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WO2019065013A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2019065013A1
WO2019065013A1 PCT/JP2018/031062 JP2018031062W WO2019065013A1 WO 2019065013 A1 WO2019065013 A1 WO 2019065013A1 JP 2018031062 W JP2018031062 W JP 2018031062W WO 2019065013 A1 WO2019065013 A1 WO 2019065013A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
refrigeration cycle
compressor
temperature side
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/JP2018/031062
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English (en)
Japanese (ja)
Inventor
卓哉 布施
加藤　吉毅
直也 牧本
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
Publication of WO2019065013A1 publication Critical patent/WO2019065013A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus.
  • Patent Document 1 shows a vapor compression type refrigeration cycle apparatus applied to an air conditioner, in which heat is exchanged between a high pressure refrigerant discharged from a compressor and air that is a fluid to be heat-exchanged, so that the blown air is obtained.
  • a refrigeration cycle apparatus for heating is disclosed.
  • a refrigeration oil for lubricating the compressor is mixed with the refrigerant, and the refrigeration oil is circulated in the cycle together with the refrigerant. Furthermore, in such a refrigeration cycle apparatus, in order to reliably return the refrigeration oil to the compressor, oil return control is performed which periodically changes the circulating refrigerant flow rate of the refrigerant circulating in the cycle.
  • the pressure of the high-pressure refrigerant fluctuates, and the heating capacity of the heat exchange target fluid may also fluctuate.
  • An object of the present disclosure is to provide a refrigeration cycle apparatus capable of suppressing fluctuation in heating capacity of a fluid to be heat-exchanged when returning refrigeration oil to a compressor.
  • the refrigeration cycle apparatus performs a heat exchange between the refrigerant discharged from the compressor and the fluid discharged by heat exchange between the refrigerant discharged from the compressor and the compressor that compresses and discharges the refrigerant mixed with the refrigeration oil. It has a refrigeration cycle provided with a condenser to be condensed, and an oil return control execution unit that executes oil return control for returning refrigeration oil to the compressor by changing the circulating refrigerant flow rate of the refrigerant circulating in the refrigeration cycle. The condensed refrigerant is subcooled at least when the oil return control is performed.
  • the refrigeration oil can be returned to the compressor.
  • the pressure fluctuation of the refrigerant discharged from the compressor is suppressed by adjusting the amount of subcooling. be able to. Therefore, the fluctuation of the heating capacity of the heat exchange target fluid can also be suppressed.
  • the condenser is not limited to the one that directly exchanges heat between the refrigerant and the heat exchange fluid, but also includes one that indirectly exchanges heat between the refrigerant and the heat exchange fluid via a heat medium or the like.
  • the refrigeration cycle apparatus 1 shown in FIG. 1 is applied to a vehicle air conditioner that adjusts the interior space of a vehicle to an appropriate temperature.
  • the refrigeration cycle apparatus 1 of the present embodiment is mounted on a hybrid vehicle that obtains a driving force for vehicle traveling from an engine (in other words, an internal combustion engine) and a traveling electric motor.
  • the hybrid vehicle of the present embodiment is configured as a plug-in hybrid vehicle capable of charging the battery 47 mounted on the vehicle with electric power supplied from an external power supply (in other words, a commercial power supply) when the vehicle is stopped.
  • an external power supply in other words, a commercial power supply
  • the driving force output from the engine is used not only for driving the vehicle but also for generating electric power in a motor generator 51 described later.
  • the electric power generated by the motor generator 51 and the electric power supplied from the external power supply can be stored in the battery 47.
  • the electric power stored in the battery 47 constitutes the refrigeration cycle apparatus 1 as well as the electric motor for traveling. It is supplied to various in-vehicle devices including electric component devices.
  • the refrigeration cycle apparatus 1 functions to heat the passenger compartment, which is an air conditioning target space (that is, heat the blown air that is a heat exchange target fluid), and to cool the passenger compartment (that is, to cool the blown air). .
  • the refrigeration cycle apparatus 1 includes a refrigeration cycle 10, a high temperature side heat exchange unit 30, a low temperature side heat exchange unit 40, and an indoor air conditioning unit 60.
  • the refrigeration cycle 10 includes a compressor 11, a condenser 12, a liquid receiver 13, a supercooling unit 14, a first pressure reducing valve 15 (pressure reducing unit), a first evaporator 16, a second pressure reducing valve 17 (pressure reducing unit), A second evaporator 18, an evaporation pressure control valve 19, a refrigerant circuit 20, and a second evaporator flow path 21 are provided.
  • a fluorocarbon-based refrigerant is used as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure refrigerant pressure does not exceed the critical pressure of the refrigerant is configured.
  • 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.
  • the refrigerant circuit 20 is an annular flow path.
  • the compressor 11, the condenser 12 (water-refrigerant heat exchanger), the liquid receiver 13, the subcooling unit 14, the first pressure reducing valve 15, and the first evaporator 16 are in the refrigerant flow direction. It is provided in this order of arrangement.
  • the compressor 11 is an electric compressor driven by the electric power supplied from the battery 47, and sucks, compresses and discharges the refrigerant flowing through the refrigerant circuit 20.
  • the operation of the compressor 11 is controlled by a control signal output from the controller 70.
  • the refrigerant inlet side of the condenser 12 is connected to the discharge port of the compressor 11.
  • the condenser 12 performs heat exchange between the high-temperature and high-pressure refrigerant (hereinafter, abbreviated as high-pressure refrigerant) discharged from the compressor 11 and the cooling water as the high-temperature side heat medium to release the heat of the high-pressure refrigerant to the cooling water.
  • Water-refrigerant heat exchanger that heats the cooling water.
  • the high pressure refrigerant condenses when the heat of the high pressure refrigerant is dissipated to the cooling water.
  • the high temperature side heat exchange unit 30 has a high temperature side heat medium flow channel 31, a high temperature side pump 32, a heater core 33, a reservoir 34, a high temperature side radiator 35, a high temperature side radiator flow channel 36, and a high temperature side flow channel switching valve 37 There is.
  • the high temperature side heat exchange unit 30 is a heating unit that heats the blown air using the high pressure refrigerant discharged from the compressor 11 as a heat source.
  • the cooling water flowing in the high temperature side heat medium flow channel 31 and the cooling water flowing in the low temperature side heat medium flow channel 41 described later use a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid It is done.
  • the high temperature side heat medium flow channel 31 is an annular flow channel that circulates the cooling water between the condenser 12 and the heater core 33.
  • the supercooling unit 14, the condenser 12, the heater core 33, and the high temperature side pump 32 are arranged in this order in the flow direction of the cooling water.
  • the high temperature side pump 32 circulates the cooling water in the high temperature side heat medium flow path 31 by sucking the cooling water and discharging it to the condenser 12 side.
  • the high temperature side pump 32 is an electric pump driven by the electric power supplied from the battery 47, and is a high temperature side flow rate adjustment unit that adjusts the flow rate of the cooling water circulating in the high temperature side heat medium passage 31.
  • the heater core 33 is disposed in a casing 61 of an indoor air conditioning unit 60 described later.
  • the heater core 33 heats the blowing air by heat exchange between the cooling water heated by the condenser 12 and the blowing air which is a fluid for heat exchange. That is, in the condenser 12 of the present embodiment, the high pressure refrigerant discharged from the compressor 11 and the blowing air as the heat exchange fluid are indirectly heat-exchanged via the cooling water which is the high temperature side heat medium.
  • the reservoir 34 is a liquid storage unit that is connected to the high temperature side heat medium flow channel 31 and stores excess cooling water flowing in the high temperature side heat medium flow channel 31.
  • the high temperature side radiator flow passage 36 is connected to the high temperature side heat medium flow passage 31 on the downstream side of the heater core 33, and the other end of the high temperature side radiator flow passage 36 is on the high temperature side heat medium upstream of the high temperature side pump 32 It is connected to the flow path 31.
  • the high temperature side radiator flow passage 36 is provided with a high temperature side radiator 35 and a high temperature side flow passage switching valve 37.
  • the high temperature side radiator 35 cools the cooling water heated by the condenser 12 by exchanging heat with the outside air blown by a radiator blower 54 described later.
  • the high temperature side radiator 35 is disposed on the front side in the vehicle bonnet. Therefore, the traveling wind can be applied to the high temperature side radiator 35 when the vehicle travels.
  • the high temperature side flow passage switching valve 37 switches the state in which the cooling water flowing in the high temperature side heat medium flow passage 31 flows in the high temperature side radiator flow passage 36 and the state in which the cooling water does not flow.
  • the high temperature side flow passage switching valve 37 is an electric two-way valve whose operation is controlled by a control signal output from the control device 70, and has a valve body and an electric actuator.
  • the liquid receiver 13 is connected to the refrigerant outlet side of the condenser 12.
  • the liquid receiver 13 separates the gas and liquid of the refrigerant flowing out of the condenser 12 and stores excess refrigerant in the refrigeration cycle 10.
  • the supercooling unit 14 is connected to the refrigerant outlet side of the liquid receiving unit 13. That is, the subcooling unit 14 is provided on the downstream side of the condenser 12.
  • the supercooling unit 14 exchanges heat between the liquid-phase refrigerant flowing out of the condenser 12 through the liquid receiving unit 13 and the cooling water discharged from the high-temperature side pump 32 and before flowing into the condenser 12, thereby performing liquid-phase refrigerant To overcool.
  • the subcooling unit 14 lowers the enthalpy of the refrigerant flowing into the first evaporator 16 and the second evaporator 18 to increase the cooling capacity that can be exhibited by the first evaporator 16 and the second evaporator 18. Can.
  • the first pressure reducing valve 15 is connected to the refrigerant outlet side of the subcooling unit 14.
  • the first pressure reducing valve 15 is an electric variable throttle mechanism whose operation is controlled by a control signal output from the control device 70, and has a valve body and an electric actuator.
  • the valve body is configured to be capable of changing the flow path opening degree (in other words, the throttle opening degree) of the refrigerant circuit.
  • the electric actuator has a stepping motor that changes the throttle opening of the valve body.
  • the first pressure reducing valve 15 can close the refrigerant circuit 20.
  • the refrigerant inlet of the first evaporator 16 is connected to the refrigerant outlet side of the first pressure reducing valve 15.
  • the first evaporator 16 exchanges the heat of the low-pressure refrigerant decompressed by the first pressure reducing valve 15 with the cooling water, which is the low-stage-side heat medium flowing through the low-temperature heat exchange unit 40, thereby converting the low-pressure refrigerant.
  • the low-pressure refrigerant absorbs heat from the cooling water and evaporates to cool the cooling water.
  • One end of the second evaporator channel 21 is connected to the refrigerant circuit 20 between the subcooling unit 14 and the first pressure reducing valve 15, and the other end of the second evaporator channel 21 is compressed with the first evaporator 16 and the first evaporator 16 It is connected to a refrigerant circuit 20 between itself and the machine 11.
  • a second pressure reducing valve 17, a second evaporator 18, and an evaporation pressure adjusting valve 19 are arranged in this order in the refrigerant flow direction.
  • the second pressure reducing valve 17 is connected to the refrigerant outlet side of the subcooling unit 14.
  • the second pressure reducing valve 17 is an electric variable throttle mechanism whose operation is controlled by a control signal output from the control device 70, and has a valve body and an electric actuator.
  • the valve body is configured to be capable of changing the flow path opening degree (in other words, the throttle opening degree) of the refrigerant circuit.
  • the electric actuator has a stepping motor that changes the throttle opening of the valve body.
  • the second pressure reducing valve 17 can close the refrigerant circuit 20 (more specifically, the second evaporator flow passage 21).
  • the refrigerant inlet of the second evaporator 18 is connected to the refrigerant outlet side of the second pressure reducing valve 17.
  • the second evaporator 18 is disposed in the casing 61 of the indoor air conditioning unit 60.
  • the second evaporator 18 is a cooling heat exchanger that evaporates the low-pressure refrigerant by exchanging heat between the heat of the low-pressure refrigerant decompressed by the second pressure reducing valve 17 and the blown air flowing in the casing 61. .
  • the low pressure refrigerant absorbs heat from the blowing air and evaporates to cool the blowing air.
  • the evaporation pressure adjustment valve 19 is an evaporation pressure adjustment unit that maintains the refrigerant evaporation pressure in the second evaporator 18 at or above a predetermined reference pressure.
  • the evaporation pressure control valve 19 is configured by a mechanical variable throttle mechanism that increases the valve opening degree as the refrigerant pressure on the outlet side of the second evaporator 18 increases.
  • the refrigerant evaporation temperature in the second evaporator 18 is equal to or higher than the frost formation suppression reference temperature (specifically, 1 ° C.) capable of suppressing frost formation in the second evaporator 18.
  • the low temperature side heat exchange unit 40 includes the low temperature side heat medium flow channel 41, the battery flow channel 42, the in-vehicle device flow channel 43, the in-vehicle device bypass flow channel 44, the low temperature side pump 45, the first low temperature side flow channel switching valve 46, and the battery
  • An on-vehicle apparatus flow path pump 48, an inverter 49, a charger 50, a motor generator 51, a second low temperature flow path switching valve 52, a low temperature radiator 53, and a radiator blower 54 are provided.
  • the low temperature side heat medium flow channel 41 is an annular flow channel, and the cooling water which is the low stage side heat medium circulates.
  • the low temperature side pump 45, the first evaporator 16, the low temperature side radiator 53, and the first low temperature side flow passage switching valve 46 are arranged in this order of arrangement with respect to the cooling water flow. There is.
  • the low temperature side pump 45 is an electric pump driven by the power supplied from the battery 47, and sucks and discharges the cooling water flowing through the low temperature side heat medium channel 41.
  • the operation of the low temperature side pump 45 is controlled by a control signal output from the controller 70 (shown in FIG. 2).
  • One end of the battery flow path 42 is connected to the first low temperature side flow path switching valve 46, and the other end of the battery flow path 42 is connected to the low temperature side heat medium flow path 41 on the downstream side of the first evaporator 16 There is.
  • the low temperature side radiator 53 absorbs heat by causing the cooling water cooled by the first evaporator 16 to exchange heat with the outside air blown by the radiator blower 54.
  • the radiator blower 54 is an electric blower that drives a fan by an electric motor, and its operation is controlled by a control signal output from the control device 70.
  • the low temperature side radiator 53 is disposed on the front side in the vehicle bonnet. Therefore, the traveling wind can be applied to the low temperature side radiator 53 when the vehicle travels.
  • a battery 47 is disposed in the battery flow path 42.
  • Battery 47 is electrically connected to inverter 49 and charger 50 to supply current to inverter 49 and store the current supplied from charger 50.
  • a lithium ion battery can be used as the battery 47.
  • the battery 47 is cooled by the cooling water flowing through the battery flow channel 42.
  • the first low temperature side flow passage switching valve 46 is disposed at a connection portion between the low temperature side heat medium flow passage 41 and the battery flow passage 42.
  • the first low temperature side flow passage switching valve 46 switches between the state in which the cooling water flowing in the low temperature side heat medium flow path 41 flows in the battery flow path 42 and the state in which the cooling water does not flow.
  • the first low temperature side flow passage switching valve 46 is an electric three-way valve whose operation is controlled by a control signal output from the control device 70, and has a valve body and an electric actuator.
  • One end of the in-vehicle apparatus flow path 43 is connected to the low-temperature side heat medium flow path 41 between the low-temperature side radiator 53 and the first low-temperature side flow path switching valve 46. It is connected to the low temperature side heat medium channel 41 between the evaporator 16 and the low temperature side radiator 53.
  • the in-vehicle device flow path pump 48, the inverter 49, the charger 50, the motor generator 51, and the second low temperature side flow passage switching valve 52 are arranged in this order of arrangement for the cooling water flow. There is.
  • the on-vehicle apparatus flow path pump 48 is an electric pump driven by the electric power supplied from the battery 47, and sucks and discharges the cooling water flowing through the on-vehicle apparatus flow path 43.
  • the operation of the on-vehicle apparatus channel pump 48 is controlled by a control signal output from the controller 70 (shown in FIG. 2).
  • the inverter 49 adjusts the voltage of the power supplied from the battery 47 and supplies the power to the motor generator 51 to drive the motor generator 51.
  • the inverter 49 is cooled by the cooling water flowing through the in-vehicle apparatus channel 43.
  • Charger 50 regulates the voltage of the power generated by motor generator 51 and charges battery 47 with this power.
  • the charger 50 is cooled by the cooling water flowing through the in-vehicle apparatus channel 43.
  • the motor generator 51 generates driving force by the electric power supplied from the inverter 49 and generates regenerative braking force by generating electric power.
  • the motor generator 51 is cooled by the cooling water flowing through the in-vehicle apparatus channel 43.
  • One end of the in-vehicle device bypass passage 44 is connected to the suction side of the in-vehicle device passage pump 48 in the in-vehicle device passage 43, and the other end of the in-vehicle device bypass passage 44 is the second low temperature side passage switching valve 52. It is connected to the.
  • the second low temperature side flow passage switching valve 52 switches between a state in which the coolant flows in the in-vehicle device bypass flow path 44 between the in-vehicle device flow path pump 48 and the motor generator 51 and a state in which the coolant does not flow.
  • the second low temperature side flow passage switching valve 52 is an electric three-way valve whose operation is controlled by a control signal output from the control device 70, and has a valve body and an electric actuator.
  • the indoor air conditioning unit 60 is for blowing the blown air into the vehicle compartment which is the space to be air conditioned.
  • the indoor air conditioning unit 60 is disposed inside the instrument panel at the forefront of the vehicle interior.
  • the indoor air conditioning unit 60 is configured by housing the second evaporator 18, the heater core 33, and the like in a casing 61 forming the outer shell thereof.
  • the casing 61 is an air passage forming portion that forms an air passage for blowing air blown into the vehicle compartment, which is a space to be air conditioned.
  • the casing 61 has a certain degree of elasticity and is molded of a resin (for example, polypropylene) which is excellent in strength.
  • a device 63 is arranged inside / outside air switching as an inside / outside air switching unit to switch and introduce inside air (air within the air conditioned space) and outside air (air outside the air conditioned space) into the casing 61 on the most upstream side of the air flow inside the casing 61
  • a device 63 is arranged.
  • the inside / outside air switching device 63 can continuously change the air volume ratio between the air volume of the inside air and the air volume of the outside air.
  • an air conditioning blower 62 for directing the air drawn in via the inside / outside air switching device 63 toward the inside of the space to be air-conditioned is disposed.
  • the air conditioning blower 62 is an electric blower that drives a centrifugal multi-blade fan (sirocco fan) by an electric motor, and the number of rotations (air flow amount) is controlled by a control voltage output from the control device 70.
  • the second evaporator 18 is disposed downstream of the air flow of the air conditioning blower 62 in the air passage formed in the casing 61. Further, the downstream side of the second evaporator 18 of the air passage formed in the casing 61 is bifurcated, and the heater core flow passage 65 and the cold air bypass passage 66 are formed in parallel.
  • the heater core flow path 65 a heater core 33 is disposed. That is, the heater core flow path 65 is a flow path through which the blown air which exchanges heat with the refrigerant in the heater core 33 flows.
  • the second evaporator 18 and the heater core 33 are disposed in this order with respect to the blowing air flow. In other words, the second evaporator 18 is disposed upstream of the heater core 33 in the flow of the blast air.
  • the cold air bypass passage 66 is a flow passage for flowing the blown air that has passed through the second evaporator 18 to the downstream side by bypassing the heater core 33.
  • the air mix door 64 which adjusts the air volume ratio which makes the heater core 33 pass among these is arrange
  • a mixing channel 67 is formed in the casing 61 on the downstream side of the merging portion of the heater core channel 65 and the cold air bypass passage 66. In the mixing flow path 67, the blowing air heated by the heater core 33 and the blowing air which has passed through the cold air bypass passage 66 and is not heated by the heater core 33 are mixed.
  • a plurality of opening holes for blowing the blowing air (air conditioning air) mixed in the mixing flow path 67 into the vehicle interior which is the air conditioning target space at the most downstream part of the blowing air flow of the casing 61 Is arranged.
  • the control device 70 shown in FIG. 2 is composed of a known microcomputer including a CPU, a ROM, a RAM and the like, and peripheral circuits thereof.
  • the control device 70 performs various operations and processing based on the control program stored in the ROM.
  • Various control target devices are connected to the output side of the control device 70.
  • the control device 70 is a control unit that controls the operation of various control target devices.
  • the control target devices controlled by the control device 70 include the compressor 11, the first pressure reducing valve 15, the second pressure reducing valve 17, the high temperature side pump 32, the high temperature side flow path switching valve 37, the low temperature side pump 45, and the first low temperature side.
  • the control device 70 is integrally configured with a control unit that controls various control target devices connected to the output side. And the structure (hardware and software) which controls the action
  • the configuration for controlling the refrigerant discharge capacity of the compressor 11 in the control device 70 is a discharge capacity control unit 70a.
  • the configuration for controlling the throttle opening degree of the first pressure reducing valve 15 is a first throttle control unit 70b.
  • the configuration for controlling the throttle opening degree of the second pressure reducing valve 17 is a second throttle control unit 70c.
  • the configuration for controlling the pumping capability of the high temperature side pump 32 is the high temperature side pumping capability control unit 70d.
  • the configuration for controlling the pumping capability of the low temperature side pump 45 is the low temperature side pumping capability control unit 70 e.
  • the configuration for controlling the air blowing capacity of the radiator fan 54 is a radiator air blowing capacity control unit 70f.
  • the configuration for controlling the blowing capacity of the air conditioning blower 62 is the air conditioning blowing capacity control unit 70g.
  • control sensor groups such as an inside air temperature sensor 71, an outside air temperature sensor 72, a solar radiation amount sensor 73, a refrigerant temperature sensor 74, and a refrigerant pressure sensor 75 are connected to the input side of the control device 70.
  • the inside air temperature sensor 71 detects a temperature Tr in the passenger compartment.
  • the outside air temperature sensor 72 detects the outside air temperature Tam.
  • the solar radiation amount sensor 73 detects the solar radiation amount Ts in the vehicle compartment.
  • the refrigerant temperature sensor 74 detects the temperature of the refrigerant circulating through the refrigeration cycle 10, for example, the temperature of the refrigerant sucked by the compressor 11.
  • the refrigerant pressure sensor 75 detects the pressure of the refrigerant on the low pressure side of the refrigeration cycle 10, for example, the pressure of the refrigerant drawn into the compressor 11.
  • An operation unit 80 is connected to the input side of the control device 70.
  • the operating unit 80 is operated by the occupant.
  • the operation unit 80 is disposed in the vicinity of an instrument panel at the front of the vehicle interior.
  • An operation signal from the operation unit 80 is input to the control device 70.
  • the operation unit 80 is provided with an air conditioner switch, a temperature setting switch, and the like.
  • the air conditioner switch sets whether to cool the blowing air in the indoor air conditioning unit.
  • the temperature setting switch sets the set temperature of the vehicle interior.
  • the control device 70 when the air conditioner switch is turned on (ON), the air conditioning control program stored in advance in the storage circuit (ROM) is executed.
  • the target blowout temperature TAO of the air blown into the vehicle compartment is calculated based on the detection signal detected by the control sensor group and the operation signal from the operation unit 80.
  • the operation mode of the refrigeration cycle apparatus 1 is determined based on the detection signal, the operation signal, and the target blowout temperature TAO. More specifically, in the refrigeration cycle apparatus 1 of the present embodiment, the heating mode, the cooling mode, and the dehumidifying heating mode can be switched as the operation mode. Each operation mode will be described below.
  • the heating mode is an operation mode in which the air is heated by the heater core 33.
  • the control device 70 determines the operation states (control signals to be output to the various control devices) of the various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 70 operates the compressor 11, the high temperature side pump 32, the low temperature side pump 45, the radiator blower 54, the air conditioning blower 62 and the like.
  • control device 70 controls compressor 11 such that the temperature of the air blown into the vehicle compartment becomes the target blowing temperature TAO.
  • the controller 70 brings the first pressure reducing valve 15 into the throttling state, and brings the second pressure reducing valve 17 into the fully closed state.
  • the control device 70 determines a control signal to be output to the first pressure reducing valve 15 so as to have a predetermined opening degree of the heating mode.
  • the control device 70 fully closes the high temperature side flow passage switching valve 37.
  • the control device 70 controls the operation of the first low temperature side flow passage switching valve 46 so that the cooling water does not flow through the battery flow passage 42.
  • the control device 70 controls the operation of the second low temperature side flow passage switching valve 52 so that the cooling water does not flow through the in-vehicle device bypass flow passage 44.
  • the control device 70 displaces the air mix door 64 to the solid line position of FIG. 1 and distributes the entire flow rate of the blown air having passed through the second evaporator 18 to the heater core flow path 65.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the high pressure refrigerant flowing into the condenser 12 exchanges heat with the cooling water pressure-fed from the high temperature side pump 32 and condenses.
  • the heat of the high-pressure refrigerant is dissipated to the cooling water, and the cooling water is heated.
  • the cooling water heated by the condenser 12 flows into the heater core 33.
  • the cooling water flowing into the heater core 33 exchanges heat with the blowing air.
  • the blowing air is heated so as to approach the target blowing temperature TAO.
  • the coolant flowing out of the heater core 33 circulates through the high temperature side heat medium flow path 31 and is sucked into the high temperature side pump 32.
  • the high pressure refrigerant flowing out of the condenser 12 flows into the liquid receiver 13 and is separated into gas and liquid. Then, the liquid high-pressure refrigerant separated in the liquid receiver 13 is heat-exchanged with the cooling water flowing through the high temperature side heat medium channel 31 in the supercooling unit 14 to be supercooled.
  • the high pressure refrigerant flowing out of the subcooling unit 14 is reduced in pressure by the first pressure reducing valve 15 to be a low pressure refrigerant because the second pressure reducing valve 17 is in a fully closed state.
  • the throttle opening degree of the first pressure reducing valve 15 is adjusted such that the degree of superheat of the refrigerant flowing out of the first evaporator 16 approaches a predetermined reference degree of superheat.
  • the low pressure refrigerant reduced in pressure by the first pressure reducing valve 15 flows into the first evaporator 16.
  • the low pressure refrigerant flowing into the first evaporator 16 absorbs heat from the cooling water pressure-fed from the low temperature side pump 45 and evaporates. Thus, the cooling water circulating in the low temperature side heat exchange unit 40 is cooled.
  • the cooling water cooled by the first evaporator 16 flows into the low temperature side radiator 53.
  • the cooling water flowing into the low temperature side radiator 53 exchanges heat with the outside air blown from the radiator blower 54 and is heated.
  • the cooling water flowing out of the low temperature side radiator 53 circulates through the low temperature side heat medium flow path 41 and is sucked into the low temperature side pump 45.
  • the low pressure refrigerant flowing out of the first evaporator 16 is compressed by the compressor 11 to be a high pressure refrigerant.
  • the blowing air heated by the heater core 33 can be blown into the vehicle compartment to heat the vehicle compartment.
  • cooling water circulates battery channel 42
  • the operation of the first low temperature side flow passage switching valve 46 may be controlled so as to
  • the waste heat of the battery 47 can be absorbed by the cooling water, and the waste heat can be absorbed by the refrigerant in the first evaporator 16. Therefore, the waste heat of the battery 47 can be used as a heat source for heating the blowing air.
  • the operation of the second low temperature side flow passage switching valve 52 was controlled so that the cooling water does not flow through the in-vehicle device bypass passage 44.
  • the operation of the second low temperature side flow passage switching valve 52 may be controlled to flow through the passage 44, and the in-vehicle device flow passage pump 48 may be further operated.
  • the cooling water can be circulated to the inverter 49, the charger 50, and the motor generator 51, the waste heat of the inverter 49 and the like is absorbed by the cooling water, and this waste heat is collected by the first evaporator 16.
  • the refrigerant can absorb heat. Therefore, the waste heat of the inverter 49 etc. can be used as a heat source for heating the blowing air.
  • the cooling water should be discharged from the battery according to the temperature range of the cooling water flowing out of the first evaporator 16.
  • the circuit circulated to the passage 42 and the circuit circulated to the on-vehicle equipment bypass passage 44 may be switched.
  • the cooling mode is an operation mode in which the second evaporator 18 cools the blown air.
  • the control device 70 determines the operation states (control signals to be output to the various control devices) of the various control target devices based on the detection signal, the target blowout temperature TAO, and the like. Specifically, the control device 70 operates the compressor 11, the high temperature side pump 32, the radiator blower 54, and the air conditioning blower 62.
  • control device 70 controls compressor 11 such that the temperature of the air blown into the vehicle compartment becomes the target blowing temperature TAO.
  • the control device 70 brings the first pressure reducing valve 15 into a fully closed state, and brings the second pressure reducing valve 17 into a throttling state.
  • the control device 70 determines a control signal to be output to the second pressure reducing valve 17 so as to have a predetermined throttle opening degree in the cooling mode.
  • the control device 70 fully opens the high temperature side flow passage switching valve 37.
  • the control device 70 positions the air mix door 64 at the broken line position in FIG. 1 and closes the heater core flow path 65 by the air mix door 64 so that the total flow rate of the blown air passing through the second evaporator 18 is a cold air bypass passage. It distributes to 66.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the high pressure refrigerant flowing into the condenser 12 exchanges heat with the cooling water pressure-fed from the high temperature side pump 32 and condenses.
  • the heat of the high-pressure refrigerant is dissipated to the cooling water, and the cooling water is heated.
  • the cooling water heated by the condenser 12 flows into the heater core 33.
  • the air mix door 64 is displaced so as to close the heater core flow path 65. Therefore, the cooling water which has flowed into the heater core 33 flows out of the heater core 33 with almost no heat release to the blast air.
  • the coolant flowing out of the heater core 33 flows through the high temperature side radiator flow passage 36 and flows into the high temperature side radiator 35.
  • the cooling water flowing into the high temperature side radiator 35 exchanges heat with the outside air blown from the radiator blower 54 and is cooled.
  • the coolant flowing out of the high temperature side radiator 35 circulates through the high temperature side radiator flow passage 36 and is sucked into the high temperature side pump 32.
  • the high pressure refrigerant flowing out of the condenser 12 flows into the liquid receiver 13 and is separated into gas and liquid. Then, the liquid high-pressure refrigerant separated in the liquid receiver 13 is heat-exchanged with the cooling water flowing through the high temperature side heat medium channel 31 in the supercooling unit 14 to be supercooled.
  • the high pressure refrigerant flowing out of the subcooling unit 14 is reduced in pressure by the second pressure reducing valve 17 to be a low pressure refrigerant because the first pressure reducing valve 15 is in a fully closed state.
  • the throttle opening degree of the second pressure reducing valve 17 is adjusted so that the degree of superheat of the refrigerant flowing out of the second evaporator 18 approaches a predetermined reference degree of superheat.
  • the low pressure refrigerant decompressed by the second pressure reducing valve 17 flows into the second evaporator 18.
  • the low-pressure refrigerant flowing into the second evaporator 18 absorbs heat from the air blown by the air conditioning blower 62 and evaporates. Thereby, the blowing air is cooled.
  • the low pressure refrigerant flowing out of the second evaporator 18 is compressed by the compressor 11 to be a high pressure refrigerant.
  • the blowing air cooled by the second evaporator 18 can be blown into the vehicle compartment to perform cooling of the vehicle compartment.
  • the dehumidifying / heating mode is an operation mode in which the blown air which has been cooled and dehumidified by the second evaporator 18 is reheated by the heater core 33.
  • the control device 70 determines the operation states (control signals to be output to various control devices) of various control target devices based on the detection signal and the target blowout temperature TAO and the like. Specifically, the control device 70 operates the compressor 11, the high temperature side pump 32, the low temperature side pump 45, the radiator blower 54, and the air conditioning blower 62.
  • control device 70 controls compressor 11 such that the temperature of the air blown into the vehicle compartment becomes the target blowing temperature TAO.
  • the controller 70 brings the first pressure reducing valve 15 into the throttling state, and brings the second pressure reducing valve 17 into the throttling state.
  • the control device 70 determines the control signal output to the first pressure reducing valve 15 and the control signal output to the second pressure reducing valve 17 so as to have a predetermined dehumidifying / heating mode throttle opening degree.
  • the control device 70 fully closes the high temperature side flow passage switching valve 37.
  • the control device 70 controls the operation of the first low temperature side flow passage switching valve 46 so that the cooling water does not flow through the battery flow passage 42.
  • the control device 70 controls the operation of the second low temperature side flow passage switching valve 52 so that the cooling water does not flow through the in-vehicle device bypass flow passage 44.
  • the control device 70 displaces the air mix door 64 to the solid line position of FIG. 1 and distributes the entire flow rate of the blown air having passed through the second evaporator 18 to the heater core flow path 65.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the high pressure refrigerant flowing into the condenser 12 exchanges heat with the cooling water pressure-fed from the high temperature side pump 32 and condenses.
  • the heat of the high-pressure refrigerant is dissipated to the cooling water, and the cooling water is heated.
  • the blown air after passing through the second evaporator 18 is heated by the heater core 33 so as to reach the target blowing temperature TAO.
  • the high-pressure refrigerant flowing out of the condenser 12 flows into the liquid receiver 13 and the gas and liquid are separated. Then, the liquid high-pressure refrigerant flowing out of the liquid receiver 13 is heat-exchanged with the cooling water flowing through the high temperature side heat medium channel 31 in the supercooling unit 14 to be supercooled.
  • the low pressure refrigerant flowing into the second evaporator 18 absorbs heat from the air blown by the air conditioning blower 62 and evaporates, as in the cooling mode. Thereby, the blast air is cooled and dehumidified.
  • the refrigerant evaporation temperature of the second evaporator 18 is maintained at 1 ° C. or higher by the function of the evaporation pressure adjusting valve 19 regardless of the throttle opening degree of the second pressure reducing valve 17 or the like.
  • the low pressure refrigerant flowing out of the second evaporator 18 merges with the low pressure refrigerant flowing out of the first evaporator 16 via the evaporation pressure control valve 19.
  • the remaining high-pressure refrigerant flowing out of the subcooling unit 14 flows into the first pressure reducing valve 15 to be reduced in pressure as in the heating mode.
  • the low pressure refrigerant reduced in pressure by the first pressure reducing valve 15 flows into the first evaporator 16.
  • the low pressure refrigerant flowing into the first evaporator 16 absorbs heat from the cooling water pressure-fed from the low temperature side pump 45 and evaporates, as in the heating mode.
  • the cooling water circulating in the low temperature side heat exchange unit 40 is cooled.
  • the cooling water cooled by the first evaporator 16 flows into the low temperature side radiator 53 as in the heating mode.
  • the cooling water flowing into the low temperature side radiator 53 exchanges heat with the outside air blown from the radiator blower 54 and is heated.
  • the cooling water flowing out of the low temperature side radiator 53 circulates through the low temperature side heat medium flow path 41 and is sucked into the low temperature side pump 45.
  • the low pressure refrigerant flowing out of the first evaporator 16 joins the low pressure refrigerant flowing out of the second evaporator 18 and is compressed by the compressor 11 to become a high pressure refrigerant.
  • dehumidifying and heating the passenger compartment can be performed by reheating the blown air cooled and dehumidified by the second evaporator 18 with the heater core 33 and blowing it out into the passenger compartment. .
  • the refrigerant evaporation temperature in the first evaporator 16 and the refrigerant evaporation temperature in the second evaporator 18 can be set to different temperature zones.
  • the heating mode by controlling the operation of the first low-temperature side flow passage switching valve 46 so that the cooling water flows through the battery flow passage 42, the waste heat of the battery 47 and the blowing air are heated. It can be used as a heat source for
  • the second low temperature side flow passage switching valve 52 controls the operation of the second low temperature side flow passage switching valve 52 so that the cooling water flows through the in-vehicle device bypass flow passage 44, and further operating the in-vehicle device flow passage pump 48, the inverter 49, the charger 50 and the waste heat of the motor generator 51 can be used as a heat source for heating the blast air.
  • the refrigeration cycle apparatus 1 of the present embodiment it is possible to realize comfortable air conditioning of the vehicle interior by switching the heating mode, the cooling mode, and the dehumidifying heating mode.
  • the cycle configuration tends to be complicated.
  • the refrigeration cycle apparatus 1 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 flow the high pressure refrigerant into the first evaporator 16 and the second evaporator 18 when switching to any refrigerant circuit, the refrigerant circuit is switched with a simple configuration without causing complication of the cycle configuration. be able to.
  • an oil return routine shown in FIG. 3 for reliably returning the refrigeration oil mixed in the refrigerant to the compressor 11 is executed.
  • the oil return routine is executed at predetermined intervals as a subroutine of the air conditioning control program.
  • the oil return routine will be described below.
  • Each control step shown in FIG. 3 constitutes a function realizing unit of the control device 70.
  • step S11 of FIG. 3 it is determined whether an insufficient condition in which the amount of return of the refrigerator oil to the compressor 11 is insufficient is satisfied. More specifically, it is determined whether a shortage condition in which the amount of return of the refrigeration oil to the compressor 11 may be short is satisfied. Therefore, step S11 of the oil return routine of the present embodiment constitutes an insufficient condition determination unit.
  • step S11 when at least one or more of (condition 1) to (condition 5) shown below are satisfied, it is determined that the shortage condition is satisfied, In the other cases, it is determined that the above-mentioned shortage condition is not established.
  • the refrigerant evaporation pressure of the refrigeration cycle 10 is low, and the refrigerant sucked into the compressor 11 is The density is lower. For this reason, the circulating refrigerant flow which circulates a cycle decreases, and it is easy to run short of the return amount to compressor 11 of refrigerator oil.
  • the refrigerant evaporation pressure of the refrigeration cycle 10 is low.
  • the density of the refrigerant drawn into the air at 11 decreases. Therefore, the flow rate of the circulating refrigerant decreases, and the return amount of the refrigeration oil to the compressor 11 is likely to be insufficient.
  • the refrigerant evaporation pressure of the refrigeration cycle 10 is low as in the case 2 and is drawn into the compressor 11
  • the density of the refrigerant is reduced. Therefore, the flow rate of the circulating refrigerant decreases, and the return amount of the refrigeration oil to the compressor 11 is likely to be insufficient.
  • step S11: YES If the shortage condition determination unit determines that the above-mentioned shortage condition is satisfied (step S11: YES), the program proceeds to step S12. On the other hand, when the shortage condition determination unit determines that the shortage condition is not satisfied (step S11: NO), the process returns to the main routine.
  • step S12 oil return control is executed. Therefore, step S12 of the oil return routine of the present embodiment constitutes an oil return control execution unit.
  • the oil return control execution unit (that is, step S12) executes oil return control that periodically changes the flow rate of the refrigerant flowing through the refrigeration cycle 10 by periodically changing the refrigerant discharge capacity of the compressor 11 .
  • the oil return control execution unit of the present embodiment increases the rotational speed of the compressor 11 to the first rotational speed Nc1 by a predetermined time td, and then the second rotational speed Nc2 for the specified time td.
  • the increase and decrease control to be reduced to the predetermined number of times is repeated.
  • the first rotation speed Nc1 is a rotation speed obtained by adding a predetermined specified rotation speed Ncd to the rotation speed of the compressor 11 at the time of normal control immediately before the oil return control is performed.
  • the second rotation speed Nc2 is a rotation speed obtained by subtracting a predetermined specified rotation speed Ncd from the rotation speed of the compressor 11 at the time of normal control before oil return control is performed.
  • the first circulating refrigerant flow rate Gr1 is obtained from the circulating refrigerant flow rate Gr just before the oil return control is executed. To increase. Thereby, the flow velocity of the refrigerant circulating in the refrigeration cycle 10 is increased, and the refrigeration oil is returned to the compressor 11 together with the refrigerant.
  • the refrigeration oil mixed in the refrigerant can be reliably returned to the compressor 11, and the compressor 11 can be lubricated. Thereby, the reliability of the compressor 11 can be improved.
  • the oil return control of the refrigeration cycle apparatus 1 of the present embodiment when the rotational speed of the compressor 11 is periodically changed, the flow rate of the circulating refrigerant changes, so the pressure of the high pressure refrigerant flowing into the condenser 12 It is also easy to change. Therefore, during the execution of the oil return control, the heating capacity of the cooling water and the heating capacity of the blowing air which is the fluid to be heated are also likely to fluctuate.
  • the refrigerant condensed by the condenser 12 is excessive even when the oil return control is being performed. It can be cooled to become a liquid phase refrigerant having a degree of cooling. That is, by performing heat exchange between the coolant and the high-pressure refrigerant in the subcooling unit 14 to adjust the amount of subcooling, it is possible to suppress pressure fluctuation of the refrigerant discharged from the compressor 11.
  • the temperature change of the cooling water which exchanges heat with the refrigerant discharged from the compressor 11 in the condenser 12 can be suppressed, and further, the heating capacity of the blowing air which exchanges heat with the cooling water in the heater core 33 Fluctuation can be suppressed.
  • the refrigerant discharged from the compressor 11 and the air, which is the heat exchange fluid are indirectly subjected to heat exchange via the cooling water to suppress the fluctuation of the heating capacity of the air when heating the air. can do.
  • the refrigeration cycle apparatus 1 of the present embodiment when the refrigeration oil is returned to the compressor, it is possible to suppress the fluctuation of the heating capacity of the heat exchange target fluid.
  • the refrigerant condensed in the condenser 12 can be reliably subcooled, with the simple configuration in which the subcooling unit 14 is provided. That is, with a simple configuration, when the refrigeration oil is returned to the compressor, it can be suppressed that the heating capacity of the fluid for heat exchange changes.
  • water is used as the condenser 12 for heat exchange between the high pressure refrigerant discharged from the compressor 11 and the high temperature side heat medium circulating the high temperature side heat medium channel 31.
  • -A refrigerant heat exchanger is provided. According to this, when heating and heating blowing air, the heat which a high pressure refrigerant has can be transferred to blowing air indirectly via cooling water. Therefore, the fluctuation of the heating capacity of the blowing air can be further suppressed.
  • the heat of the high-temperature refrigerant is transferred to the cooling water having a relatively large specific heat in the condenser 12, so that the temperature change of the cooling water is suppressed.
  • the temperature change of the blowing air heat-exchanged with the cooling water is suppressed. Therefore, the fluctuation of the heating capacity of the blowing air can be further suppressed.
  • the refrigeration cycle apparatus 1 of this embodiment has an insufficient condition determination part comprised by control step S11. And the oil return control execution part comprised by control step S12 performs oil return control, when it is judged by the insufficiency condition judgment part that the insufficiency condition is satisfied. Thus, unnecessary execution of oil return control can be suppressed.
  • the oil return control execution unit changes the refrigerant discharge capacity of the compressor 11 to change the flow rate of the circulating refrigerant circulating in the refrigeration cycle 10. According to this, it is possible to reliably change the circulating refrigerant flow rate, and to reliably return the refrigerator oil to the compressor 11.
  • the oil return control execution unit of the refrigeration cycle apparatus 1 according to the second embodiment periodically changes the circulating refrigerant flow rate by changing the throttle opening of at least one of the first pressure reducing valve 15 and the second pressure reducing valve 17. .
  • the operation of the first pressure reducing valve 15 is controlled to periodically change the circulating refrigerant flow rate.
  • the operation of the second pressure reducing valve 17 is controlled to periodically change the circulating refrigerant flow rate.
  • the operation of either one of the first pressure reducing valve 15 and the second pressure reducing valve 17 is controlled to periodically change the circulating refrigerant flow rate.
  • the heating capacity of the heat exchange target fluid fluctuates when returning the refrigeration oil to the compressor, as in the first embodiment. It is possible to suppress the
  • the oil return control execution unit of the refrigeration cycle apparatus 1 of the third embodiment changes the temperature of the refrigerant circulating in the refrigeration cycle 10 to change the flow rate of the circulating refrigerant periodically.
  • the pressure feeding capability of the cooling water of the low temperature side pump 45 or the air flow rate of the radiator fan 54 is periodically changed. Then, by adjusting the heat absorption amount of the refrigerant in the first evaporator 16, the temperature of the refrigerant drawn into the compressor 11 is periodically changed. Thereby, the density of the refrigerant drawn into the compressor 11 is changed to periodically change the circulating refrigerant flow rate.
  • the heating capacity of the heat exchange target fluid fluctuates when returning the refrigeration oil to the compressor, as in the first embodiment. It is possible to suppress the
  • the refrigeration cycle apparatus 1 of the fourth embodiment is a modification of the refrigeration cycle apparatus 1 of the third embodiment.
  • the oil return control execution unit of the refrigeration cycle apparatus 1 of the third embodiment periodically changes the air flow rate of the air conditioning blower 62. Then, by adjusting the heat absorption amount of the refrigerant in the second evaporator 18, the temperature of the refrigerant drawn into the compressor 11 is periodically changed. Thereby, the density of the refrigerant drawn into the compressor 11 is changed to periodically change the circulating refrigerant flow rate.
  • the heating capacity of the heat exchange target fluid fluctuates when returning the refrigeration oil to the compressor, as in the first embodiment. It is possible to suppress the
  • refrigeration cycle apparatus 1 may be applied to an electric vehicle traveling with the drive power of only the motor generator 51.
  • the refrigeration cycle apparatus 1 may be applied to a normal vehicle that obtains driving power for traveling from an internal combustion engine.
  • the supercooling unit 14 for supercooling the refrigerant flowing out of the condenser 12 is provided on the downstream side of the condenser 12.
  • the control device 70 may be provided with a subcooling execution unit 70 h that uses the refrigerant that has flowed out of the condenser 12 as the subcooling liquid phase refrigerant.
  • the amount of heat exchange between the high-pressure refrigerant and the cooling water in the condenser 12 is changed by changing the discharge flow rate of the cooling water of the high temperature side pump 32 as the supercooling execution unit 70h, and the refrigerant flows out of the condenser 12 It is also possible to employ one that subcools the refrigerant. Also in this case, the refrigerant flowing out of the condenser 12 can be reliably subcooled.
  • a solenoid valve for opening and closing the refrigerant circuit and a thermal expansion valve for adjusting the degree of superheat of the refrigerant on the outlet side of the second evaporator 18 to a reference degree of superheat may be adopted.
  • the oil return control execution unit changes the pumping capability of the low temperature side pump 45, the blowing capability of the radiator blower 54, and the blowing capability of the air conditioning blower 62 to change the temperature of the refrigerant.
  • coolant is not limited to this.
  • the refrigerant circuit 20 is provided with a refrigerant temperature adjustment unit such as a Peltier element for heating or cooling the refrigerant circulating in the refrigerant circuit 20, and the oil return control execution unit controls the operation of the refrigerant temperature adjustment unit.
  • the temperature may be changed to change the circulating refrigerant flow rate.
  • Each component apparatus which comprises the refrigerating cycle apparatus 1 is not limited to what was disclosed by the above-mentioned embodiment.
  • the above-mentioned embodiment explained the example which adopted an electric compressor as compressor 11, when applied to a vehicle travel engine, the vehicle travels via a pulley, a belt, etc. as compressor 11.
  • An engine driven compressor driven by a rotational driving force transmitted from an engine may be employed.
  • the low temperature side radiator 53 and the high temperature side radiator 35 may be connected by a common fin.
  • the low temperature side radiator 53 and the high temperature side radiator 35 are connected so as to be able to transfer heat to each other by a common fin, the heat of the cooling water of the high temperature side heat medium flow path 31 comes from the high temperature side radiator 35 It moves to the low temperature side radiator 53. Thereby, the temperature of the low temperature side radiator 53 rises, and the frost adhering to the surface of the low temperature side radiator 53 can be melted.
  • the refrigeration cycle apparatus 1 capable of switching the operation mode has been described.
  • the heating capacity of the heat exchange fluid is suppressed from fluctuating In order to obtain an effect, it is not essential that the operation mode be switchable.
  • operation modes other than those disclosed in the above embodiments may be provided.
  • the first pressure reducing valve 15 is fully closed, and the second pressure reducing valve 17 is throttled.
  • the operation of the first low temperature side flow passage switching valve 46 is controlled such that the cooling water circulating in the low temperature side heat medium flow channel 41 flows through the battery flow channel 42.
  • the air mix door 64 is displaced such that the entire flow rate of the blown air that has passed through the second evaporator 18 is allowed to flow through the cold air bypass passage 66.
  • the waste heat of the battery 47 can be absorbed by the refrigerant in the first evaporator 16 through the cooling water circulating through the low temperature side heat medium channel 41. . Then, the heat absorbed by the refrigerant can be released to the outside air by the high temperature side radiator 35 through the cooling water circulating through the high temperature side heat medium flow path 31. According to this, it may be possible to switch to the battery cooling mode in which the battery 47 is cooled without performing the air conditioning of the vehicle interior.
  • air conditioning of the vehicle interior is performed by controlling the operation of the second low temperature side flow passage switching valve 52 so that the cooling water circulating in the low temperature side heat medium flow passage 41 flows through the on-vehicle device bypass flow passage 44
  • it may be possible to switch to the device cooling mode for cooling the on-vehicle device such as the inverter 49 or the like.

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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)

Abstract

Ce dispositif à cycle frigorifique (1) comprend: un cycle frigorifique (10) comprenant un compresseur (11) pour comprimer et décharger un fluide frigorigène dans lequel une huile de réfrigérateur est mélangée, et un condenseur (12) pour échanger de la chaleur entre le fluide frigorigène refoulé du compresseur et un fluide devant subir un échange de chaleur et pour condenser le fluide frigorigène; et une partie de réalisation de commande de retour d'huile qui effectue une commande de retour d'huile pour modifier le débit du fluide frigorigène circulant à travers le cycle frigorifique et pour renvoyer l'huile de réfrigérateur au compresseur. Le fluide frigorigène condensé est sur-refroidi au moins lorsque la commande de retour d'huile est en cours d'exécution. Ainsi, l'huile de réfrigérateur déchargée conjointement avec le fluide frigorigène provenant du compresseur peut être renvoyée au compresseur tout en supprimant un changement de la capacité de chauffage du fluide devant subir un échange de chaleur.
PCT/JP2018/031062 2017-09-28 2018-08-23 Dispositif à cycle frigorifique Ceased WO2019065013A1 (fr)

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US20220266656A1 (en) * 2019-09-10 2022-08-25 Denso Corporation Vehicle heat exchange system
US12090814B2 (en) * 2019-09-10 2024-09-17 Denso Corporation Vehicle heat exchange system
CN116373553A (zh) * 2023-03-21 2023-07-04 浙江联控技术有限公司 空调系统回油的控制方法、汽车热泵空调系统及电动汽车

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