaporator 16 and radiates heat, as in the heating mode.
  • the blowing air is heated, and the temperature of the blowing air approaches the target blowing temperature TAO.
  • the refrigerant flowing out of the indoor condenser 12a flows into the outdoor heat exchanger 12b. Since the shutter mechanism 12c blocks the outdoor air passage of the outdoor heat exchanger 12b, the refrigerant flowing into the outdoor heat exchanger 12b flows out of the outdoor heat exchanger 12b with little heat release to the outside air.
  • coolant which flowed out out of the outdoor heat exchanger 12b is branched by the branch part 13a.
  • One of the refrigerants branched by the branch portion 13a flows into the cooling expansion valve 15a and is decompressed as in the cooling mode.
  • the other refrigerant branched by the branch portion 13a flows into the heat absorption expansion valve 15b and is decompressed, as in the heating mode.
  • the subsequent operation is the same as in the dehumidifying and heating mode of the first embodiment.
  • the dehumidified heating of the vehicle interior can be performed by reheating the blown air cooled and dehumidified by the indoor evaporator 16 by the indoor condenser 12a and blowing it out into the vehicle interior.
  • the refrigeration cycle apparatus 10 can switch between the cooling mode, the heating mode, and the dehumidifying heating mode by switching the refrigerant circuit, and the air conditioning in the vehicle interior can be comfortable. Can be realized.
  • the refrigerant circuit can be switched with a simple configuration without causing complication of the cycle configuration.
  • the indoor condenser 12a is provided. Therefore, in the heating mode and in the dehumidifying and heating mode, the high-temperature and high-pressure refrigerant discharged from the compressor 11 and the blowing air can be directly heat-exchanged to heat the blowing air.
  • the outdoor heat exchanger 12b is provided. Therefore, the heat absorbed from the blown air can be dissipated to the outside air, and the interior of the vehicle can be cooled.
  • the heat absorbing on / off valve 14b is eliminated, and an electric mechanism that changes the throttle opening degree by an electrical mechanism as a heat absorbing decompressor.
  • An example will be described in which the heat absorption expansion valve 15c of the formula (hereinafter referred to as the electric expansion valve 15c) is adopted.
  • the electric expansion valve 15c is a heat absorption pressure reducing portion that reduces the pressure of the refrigerant flowing out of the other refrigerant outlet of the branch portion 13a.
  • the electric expansion valve 15c includes a valve body configured to be capable of changing the throttle opening degree, and an electric actuator (specifically, a stepping motor) that changes the opening degree of the valve body. Is a variable stop mechanism of the formula.
  • the operation of the electric expansion valve 15 c is controlled by a control signal (control pulse) output from the air conditioning controller 60. Further, the electric expansion valve 15c has a fully closing function of closing the refrigerant passage by fully closing the valve opening degree. Therefore, the electric expansion valve 15c of the present embodiment also has a function as a circuit switching unit.
  • an outlet side temperature sensor 62h and an outlet side pressure sensor 62i are connected to the input side of the air conditioning control device 60 of the present embodiment.
  • the outlet side temperature sensor 62 h is an outlet side temperature detection unit that detects the outlet side temperature Te 1 of the refrigerant on the outlet side of the outdoor evaporator 18.
  • the outlet-side pressure sensor 62i is an outlet-side pressure detection unit that detects the outlet-side pressure Pe1 of the refrigerant on the outlet side of the outdoor evaporator 18.
  • operation of the electrical expansion valve 15c among the air-conditioning control apparatuses 60 of this embodiment is the thermal expansion valve control part 60b.
  • the change in the heat absorption pressure P2 corresponding to the change in the heat absorption temperature T2 during the normal operation in the heating mode and the dehumidifying heating mode is as shown in FIG. 2 of the first embodiment.
  • the operation of the electric expansion valve 15c is controlled so as to approach the heat absorption characteristic line CL2 indicated by the broken line.
  • the air conditioning control device 60 not only the outlet temperature Te1 detected by the outlet temperature sensor 62h and the outlet pressure Pe1 detected by the outlet pressure sensor 62i but also detection signals from other sensors. Based on the control map, the control map stored in advance in the air conditioning control device 60 is used to control the operation of the electric expansion valve 15c.
  • the heat absorption expansion valve control unit 60b operates the electric expansion valve 15c so that the change in the heat absorption pressure P2 corresponding to the change in the heat absorption temperature T2 approaches the heat absorption characteristic line CL2. I have control. Therefore, in the refrigeration cycle apparatus 10 of the present embodiment, as in the first embodiment, the cooling mode, the heating mode, and the dehumidifying heating mode can be switched, and comfortable air conditioning of the vehicle interior can be realized.
  • the refrigerant circuit can be switched with a simple configuration without causing complication of the cycle configuration.
  • the air conditioning control device 60 of the present embodiment has a frosting determination unit 60c.
  • the frost formation determination unit 60c is a control program that determines whether frost formation has occurred in the outdoor evaporator 18.
  • the frost formation determining unit 60c is executed at predetermined intervals as a subroutine of the air conditioning control program.
  • the outlet side temperature Te1 detected by the outlet side temperature sensor 62h subtracts a predetermined reference temperature ⁇ from the outside air temperature Tam detected by the outside air temperature sensor.
  • a control program is employed that determines that frost is formed on the outdoor heat exchanger 18.
  • the frost formation determination unit 60c determines that frost formation has occurred in the outdoor evaporator 18 while the heating mode and the dehumidifying and heating mode are being performed, the operation in the defrost mode is performed.
  • the air conditioning control device 60 increases the throttle opening degree of the electric expansion valve 15c. Thereby, the temperature of the refrigerant flowing into the outdoor evaporator 18 can be raised to melt and defrost the frost generated in the outdoor evaporator 18.
  • the defrosting mode is continued until a predetermined reference defrosting time elapses.
  • the defrosting mode can be executed by changing the throttle opening degree of the electric expansion valve 15c. it can.
  • refrigeration cycle device 10 concerning this indication to an air-conditioner for electric vehicles
  • application of refrigeration cycle device 10 is not limited to this.
  • the present invention may be applied to an air conditioner for a hybrid vehicle that obtains driving force for traveling the vehicle from both an internal combustion engine and an electric motor.
  • the present invention is not limited to vehicles, and may be applied to stationary air conditioners and the like.
  • the refrigeration cycle apparatus 10 may be applied to, for example, an air conditioner that does not operate in the cooling mode.
  • the high temperature side radiator 23 of the high temperature side heat medium circuit 20 described in the first to third and fifth embodiments may be eliminated.
  • the outdoor heat exchanger 12b described in the fourth embodiment may be eliminated.
  • the cooling only operation mode In the cooling only operation mode, the low temperature side heat medium absorbs heat absorbed by the on-vehicle device 32 to the refrigerant, and the heat is dissipated in the high temperature side radiator 23 or the outdoor heat exchanger 12b. According to this, it is possible to cool the in-vehicle device 32 without air conditioning the vehicle interior.
  • the low pressure refrigerant is made to flow into both the indoor evaporator 16 and the outdoor evaporator 18 or the chiller 18a as in the dehumidifying and heating mode at the time of the cooling mode described above, cooling of the vehicle interior is simultaneously performed.
  • the in-vehicle device 32 can be cooled.
  • the operation mode may be switched according to the outside air temperature Tam.
  • the heating mode ⁇ dehumidifying heating mode ⁇ cooling mode may be switched in accordance with the rise of the outside air temperature Tam.
  • the time when the outside air temperature Tam is a temperature at which the dehumidifying and heating mode is switched to the heating mode may be set as a time when a predetermined condition is satisfied.
  • the operation mode may be switched according to the refrigerant evaporation temperature in the indoor evaporator 16 and the outdoor evaporator 18 (or the chiller 18a).
  • the heating mode ⁇ the dehumidifying heating mode ⁇ the cooling mode may be switched in the order as the refrigerant evaporation temperature rises. Then, when the refrigerant evaporation temperature in the outdoor evaporator 18 (or the chiller 18a) is a temperature at which the dehumidifying and heating mode is switched to the heating mode, a predetermined condition may be satisfied.
  • the frosting determination unit 60c described in the fifth embodiment described above is not limited to the determination unit that determines whether frosting actually occurs in the outdoor evaporator 18.
  • a determination unit that determines whether or not there is an operating condition that may cause frost formation on the outdoor evaporator 18, or a determination unit that determines whether or not frost formation may occur on the outdoor evaporator 18 It may be.
  • the frost formation determination unit 60c causes frost formation on the outdoor evaporator 18
  • a control program that determines that there is a program may be employed. In this case, it is desirable to set the frost formation reference temperature to a value lower than 0 ° C.
  • Each composition of refrigerating cycle device 10 is not limited to what was indicated by the above-mentioned embodiment.
  • the receiver is disposed in the refrigerant passage extending from the outlet of the refrigerant passage of the high temperature side water-refrigerant heat exchanger 12 to the refrigerant inlet of the branch portion 13a.
  • the receiver is a gas-liquid separation unit that separates the gas and liquid of the refrigerant flowing into the inside and stores the excess liquid phase refrigerant of the cycle.
  • the receiver may be disposed in the refrigerant flow path extending from the refrigerant outlet of the outdoor heat exchanger 12b to the refrigerant inlet of the branch portion 13a.
  • the branch portion 13a has a three-way joint structure.
  • the flow rate of the refrigerant flowing into the cooling expansion valve 15a and the heat absorption expansion valve 15b An electric three-way flow control valve may be employed to adjust the refrigerant flow ratio to the refrigerant flow rate. That is, the branch unit and the circuit switching unit may be integrally configured.
  • the arrangement of the cooling on-off valve 14a and the heat-absorbing on-off valve 14b is not limited to the refrigerant flow upstream side of the cooling pressure reducing portion and the heat-absorbing pressure reducing portion. It may be disposed downstream of the refrigerant flow downstream of the cooling pressure reducing portion and the heat absorbing pressure reducing portion.
  • the thermal expansion valve is adopted as the cooling pressure reducing portion and the electric expansion valve is adopted as the heat absorbing pressure reducing portion.
  • the electric expansion valve as the cooling pressure reducing portion
  • a thermal expansion valve may be employed as the heat absorption pressure reducing portion.
  • the low-pressure refrigerant passage of the internal heat exchanger 19 is disposed downstream of the junction 13b.
  • the arrangement of the low-pressure refrigerant passage is not limited to this.
  • the low pressure side refrigerant passage may be disposed downstream of the refrigerant flow of the heat absorption evaporator and upstream of the merging portion 13b.
  • the low temperature side radiator 33 and the battery as the in-vehicle device 32 are disposed in the low temperature side heat medium circuit 30, but the low temperature side radiator 33 and the in-vehicle device At least one of 32 may be disposed.
  • the on-vehicle device 32 is not limited to the battery, and may be any heat-generating device that generates heat during operation.
  • an electric motor that outputs a driving force for traveling
  • an inverter that converts the frequency of electric power supplied to the electric motor
  • a charger for charging the battery with electric power, or the like may be adopted.
  • a plurality of heat generating devices may be adopted as the on-vehicle device 32 and connected in parallel or in series to the flow of the low temperature side heat medium.
  • the high temperature side radiator 23 and the low temperature side radiator 33 are not limited to the mutually independent structure.
  • the high temperature side radiator 23 and the low temperature side radiator 33 may be integrated so that the heat possessed by the high temperature side heat carrier and the heat possessed by the low temperature side heat carrier can be mutually transferred.
  • the heat mediums may be integrated so as to be capable of transferring heat by sharing a part of components (for example, heat exchange fins) of the high temperature side radiator 23 and the low temperature side radiator 33.
  • coolant is not limited to this.
  • R1234yf, R600a, R410A, R404A, R32, R407C, etc. may be adopted.
  • the outdoor evaporator 18 of the refrigeration cycle apparatus 10 including the internal heat exchanger 19 described in the second embodiment is eliminated, and the chiller 18a, the low temperature side heat medium circuit 30 and the like are applied as in the third embodiment. You may
  • the internal heat exchanger 19 described in the second embodiment may be applied to the refrigeration cycle apparatus 10 including the indoor condenser 12a and the like as the heating unit described in the fourth embodiment, and the third embodiment.
  • the chiller 18a and the low temperature side heat medium circuit 30 described in the above may be applied.
  • the electric expansion valve 15c similar to that of the fifth embodiment may be employed as the heat absorption pressure reducing portion of the refrigeration cycle apparatus 10 described in the second to fourth embodiments.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
PCT/JP2018/028966 2017-08-31 2018-08-02 冷凍サイクル装置 Ceased WO2019044353A1 (ja)

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CN201880055683.7A CN111065866A (zh) 2017-08-31 2018-08-02 制冷循环装置
US16/799,467 US11787258B2 (en) 2017-08-31 2020-02-24 Refrigeration cycle device

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WO2022249790A1 (ja) * 2021-05-24 2022-12-01 株式会社デンソー 冷凍サイクル装置
JP7512952B2 (ja) 2021-05-24 2024-07-09 株式会社デンソー 冷凍サイクル装置
WO2023182106A1 (ja) * 2022-03-21 2023-09-28 株式会社デンソー 冷凍サイクル装置
JP2023138890A (ja) * 2022-03-21 2023-10-03 株式会社デンソー 冷凍サイクル装置
JP7666372B2 (ja) 2022-03-21 2025-04-22 株式会社デンソー 冷凍サイクル装置

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JP2019045034A (ja) 2019-03-22
US11787258B2 (en) 2023-10-17
DE112018004831T5 (de) 2020-06-10

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