WO2018042969A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018042969A1
WO2018042969A1 PCT/JP2017/027371 JP2017027371W WO2018042969A1 WO 2018042969 A1 WO2018042969 A1 WO 2018042969A1 JP 2017027371 W JP2017027371 W JP 2017027371W WO 2018042969 A1 WO2018042969 A1 WO 2018042969A1
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WIPO (PCT)
Prior art keywords
refrigerant
temperature
cooling
heat exchanger
heat medium
Prior art date
Application number
PCT/JP2017/027371
Other languages
English (en)
Japanese (ja)
Inventor
功嗣 三浦
加藤　吉毅
竹内　雅之
橋村　信幸
慧伍 佐藤
憲彦 榎本
賢吾 杉村
アリエル マラシガン
Original Assignee
株式会社デンソー
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
Priority claimed from JP2017103377A external-priority patent/JP6673294B2/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to CN201780052588.7A priority Critical patent/CN109642755B/zh
Priority to DE112017004350.6T priority patent/DE112017004350B4/de
Publication of WO2018042969A1 publication Critical patent/WO2018042969A1/fr
Priority to US16/285,269 priority patent/US11014430B2/en

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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
    • 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
    • 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 having a heat exchanger that exchanges heat between refrigerant and outside air.
  • a refrigeration cycle apparatus has a compressor, a condenser, a decompression unit, and an evaporator, and is used, for example, in a vehicle air conditioner.
  • the refrigeration cycle apparatus described in Patent Document 1 includes a compressor, an indoor condenser, a first expansion valve, a second expansion valve, an outdoor heat exchanger, and an indoor evaporator.
  • This refrigeration cycle apparatus can be switched to a cooling mode, a heating mode, and a dehumidifying heating mode by switching the refrigerant circuit configuration.
  • the refrigeration cycle apparatus is switched to a refrigerant circuit configuration in which an indoor evaporator and an outdoor heat exchanger are connected in parallel and the refrigerant is evaporated in both.
  • the refrigerant is evaporated in both.
  • the indoor evaporator the blown air blown into the room is cooled by exchanging heat with the refrigerant.
  • the outdoor heat exchanger heat for reheating the blown air is absorbed from the outside air.
  • the indoor evaporator must be cooled while maintaining a temperature that does not cause overcooling.
  • the refrigerant evaporation temperature of the indoor heat exchanger must be controlled to a temperature lower than the outside air temperature.
  • the outside air temperature is low as in winter, it is necessary to control the refrigerant evaporation temperature of the indoor heat exchanger to a temperature lower than 0 ° C.
  • the refrigeration cycle apparatus described in Patent Document 1 arranges a constant pressure valve on the downstream side of the indoor evaporator with respect to the refrigerant flow, thereby setting the refrigerant evaporation temperature of the indoor evaporator to 0 ° C. It is comprised so that it may maintain above.
  • an object of the present disclosure is to provide a refrigeration cycle apparatus capable of suppressing the device to be cooled from being supercooled even in a low temperature environment without using a constant pressure valve.
  • the refrigeration cycle apparatus includes a compressor, a radiator, a decompression unit, an evaporator, a heat medium cooling evaporator, a cooling target device, a detection unit, and a control device.
  • the compressor compresses and discharges the refrigerant.
  • the radiator dissipates heat from the refrigerant discharged from the compressor.
  • the decompression unit decompresses the refrigerant radiated by the radiator.
  • An evaporator heat-exchanges the refrigerant
  • the heat medium cooling evaporator cools the cooling heat medium by exchanging heat between the refrigerant decompressed by the decompression unit and the cooling heat medium having a specific heat larger than that of air.
  • the cooling target device is cooled by a cooling heat medium that exchanges heat with the refrigerant in the heat medium cooling evaporator.
  • the detection unit detects overcooling when the cooling target device is equal to or lower than a predetermined reference temperature. When the detection unit detects overcooling of the cooling target device, the control device increases the degree of superheat of the refrigerant flowing out of the heat medium cooling evaporator more than the state in which the cooling target device is not detected.
  • the detection unit detects overcooling of the cooling target device, the degree of superheat of the refrigerant flowing out of the heat medium cooling evaporator is not detected by the control device. Is raised more than.
  • the refrigeration cycle apparatus can suppress the temperature drop of the cooling heat medium while maintaining the amount of heat absorbed from the outside air in the evaporator even in a low temperature environment. Therefore, this refrigeration cycle apparatus can suppress the device to be cooled by the cooling heat medium from being overcooled.
  • control device performs control to increase the degree of superheat of the refrigerant flowing out from the heat medium cooling evaporator, so that no other configuration such as a constant pressure valve is required. That is, it is possible to prevent the device to be cooled from being overcooled without increasing the number of parts or complicating the cycle configuration.
  • the refrigeration cycle apparatus includes a compressor, a radiator, a decompression unit, a heat medium cooling evaporator, a cooling target device, a detection unit, and a control device.
  • the compressor compresses and discharges the refrigerant.
  • the radiator dissipates heat from the refrigerant discharged from the compressor.
  • the decompression unit decompresses the refrigerant radiated by the radiator.
  • the heat medium cooling evaporator cools the cooling heat medium by exchanging heat between the refrigerant decompressed by the decompression unit and the cooling heat medium having a specific heat larger than that of air.
  • the cooling target device is cooled by a cooling heat medium that exchanges heat with the refrigerant in the heat medium cooling evaporator.
  • the detection unit detects overcooling when the cooling target device is equal to or lower than a predetermined reference temperature.
  • the control device increases the degree of superheat of the refrigerant flowing out of the heat medium cooling evaporator more than the state in which the cooling target device is not detected.
  • the detection unit detects overcooling of the cooling target device, the degree of superheat of the refrigerant flowing out of the heat medium cooling evaporator is not detected by the control device. Is raised more than.
  • the said refrigeration cycle apparatus can suppress the temperature fall of the heat carrier for cooling also in a low temperature environment, and can suppress that the apparatus for cooling by the heat medium for cooling is overcooled.
  • the refrigeration cycle apparatus performs control which raises the superheat degree of the refrigerant
  • the refrigeration cycle apparatus 10 is a vehicle refrigeration cycle apparatus that constitutes a vehicle air conditioner 1 for adjusting a vehicle interior space to an appropriate temperature.
  • the refrigeration cycle apparatus 10 is applied to a hybrid vehicle that obtains a driving force for vehicle travel from an engine (in other words, an internal combustion engine) and a travel electric motor.
  • the hybrid vehicle in the first embodiment is configured as a plug-in hybrid vehicle.
  • this hybrid vehicle can charge the battery 27 mounted on the vehicle with electric power supplied from an external power source (in other words, commercial power source) when the vehicle is stopped.
  • an external power source in other words, commercial power source
  • An example of the battery 27 is a lithium ion battery.
  • the driving force output from the engine is used not only for driving the vehicle but also for operating the generator. That is, the battery 27 stores the power generated by the generator and the power supplied from the external power source.
  • the electric power stored in the battery 27 is supplied not only to the traveling electric motor but also to various in-vehicle devices including the electric components constituting the refrigeration cycle apparatus 10.
  • the vehicle air conditioner 1 includes a refrigeration cycle apparatus 10 and an indoor air conditioning unit 30.
  • the refrigeration cycle apparatus 10 is configured as a vapor compression refrigerator.
  • the refrigeration cycle apparatus 10 includes a compressor 11, a high-pressure side heat exchanger 12, a first expansion valve 13, an outdoor heat exchanger 14, a second expansion valve 15, and a low-pressure side heat exchanger 16.
  • the refrigeration cycle apparatus 10 a chlorofluorocarbon refrigerant is used as the refrigerant. That is, the refrigeration cycle apparatus 10 constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.
  • the compressor 11 sucks in the refrigerant of the refrigeration cycle apparatus 10, compresses it, and discharges it.
  • the compressor 11 is configured by an electric compressor driven by electric power supplied from the battery 27 or a variable capacity compressor driven by a belt.
  • the high-pressure side heat exchanger 12 condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant discharged from the compressor 11 and cooling water of a high-temperature cooling water circuit 21 described later.
  • the high pressure side heat exchanger 12 functions as a so-called condenser.
  • the first expansion valve 13 decompresses and expands the liquid-phase refrigerant that has flowed out of the high-pressure side heat exchanger 12. That is, the 1st expansion valve 13 comprises the pressure reduction part in this indication, and functions as a 1st pressure reduction part.
  • the first expansion valve 13 includes a valve body and an electric actuator, and has an electric variable throttle mechanism.
  • the valve body is configured to be able to change the passage opening (in other words, the throttle opening) of the refrigerant passage.
  • the electric actuator has a stepping motor that changes the throttle opening of the valve body.
  • the variable throttle mechanism in the first expansion valve 13 has a fully open function for fully opening the refrigerant passage when the throttle opening is fully opened. That is, the first expansion valve 13 can prevent the refrigerant from depressurizing by fully opening the refrigerant passage.
  • the operation of the first expansion valve 13 is controlled by a control signal output from the control device 40 described later.
  • the outdoor heat exchanger 14 is an air refrigerant heat exchanger that exchanges heat between the refrigerant flowing out of the first expansion valve 13 and the outside air.
  • the outdoor heat exchanger 14 functions as a heat absorber that causes the refrigerant to absorb the heat of the outside air.
  • the outdoor heat exchanger 14 functions as a radiator that radiates the heat of the refrigerant to the outside air.
  • outside air is blown to the outdoor heat exchanger 14 by an outdoor blower (not shown).
  • the outdoor blower is configured by an electric blower that drives a fan with an electric motor, and blows outside air toward the outdoor heat exchanger 14.
  • the outdoor heat exchanger 14 and the outdoor air blower are arrange
  • the second expansion valve 15 is disposed downstream of the high-pressure side heat exchanger 12 in the refrigerant flow. In the first embodiment, the second expansion valve 15 is disposed on the downstream side of the outdoor heat exchanger 14.
  • the second expansion valve 15 can expand the liquid refrigerant flowing out from the high pressure side heat exchanger 12 under reduced pressure.
  • the second expansion valve 15 constitutes a decompression unit in the present disclosure and can function as a second decompression unit.
  • the second expansion valve 15 includes a valve body and an electric actuator.
  • the valve body is configured to be able to change the passage opening (in other words, the throttle opening) of the refrigerant passage.
  • the electric actuator has a stepping motor that changes the throttle opening of the valve body. The operation of the second expansion valve 15 is controlled by a control signal output from the control device 40.
  • the second expansion valve 15 has an electric variable throttle mechanism.
  • the variable throttle mechanism in the second expansion valve 15 has a fully open function for fully opening the refrigerant passage when the throttle opening is fully opened, and a fully closed function for fully closing the refrigerant passage when the throttle opening is fully closed. ing.
  • the second expansion valve 15 can prevent the refrigerant from depressurizing by fully opening the refrigerant passage.
  • the second expansion valve 15 can also block the refrigerant flow by fully closing the refrigerant passage.
  • the low-pressure side heat exchanger 16 evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant flowing out of the second expansion valve 15 and the cooling water of the low-temperature cooling water circuit 22 described later.
  • the low-pressure side heat exchanger 16 is a so-called evaporator and functions as a heat medium cooling evaporator in the present disclosure.
  • the gas-phase refrigerant evaporated in the low-pressure side heat exchanger 16 is sucked into the compressor 11 and compressed.
  • the high temperature cooling water circuit 21 includes the high pressure side heat exchanger 12, the high temperature side pump 23, and the heater core 24 described above.
  • the high temperature cooling water circuit 21 circulates cooling water as a heat medium by driving the high temperature side pump 23, and exchanges heat in the high pressure side heat exchanger 12 and the heater core 24.
  • the cooling water in the high-temperature cooling water circuit 21 is a fluid as a heat medium and a high-temperature heat medium.
  • at least ethylene glycol, dimethylpolysiloxane, a liquid containing nanofluid, or an antifreeze liquid is used as the cooling water of the high-temperature cooling water circuit 21.
  • the high temperature side pump 23 is an electric heat medium pump that sucks and discharges cooling water in the high temperature cooling water circuit 21.
  • the high temperature side pump 23 can circulate the cooling water of the high temperature cooling water circuit 21 by driving.
  • the heater core 24 heats the air blown into the vehicle interior by exchanging heat between the cooling water of the high-temperature coolant circuit 21 and the air blown into the vehicle interior. That is, the heater core 24 is a high temperature side heat medium heat exchanger.
  • the cooling water dissipates heat to the air blown into the vehicle interior due to a change in sensible heat. That is, in the heater core 24, even if the cooling water dissipates heat to the air blown into the vehicle interior, the cooling water maintains a liquid phase and does not change phase.
  • the low-temperature cooling water circuit 22 includes the low-pressure side heat exchanger 16, the low-temperature side pump 25, and the cooler core 26 described above.
  • the low temperature cooling water circuit 22 circulates the cooling water as a heat medium by driving the low temperature side pump 25, and exchanges heat with the low pressure side heat exchanger 16 and the cooler core 26.
  • the cooling water in the low-temperature cooling water circuit 22 is a fluid as a heat medium and corresponds to the cooling heat medium in the present disclosure.
  • a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid is used as the cooling water of the low-temperature cooling water circuit 22.
  • the low temperature side pump 25 is an electric heat medium pump that sucks and discharges cooling water.
  • the cooler core 26 is a low-temperature heat medium heat exchanger that cools the air blown into the vehicle interior by exchanging heat between the cooling water of the low-temperature coolant circuit 22 and the air blown into the vehicle interior.
  • the cooling water absorbs heat from the air blown into the vehicle interior due to the change in sensible heat. That is, in the cooler core 26, even if the cooling water absorbs heat from the air blown into the passenger compartment, the cooling water remains in a liquid phase and does not change in phase.
  • the indoor air conditioning unit 30 constituting the vehicle air conditioner 1 will be described with reference to the drawings.
  • the indoor air conditioning unit 30 is disposed inside the instrument panel (for example, an instrument panel) at the forefront of the vehicle interior.
  • the indoor air conditioning unit 30 houses a heater core 24, a cooler core 26, an indoor blower 32, an inside / outside air switching device 33, a cold air bypass passage 35, an air mix door 36, and the like in a casing 31 that forms an outer shell thereof.
  • the casing 31 forms an air passage for the air blown into the vehicle interior.
  • the casing 31 is formed of a resin (for example, polypropylene) having a certain elasticity and excellent in strength.
  • the inside / outside air switching device 33 is disposed on the most upstream side of the blast air flow in the casing 31.
  • the inside / outside air switching device 33 switches between vehicle interior air (inside air) and outside air.
  • the inside / outside air switching device 33 is formed with an inside air introduction port for introducing inside air into the casing 31 and an outside air introduction port for introducing outside air.
  • an inside / outside air switching door is arranged inside the inside / outside air switching device 33.
  • the inside / outside air switching door continuously adjusts the opening area of the inside air introduction port and the outside air introduction port, and changes the air volume ratio between the air volume of the inside air and the air volume of the outside air.
  • the indoor blower 32 is disposed inside the casing 31 on the downstream side of the air flow of the inside / outside air switching device 33.
  • the indoor blower 32 blows air introduced through the inside / outside air switching device 33 toward the vehicle interior.
  • the indoor blower 32 is an electric blower that drives a centrifugal multiblade fan 32a (sirocco fan) by an electric motor 32b.
  • the rotational speed (air flow rate) of the indoor blower 32 is controlled by a control signal (control voltage) output from the control device 40 described later.
  • the heater core 24 and the cooler core 26 are disposed on the downstream side of the air flow of the indoor blower 32. And the cooler core 26 is arrange
  • a cold air bypass passage 35 is formed in the casing 31 to bypass the heater core 24 and flow the air that has passed through the cooler core 26.
  • the air mix door 36 is disposed on the air flow downstream side of the cooler core 26 and on the air flow upstream side of the heater core 24.
  • the air mix door 36 has a rotating shaft that is rotatably supported with respect to the casing 31 and a door substrate portion that is coupled to the rotating shaft.
  • the rotation shaft of the air mix door 36 is driven by a servo motor.
  • the operation of the servo motor is controlled by the control device 40. Therefore, the air mix door 36 can adjust the air volume ratio between the air that has passed through the cooler core 26 and the air that passes through the heater core 24 and the air that passes through the cold air bypass passage 35.
  • a mixing space is formed on the air flow downstream side of the heater core 24 and the air flow downstream side of the cold air bypass passage 35. This mixing space is used when air that has passed through the heater core 24 and air that has passed through the cold air bypass passage 35 are mixed.
  • an air outlet (not shown) is arranged on the most downstream side of the blown air flow of the casing 31. This air outlet is formed so that the conditioned air mixed in the mixing space is blown out into the vehicle interior, which is the air-conditioning target space.
  • a face air outlet that blows air-conditioned air to the upper body of the passenger in the passenger compartment
  • a foot air outlet that blows air-conditioned air to the feet of the passenger
  • air-conditioned air to the inner surface of the front window glass of the vehicle
  • the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air volume ratio between the air passing through the high-pressure side heat exchanger 12 and the air passing through the cold air bypass passage 35 by the air mix door 36. Is done. Thereby, the temperature of the conditioned air blown out from each outlet is adjusted.
  • a face door for adjusting the opening area of the face outlet, a foot door for adjusting the opening area of the foot outlet, and the defroster outlet is arrange
  • These face doors, foot doors, and defroster doors are configured to switch the air outlet mode, and their servos are controlled by a control signal output from a control device 40 described later via a link mechanism or the like. It is driven by a motor.
  • the control device 40 controls the operation of various devices to be controlled that constitute the refrigeration cycle apparatus 10.
  • the control device 40 includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof.
  • control apparatus 40 performs various calculations and processes based on the control program memorize
  • Control target devices controlled by the control device 40 are the compressor 11, the first expansion valve 13, the second expansion valve 15, the high temperature side pump 23, the low temperature side pump 25, and the like.
  • Software and hardware for controlling the electric motor of the compressor 11 in the control device 40 function as a refrigerant discharge capacity control unit. Moreover, the software and hardware which control the 1st expansion valve 13 among the control apparatuses 40 function as a 1st pressure reduction amount control part. And the software and hardware which control the 2nd expansion valve 15 among the control apparatuses 40 function as a 2nd pressure reduction amount control part.
  • software and hardware for controlling the high temperature side pump 23 in the control device 40 function as a high temperature side heat medium flow control unit.
  • the software and hardware which control the low temperature side pump 25 among the control apparatuses 40 function as a low temperature side heat-medium flow control part.
  • a sensor group including various sensors is connected to the input side of the control device 40.
  • the sensor group includes an inside air temperature sensor 41, an outside air temperature sensor 42, a solar radiation amount sensor 43, a cooler core temperature sensor 44, a cold air blowing temperature sensor 45, a cooling water temperature sensor 46, a refrigerant pressure sensor 47, and a refrigerant temperature sensor 48.
  • the battery temperature sensor 49 is included.
  • the cooler core temperature sensor 44, the cold air blowing temperature sensor 45, the cooling water temperature sensor 46, the refrigerant pressure sensor 47, the refrigerant temperature sensor 48, and the battery temperature sensor 49 correspond to a detection unit of the present disclosure.
  • the inside air temperature sensor 41 detects the passenger compartment temperature Tr.
  • the outside air temperature sensor 42 detects the outside air temperature Tam.
  • the solar radiation amount sensor 43 detects the solar radiation amount Ts in the passenger compartment.
  • the cooler core temperature sensor 44 detects the temperature of the cooler core 26 body.
  • the cooler core temperature sensor 44 is attached to a fin or a tank constituting the cooler core 26.
  • the cold air blowing temperature sensor 45 detects the temperature of the air that has passed through the cooler core 26.
  • the cold air blowing temperature sensor 45 is disposed on the air flow downstream side of the cooler core 26 and on the air flow upstream side of the air mix door 36 and the heater core 24.
  • the cooling water temperature sensor 46 detects the temperature of the cooling water circulating in the low temperature cooling water circuit 22.
  • the cooling water temperature sensor 46 is attached to a cooling water pipe that flows between the low pressure side heat exchanger 16 and the cooler core 26.
  • the refrigerant pressure sensor 47 detects the pressure of the refrigerant flowing on the low pressure side of the refrigeration cycle.
  • the low pressure side is, for example, between the outlet of the first expansion valve 13 and the suction side of the compressor 11.
  • the refrigerant pressure sensor 47 is attached to the outlet of the low pressure side heat exchanger 16.
  • the refrigerant temperature sensor 48 detects the temperature of the refrigerant flowing on the low pressure side of the refrigeration cycle. In the first embodiment, the refrigerant temperature sensor 48 detects the temperature of the refrigerant flowing from the outlet of the outdoor heat exchanger 14 toward the inlet of the low-pressure side heat exchanger 16.
  • the battery temperature sensor 49 detects the temperature of the battery 27 mounted on the vehicle. As described above, the battery 27 stores electric power for driving the electric motor for traveling, the components of the refrigeration cycle apparatus 10, and the like.
  • the various sensors may be ones that detect measured values obtained by actually measuring temperature and pressure. Or various sensors may detect the estimated value regarding the temperature or pressure of a detection target apparatus according to the physical quantity which has a strong correlation with temperature or pressure.
  • the physical quantity is, for example, the temperature of a component device other than the detection target device.
  • An operation panel 50 disposed near the instrument panel in the front of the passenger compartment is connected to the input side of the control device 40.
  • the operation panel 50 is provided with various operation switches and is operated by a passenger. Operation signals from various operation switches are input to the control device 40.
  • the various operation switches on the operation panel 50 include an air conditioner switch, a temperature setting switch, and the like.
  • the air conditioner switch sets whether or not to cool the air blown into the vehicle interior by the indoor air conditioning unit 30.
  • the temperature setting switch sets a set temperature in the passenger compartment.
  • the control device 40 switches the air conditioning mode of the vehicle air conditioner 1 to any one of the heating mode, the cooling mode, and the dehumidifying heating mode based on the target blowing temperature TAO or the like.
  • the target air temperature TAO is the target temperature of the air that is blown out into the passenger compartment.
  • the control device 40 calculates the target blowing temperature TAO based on the following mathematical formula.
  • TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ Ts + C
  • Tset indicates the vehicle interior set temperature set by the temperature setting switch of the operation panel 50
  • Tr indicates the internal air temperature detected by the internal air temperature sensor 41.
  • Tam indicates the outside air temperature detected by the outside air temperature sensor 42
  • Ts indicates the amount of solar radiation detected by the solar radiation amount sensor 43.
  • Kset, Kr, Kam, Ks are control gains
  • C is a correction constant.
  • Heating mode In the heating mode, the control device 40 brings the first expansion valve 13 into a throttled state and the second expansion valve 15 into a fully opened state. In the heating mode, the control device 40 drives the high temperature side pump 23 and stops the low temperature side pump 25.
  • control apparatus 40 determines the operating state of the various control equipment connected to the control apparatus 40 based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.
  • the operating states of various control devices are control signals output to the various control devices.
  • the control signal output to the first expansion valve 13 is determined so that the supercooling degree of the refrigerant flowing into the first expansion valve 13 approaches a predetermined target supercooling degree.
  • the target degree of subcooling is determined so that the coefficient of performance of the cycle (so-called COP) approaches the maximum value.
  • the air mix door 36 fully opens the air passage of the heater core 24, and the total flow rate of the blown air that has passed through the cooler core 26 passes through the air passage of the heater core 24. To be determined.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12, exchanges heat with the cooling water in the high-temperature cooling water circuit 21, and dissipates heat. Thereby, the cooling water of the high temperature cooling water circuit 21 is heated.
  • the refrigerant flowing out from the high pressure side heat exchanger 12 flows into the first expansion valve 13 and is depressurized until it becomes a low pressure refrigerant.
  • the low-pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14, absorbs heat from the outside air blown from an outdoor blower (not shown), and evaporates.
  • the refrigerant that has flowed out of the outdoor heat exchanger 14 flows into the second expansion valve 15. At this time, since the second expansion valve 15 is fully opened, the refrigerant flowing out of the outdoor heat exchanger 14 flows into the low-pressure side heat exchanger 16 without being depressurized by the second expansion valve 15.
  • the cooling water of the low temperature cooling water circuit 22 does not circulate in the low pressure side heat exchanger 16. Therefore, the low-pressure refrigerant that has flowed into the low-pressure side heat exchanger 16 flows out of the low-pressure side heat exchanger 16 with almost no heat absorption from the cooling water in the low-temperature cooling water circuit 22.
  • the refrigerant that has flowed out of the low-pressure side heat exchanger 16 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.
  • the heat of the high-pressure refrigerant discharged from the compressor 11 by the high-pressure side heat exchanger 12 is radiated to the cooling water of the high-temperature cooling water circuit 21, and the high-temperature cooling water circuit 21 of the high-temperature cooling water circuit 21 is discharged by the heater core 24.
  • the heat of the cooling water is dissipated to the air blown into the passenger compartment.
  • the refrigeration cycle apparatus 10 can blow out heated air blown into the vehicle interior by operating in the heating mode. That is, the refrigeration cycle apparatus 10 can realize heating of the passenger compartment.
  • the control device 40 sets the first expansion valve 13 to a fully open state and the second expansion valve 15 to a throttle state. In the cooling mode, the control device 40 stops the high temperature side pump 23 and drives the low temperature side pump 25.
  • control apparatus 40 determines the operating state of the various control equipment connected to the control apparatus 40 based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.
  • the control signal output to the second expansion valve 15 is determined so that the supercooling degree of the refrigerant flowing into the second expansion valve 15 approaches the target supercooling degree.
  • This target supercooling degree is determined in advance so that the COP approaches the maximum value.
  • the control signal output to the servo motor of the air mix door 36 is determined so that the air mix door closes the air passage of the heater core 24 and the total flow rate of the blown air that has passed through the cooler core 26 flows through the cold air bypass passage 35. Is done.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12.
  • the cooling water of the high temperature cooling water circuit 21 is not circulated in the high pressure side heat exchanger 12. Therefore, the refrigerant that has flowed into the high-pressure side heat exchanger 12 flows out of the high-pressure side heat exchanger 12 with little heat exchange with the cooling water in the high-temperature cooling water circuit 21.
  • the refrigerant that has flowed out of the high-pressure side heat exchanger 12 flows into the first expansion valve 13.
  • the first expansion valve 13 fully opens the refrigerant passage. Therefore, the refrigerant that has flowed out of the high-pressure side heat exchanger 12 flows into the outdoor heat exchanger 14 without being depressurized by the first expansion valve 13.
  • the refrigerant flowing into the outdoor heat exchanger 14 dissipates heat to the outside air blown from the outdoor fan in the outdoor heat exchanger 14.
  • the refrigerant flowing out of the outdoor heat exchanger 14 flows into the second expansion valve 15 and is decompressed and expanded at the second expansion valve 15 until it becomes a low-pressure refrigerant.
  • the low-pressure refrigerant decompressed by the second expansion valve 15 flows into the low-pressure side heat exchanger 16, absorbs heat from the cooling water in the low-temperature cooling water circuit 22, and evaporates. Thereby, the cooling water of the low-temperature cooling water circuit 22 is cooled. That is, the air blown into the passenger compartment is cooled by the cooler core 26.
  • the refrigerant flowing out from the low-pressure side heat exchanger 16 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.
  • the cooling water in the low-temperature cooling water circuit 22 is cooled in the low-pressure side heat exchanger 16 by heat exchange with the low-pressure refrigerant.
  • the cooler core 26 the vehicle interior blown air can be cooled by the cooling water.
  • the refrigeration cycle apparatus 10 can blow out the cooled air in the vehicle interior into the vehicle interior by operating in the cooling mode. That is, the refrigeration cycle apparatus 10 can realize cooling of the passenger compartment.
  • the control device 40 sets the opening degrees of the first expansion valve 13 and the second expansion valve 15 to a predetermined state.
  • the opening degree of the first expansion valve 13 is set to a predetermined value, and the opening degree of the second expansion valve 15 is fully opened.
  • the control device 40 drives both the high temperature side pump 23 and the low temperature side pump 25.
  • control apparatus 40 determines the operating state of the various control equipment connected to the control apparatus 40 based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.
  • the air mix door 36 fully opens the air passage of the heater core 24, and the total flow rate of the air that has passed through the cooler core 26 passes through the air passage of the heater core 24. It is determined.
  • the control device 40 adjusts the opening of the first expansion valve 13 and the second expansion valve 15 to a predetermined value based on the target blowing temperature TAO, the detection signal of the sensor group, and the like. Thereby, the pressure reduction amount in the first expansion valve 13 and the pressure reduction amount in the second expansion valve 15 are set. And the state defined based on this target blowing temperature TAO etc. is called the normal state in dehumidification heating mode.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12 and exchanges heat with the cooling water in the high-temperature cooling water circuit 21 to radiate heat. Thereby, the cooling water of the high temperature cooling water circuit 21 is heated.
  • the refrigerant flowing out from the high pressure side heat exchanger 12 flows into the first expansion valve 13 and is depressurized until it becomes a low pressure refrigerant.
  • the low-pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14 and radiates heat to the outside air blown from the outdoor blower.
  • the refrigerant flowing out of the outdoor heat exchanger 14 flows into the second expansion valve 15.
  • the second expansion valve 15 since the second expansion valve 15 is fully opened, the refrigerant flowing out of the outdoor heat exchanger 14 flows into the low-pressure side heat exchanger 16 without being depressurized by the second expansion valve 15.
  • the low-pressure refrigerant that has flowed into the low-pressure side heat exchanger 16 absorbs heat from the cooling water in the low-temperature cooling water circuit 22 and evaporates. Thereby, the cooling water of the low-temperature cooling water circuit 22 is cooled.
  • the refrigerant flowing out from the low-pressure side heat exchanger 16 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.
  • the vehicle interior blown air cooled and dehumidified by the cooler core 26 can be heated by the heater core 24 and blown out into the vehicle interior.
  • dehumidification heating of a vehicle interior is realizable.
  • the refrigeration cycle apparatus 10 can be heated to a desired temperature while dehumidifying the interior of the vehicle by operating in the dehumidifying heating mode, and the comfort of the interior of the vehicle can be enhanced.
  • the device to be cooled (cooler core 26 in the present embodiment) cooled by the cooling water circulating in the low-temperature cooling water circuit 22 is supercooled
  • the temperature of the equipment to be cooled may be below the reference temperature.
  • a state in which the cooling target device is supercooled and the temperature of the cooling target device is equal to or lower than the reference temperature is referred to as a supercooling state.
  • the device to be cooled is easily overcooled. If the cooling target device is in an overcooled state, the performance inherent in the cooling target device may not be fully exhibited.
  • the cooling target device is the cooler core 26 as in the first embodiment
  • the cooler core 26 is supercooled to 0 ° C. or less
  • the condensed water generated on the surface of the cooler core 26 freezes and forms frost. End up. If frosting of the cooler core 26 occurs, the heat exchange capability of the cooler core 26 is reduced.
  • the control device 40 reads the control program shown in FIG. 3 from the ROM of the control device 40 and executes it.
  • the control program shown in FIG. 3 is repeatedly executed by the control device 40 while the refrigeration cycle apparatus 10 is operating in the dehumidifying heating mode. However, in conjunction with the outside air temperature sensor 42, when the outside air falls below a predetermined temperature (for example, 5 ° C.), the control device 40 may start execution of the control program.
  • a predetermined temperature for example, 5 ° C.
  • a supercooling determination is performed to determine whether or not the cooler core 26 may be supercooled.
  • control device 40 reads the detection signal from the sensor group and the reference value set in the ROM or the like. And the value based on the detection signal from a sensor group and a reference value are compared, and the presence or absence of possibility that a cooling object apparatus will be overcooled is determined.
  • the temperature of the cooler core 26 detected by the cooler core temperature sensor 44 is compared with a reference value (reference temperature) (for example, around 0 ° C.).
  • the control device 40 determines that the cooler core 26 may be supercooled (S10: YES). In this case, in order to suppress the frost formation accompanying the supercooling of the cooler core 26, the superheat degree control (S20) mentioned later is performed.
  • the controller 40 determines that there is no possibility that the cooler core 26 is overcooled (S10: NO). In this case, the control device 40 ends this control program. Thereafter, the control device 40 starts again the execution of the control program shown in FIG. 3 and performs the process of S10.
  • control device 40 performs the superheat degree control in order to suppress the overcooling of the cooler core 26 that is the object to be cooled while maintaining the heating performance in the dehumidifying heating mode.
  • the heating performance is, for example, the blowing temperature downstream from the heater core 24.
  • the cooling of the cooling target device in the refrigeration cycle apparatus 10 is performed by the cooling water of the low-temperature cooling water circuit 22, it is strongly influenced by the temperature of the cooling water.
  • the cooling water circulating in the low-temperature cooling water circuit 22 is cooled by exchanging heat with the low-pressure refrigerant in the low-pressure side heat exchanger 16. Therefore, it is important to control the temperature efficiency of the low-pressure side heat exchanger 16 in order to suppress the device to be cooled from being supercooled.
  • the relationship between the temperature efficiency of the air refrigerant heat exchanger (for example, the outdoor heat exchanger 14) and the cooling water refrigerant heat exchanger (for example, the low-pressure side heat exchanger 16), and the degree of superheat of the refrigerant flowing out from these. Will be described with reference to FIG.
  • the temperature efficiency of the air refrigerant heat exchanger is illustrated as Ea
  • the temperature efficiency of the cooling water refrigerant heat exchanger is illustrated as Ew.
  • the relationship between each temperature efficiency and the degree of superheat when the degree of superheat of the refrigerant flowing out from the air refrigerant heat exchanger and the cooling water refrigerant heat exchanger is 1K is assumed to be 100 is shown.
  • the temperature efficiency of the air refrigerant heat exchanger gradually decreases as the degree of superheat of the refrigerant flowing out of the air refrigerant heat exchanger increases.
  • the temperature efficiency of the cooling water refrigerant heat exchanger decreases as the degree of superheat of the refrigerant flowing out of the cooling water refrigerant heat exchanger increases, and when it exceeds a predetermined value. It has greatly decreased.
  • the temperature efficiency of the cooling water refrigerant heat exchanger for cooling water having a specific heat higher than that of air is determined by setting the superheat degree of the refrigerant flowing out to a predetermined value (for example, 5K). If it is larger than the degree, the temperature efficiency of the air refrigerant heat exchanger is greatly reduced.
  • the temperature drop of the cooling water is suppressed, the temperature drop of the cooling target device cooled by the cooling water can also be suppressed, so that the cooling target device can be suppressed from being overcooled.
  • control device 40 After changing the superheat degree of the refrigerant flowing out from the low pressure side heat exchanger 16 in S20, the control device 40 ends this control program. Thereafter, the control device 40 starts again the execution of the control program shown in FIG. 3 and performs the process of S10.
  • control device 40 changes the superheat degree of the refrigerant flowing out from the low-pressure side heat exchanger 16 to a value (for example, 5K or more) larger than that in the normal state.
  • the amount of pressure reduction at is larger than the normal state.
  • control device 40 controls the degree of superheat of the refrigerant flowing out from the low pressure side heat exchanger 16 from the normal state by controlling the opening degree (that is, the flow path area) of the first expansion valve 13 to be smaller than that in the normal state. Is also changed to a large value (for example, 5K or more).
  • the temperature efficiency in the low-pressure side heat exchanger 16 can be reduced by setting the superheat degree of the refrigerant flowing out from the low-pressure side heat exchanger 16 to a value larger than that in the normal state.
  • the temperature efficiency of the outdoor heat exchanger 14 which is an air refrigerant heat exchanger maintains a certain level of capacity as shown in FIG. Considering this point, the refrigeration cycle apparatus 10 can ensure the amount of heat absorbed in the outdoor heat exchanger 14 even when the device to be cooled is suppressed from being overcooled.
  • the refrigeration cycle apparatus 10 by performing S20, it is possible to prevent overcooling and frosting of the cooler core 26 while maintaining the heating performance in the dehumidifying heating mode. Furthermore, the refrigeration cycle apparatus 10 can prevent a decrease in the air volume due to frost formation on the cooler core 26.
  • the opening degree of the first expansion valve 13 is determined so that the degree of superheat of the refrigerant flowing out from the low-pressure side heat exchanger 16 is larger than the normal state (for example, 5K or more). It has been changed by a control command.
  • the opening of the second expansion valve 15 is set to a fully open state.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12, exchanges heat with the cooling water in the high-temperature cooling water circuit 21, and dissipates heat. Thereby, the cooling water of the high temperature cooling water circuit 21 is heated.
  • coolant which flowed out from the high pressure side heat exchanger 12 flows in into the 1st expansion valve 13, and is pressure-reduced until it becomes a low pressure refrigerant
  • the low-pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14 and dissipates heat to the outside air blown from the outdoor blower. .
  • the refrigerant flowing out of the outdoor heat exchanger 14 flows into the second expansion valve 15.
  • the refrigerant that has flowed out of the outdoor heat exchanger 14 is in a gas-liquid two-phase state.
  • the 2nd expansion valve 15 is a full open state, the refrigerant
  • the low-pressure refrigerant that has flowed into the low-pressure side heat exchanger 16 absorbs heat from the cooling water in the low-temperature cooling water circuit 22 and evaporates. Thereby, the cooling water of the low-temperature cooling water circuit 22 is cooled.
  • the air blown into the passenger compartment after being cooled and dehumidified by the cooler core 26 can be heated by the heater core 24 and blown out into the passenger compartment. Thereby, dehumidification heating of a vehicle interior is realizable.
  • the refrigeration cycle apparatus 10 can be heated to a desired temperature while dehumidifying the passenger compartment by operating in the dehumidifying heating mode even when the outside air temperature is low, and the comfort in the passenger compartment is enhanced. Can do.
  • the two examples shown in FIG. 6 have the same configuration as the refrigeration cycle apparatus 10 according to the first embodiment, except for the presence or absence of superheat degree control by opening degree control of the first expansion valve 13. That is, both of these two examples operate in the dehumidifying heating mode in a low temperature environment, and it is assumed that the cooler core 26 may be supercooled (S10: YES).
  • the refrigerant circulating in the refrigeration cycle apparatus 10 is in a low temperature and low pressure state when flowing into the low pressure side heat exchanger 16.
  • the temperature at the refrigeration cycle side inlet in the low pressure side heat exchanger 16 is, for example, ⁇ 10 ° C.
  • the temperature at the low-temperature cooling water circuit 22 side outlet in the low-pressure side heat exchanger 16 in this case is, for example, ⁇ 7 ° C.
  • the cooling water cooled by the low pressure side heat exchanger 16 flows into the cooler core 26.
  • the cooler core 26 cools the blown air by exchanging heat between the cooled cooling water and the blown air blown by the indoor blower 32.
  • Twa temperature change amount
  • the temperature of the blower air on the cooler core 26 is -5 ° C., for example.
  • the temperature on the outlet side of the cooler core 26 is the frosting limit value Tf (for example, ⁇ 4 ° C. to ⁇ 2 ° C. ) Will be lower.
  • the cooler core 26 cannot be suppressed from being supercooled, and the temperature on the outlet side of the cooler core 26 decreases to a temperature lower than the frosting limit value Tf. End up. In this case, the cooler core 26 is frosted and the ventilation resistance is increased. As a result, the indoor blower 32 cannot blow a predetermined amount of air into the vehicle interior.
  • the refrigerant circulating in the refrigeration cycle apparatus 10 is in a low temperature and low pressure state when flowing into the low pressure side heat exchanger 16. Therefore, the temperature at the refrigeration cycle side inlet in the low pressure side heat exchanger 16 is, for example, ⁇ 10 ° C.
  • the superheat degree control is performed by the control apparatus 40, the opening degree of the first expansion valve 13 is controlled to be smaller than the normal state, and the superheat of the refrigerant flowing out from the low pressure side heat exchanger 16 is performed.
  • the degree is changed to a value larger than the normal state (for example, 5K or more). Thereby, the temperature efficiency in the low voltage
  • the low-pressure side heat exchanger 16 performs heat exchange between the low-temperature and low-pressure refrigerant and the cooling water in the low-temperature cooling water circuit 22. Thereby, this cooling water is cooled by heat exchange in the low-pressure side heat exchanger 16.
  • the temperature drop of the cooling water in this case is smaller than when the superheat control is not performed.
  • the second temperature that is greater than the first temperature change amount Ta between the temperature at the refrigeration cycle side inlet of the low pressure side heat exchanger 16 and the temperature at the low temperature cooling water circuit 22 side outlet of the low pressure side heat exchanger 16.
  • a temperature difference of the change amount Tb occurs.
  • the temperature at the low-temperature cooling water circuit 22 side outlet in the low-pressure side heat exchanger 16 in this case is, for example, ⁇ 1 ° C.
  • the cooling water cooled by the low pressure side heat exchanger 16 flows into the cooler core 26.
  • the cooler core 26 cools the blown air by exchanging heat between the cooled cooling water and the blown air blown by the indoor blower 32.
  • a temperature difference of the cooler core temperature change amount Twa occurs between the cooling water inflow side and the blown air blowing side in the cooler core 26.
  • the cooler core temperature change amount Twa is equal to the case where the above-described superheat degree control is not performed. Therefore, as shown in FIG. 6, the temperature of the blower air on the cooler core 26 in this case is + 1 ° C., for example.
  • the cooler core 26 when the cooler core 26 may be supercooled, if the superheat control is performed, the temperature on the outlet side of the cooler core 26 is higher than the frosting limit value Tf (for example, ⁇ 4 ° C. to ⁇ 2 ° C.). Get higher.
  • Tf for example, ⁇ 4 ° C. to ⁇ 2 ° C.
  • the superheat control By executing the superheat control in this way, it is possible to suppress the supercooling of the cooler core 26, and to maintain the cooler core 26 at a temperature higher than the frosting limit value Tf. That is, according to the vehicle air conditioner 1, it is possible to suppress overcooling and frost formation of the cooler core 26, and it is possible to continue blowing a predetermined amount of air into the vehicle interior by the indoor blower 32.
  • the refrigeration cycle apparatus 10 of the first embodiment includes the compressor 11, the high-pressure side heat exchanger 12, the first expansion valve 13, the outdoor heat exchanger 14, and the low-pressure side heat exchanger 16. And a cooler core 26.
  • the refrigeration cycle apparatus 10 which concerns on 1st Embodiment has the high temperature cooling water circuit 21 which has the high voltage
  • the vehicle air conditioner 1 is configured together with the low-temperature cooling water circuit 22.
  • the refrigeration cycle apparatus 10 by appropriately controlling the operations of the refrigeration cycle apparatus 10, the high-temperature cooling water circuit 21, and the low-temperature cooling water circuit 22, it is possible to execute appropriate cooling, heating, and dehumidification heating in the passenger compartment. And comfortable air conditioning in the passenger compartment can be realized.
  • an outdoor heat exchanger 14 and a low-pressure side heat exchanger 16 are connected in series on the downstream side of the first expansion valve 13. .
  • the controller 40 determines that the cooler core 26 may be supercooled (S10: YES)
  • the controller 40 increases the amount of pressure reduction in the first expansion valve 13 and flows out from the low pressure side heat exchanger 16.
  • the superheat degree control which raises the superheat degree of the refrigerant
  • the temperature efficiency between the refrigerant and the cooling water in the low-pressure side heat exchanger 16 is greatly reduced by increasing the degree of superheat of the refrigerant flowing out from the low-pressure side heat exchanger 16 from the normal state. Can be made.
  • the temperature of the cooling water for cooling the cooler core 26 can be maintained at a certain level or more by reducing the temperature efficiency between the refrigerant and the cooling water in the low-pressure side heat exchanger 16. it can.
  • the cooler core 26 that is cooled by the cooling water while maintaining the heat absorption amount from the outside air in the outdoor heat exchanger 14 even when operated in the dehumidifying heating mode in a low temperature environment. Supercooling and frost formation can be suppressed.
  • pressure side heat exchanger 16 is raised by making the opening degree of the 1st expansion valve 13 smaller than a normal state. That is, other configurations such as a constant pressure valve are not required. That is, according to the refrigeration cycle apparatus 10, it is possible to suppress overcooling and frosting of the cooler core 26 without increasing the number of parts or complicating the cycle configuration.
  • control device 40 compares the temperature of the main body of the cooler core 26 detected by the cooler core temperature sensor 44 with a reference value to determine the possibility that the cooler core 26 is supercooled. (S10).
  • the refrigeration cycle apparatus 10 it is possible to determine with high accuracy whether or not the cooler core 26 may be supercooled, and it is possible to appropriately suppress overcooling and frosting of the cooler core 26.
  • the refrigeration cycle apparatus 10 constitutes the vehicle air conditioner 1 together with the high-temperature cooling water circuit 21 and the low-temperature cooling water circuit 22 as in the first embodiment.
  • the configurations of the refrigeration cycle apparatus 10, the high-temperature cooling water circuit 21, the low-temperature cooling water circuit 22, and the indoor air conditioning unit 30 are basically the same as those in the first embodiment.
  • positioning of each structure in the refrigerating-cycle apparatus 10 and the content of the superheat degree control in S20 differ.
  • the refrigeration cycle apparatus 10 includes a compressor 11, a high-pressure side heat exchanger 12, a first expansion valve 13, an outdoor heat exchanger 14, a second expansion valve 15, and a low-pressure side heat exchanger 16. ing.
  • the first expansion valve 13 and the outdoor heat exchanger 14, the second expansion valve 15, and the low pressure side heat exchanger 16 are located downstream of the high pressure side heat exchanger 12. Are connected to each other in parallel to the refrigerant flow.
  • the flow of the refrigerant that has flowed out of the high-pressure side heat exchanger 12 is branched into a flow that flows into the first expansion valve 13 and a flow that flows into the second expansion valve 15.
  • the high-pressure refrigerant that has flowed into the first expansion valve 13 is depressurized by the first expansion valve 13 until it becomes a low-pressure refrigerant.
  • the low-pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14 and absorbs heat from the outside air blown from the outdoor blower.
  • the high-pressure refrigerant that has flowed into the second expansion valve 15 is decompressed by the second expansion valve 15 until it becomes a low-pressure refrigerant.
  • the second expansion valve 15 according to the second embodiment is in a predetermined throttle state, and its opening degree is a predetermined value.
  • the low-pressure refrigerant decompressed by the second expansion valve 15 flows into the low-pressure side heat exchanger 16 and exchanges heat with the cooling water circulating in the low-temperature cooling water circuit 22. Thereby, the cooling water circulating through the low-temperature cooling water circuit 22 is cooled. Therefore, also in the second embodiment, the cooler core 26 is cooled by the cooling water of the low-temperature cooling water circuit 22.
  • the refrigerant that has flowed out of the outdoor heat exchanger 14 and the refrigerant that has flowed out of the low-pressure side heat exchanger 16 merge on the upstream side of the compressor 11 and flow into the compressor 11.
  • control device 40 when operating in the dehumidifying heating mode, the control device 40 reads the control program shown in FIG. 3 from the ROM of the control device 40 and executes it.
  • control device 40 determines whether or not the cooler core 26 may be supercooled in S10. Specifically, also in the second embodiment, the temperature of the cooler core 26 detected by the cooler core temperature sensor 44 is compared with a reference value (for example, around 0 ° C.) stored in the ROM.
  • a reference value for example, around 0 ° C.
  • control device 40 increases the ratio of the pressure reduction amount of the second expansion valve 15 to the pressure reduction amount of the first expansion valve 13 as a superheat degree control, so that the low pressure side heat is increased.
  • the degree of superheat of the refrigerant flowing out of the exchanger 16 is increased.
  • control device 40 does not change the opening degree (that is, the flow path area) of the first expansion valve 13 and changes the opening degree (that is, the flow area) of the second expansion valve 15 from the normal state. Also, the degree of superheat of the refrigerant flowing out from the low pressure side heat exchanger 16 is increased to a predetermined value or more (for example, 5K or more).
  • pressure side heat exchanger 16 can be reduced.
  • the refrigeration cycle apparatus 10 can suppress the temperature fall of the cooling water circulating through the low-temperature cooling water circuit 22 including the low-pressure side heat exchanger 16.
  • the refrigeration cycle apparatus 10 can suppress overcooling and frosting of the cooler core 26 that is cooled by the cooling water.
  • the temperature efficiency of the outdoor heat exchanger 14 that is an air refrigerant heat exchanger maintains a certain level of capability as shown in FIG. Considering this point, the refrigeration cycle apparatus 10 can ensure the amount of heat absorbed in the outdoor heat exchanger 14 even when the device to be cooled is suppressed from being overcooled.
  • the vehicle air conditioner 1 can prevent a decrease in the air volume due to frost formation on the cooler core 26.
  • the opening of the first expansion valve 13 is the same as that in the normal state.
  • the opening degree of the second expansion valve 15 is determined so that the degree of superheat of the refrigerant flowing out from the low-pressure side heat exchanger 16 is set to a value larger than the normal state (for example, 5K or more). That is, the opening degree of the second expansion valve 15 is changed to be smaller than the normal state by a control command from the control device 40.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12 and exchanges heat with the cooling water in the high-temperature cooling water circuit 21 to dissipate heat. Thereby, the cooling water of the high temperature cooling water circuit 21 is heated.
  • the refrigerant that has flowed out of the high-pressure side heat exchanger 12 branches into a flow toward the first expansion valve 13 and a flow toward the second expansion valve 15.
  • the high-pressure refrigerant flowing into the first expansion valve 13 is depressurized until it becomes a low-pressure refrigerant.
  • the opening degree of the first expansion valve 13 at this time is the same as the normal state in which the superheat degree control is not performed.
  • the low-pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14 and dissipates heat to the outside air blown from the outdoor blower.
  • the refrigerant at the outlet of the outdoor heat exchanger 14 is in a gas-liquid two-phase state.
  • the high-pressure refrigerant that has flowed into the second expansion valve 15 is depressurized until it becomes a low-pressure refrigerant with a depressurization amount in accordance with the superheat degree control described above.
  • the opening degree of the second expansion valve 15 is changed smaller than the normal state in accordance with the superheat control. Therefore, the refrigerant flowing out from the second expansion valve 15 has a lower pressure than the refrigerant flowing out from the first expansion valve 13.
  • the low-pressure refrigerant decompressed by the second expansion valve flows into the low-pressure side heat exchanger 16 and absorbs heat from the cooling water in the low-temperature cooling water circuit 22. Evaporate. Thereby, the cooling water of the low-temperature cooling water circuit 22 is cooled.
  • the temperature drop of the cooling water cooled in the low-pressure side heat exchanger 16 is less than the normal state. That is, according to the refrigeration cycle apparatus 10, it is possible to suppress the cooling water that cools the cooler core 26 from being overcooled, and thus it is possible to suppress the overcooling and frost formation of the cooler core 26.
  • the pressure loss in the low-pressure side heat exchanger 16 is smaller than the pressure loss in the outdoor heat exchanger 14 because the refrigerant flow rate in the outdoor heat exchanger 14 and the refrigerant flow rate in the low-pressure side heat exchanger 16 are different. ing.
  • the refrigerant flowing out of the outdoor heat exchanger 14 joins with the refrigerant flowing out of the low-pressure side heat exchanger 16. It is desirable that the degree of superheat of the refrigerant at the time of merging indicated by a point b7 in FIG. 8 is in a state of 1K to 5K.
  • the refrigeration cycle apparatus 10 heats the vehicle interior blown air cooled by the cooler core 26 and dehumidified by the heater core 24 when the superheat control is performed in the dehumidifying heating mode. Can be blown into the passenger compartment. Thereby, dehumidification heating of a vehicle interior is realizable.
  • the refrigeration cycle apparatus 10 can be heated to a desired temperature while dehumidifying the interior of the vehicle by operating in the dehumidifying heating mode, and the comfort of the interior of the vehicle can be enhanced.
  • the refrigeration cycle apparatus 10 which concerns on 2nd Embodiment reduces the temperature efficiency in the low voltage
  • the refrigerating-cycle apparatus 10 can suppress the temperature fall of the cooling water which circulates through the low temperature cooling water circuit 22 containing the low voltage
  • the refrigeration cycle apparatus 10 can ensure the amount of heat absorbed in the outdoor heat exchanger 14 while suppressing the device to be cooled from being supercooled.
  • the refrigeration cycle apparatus 10 by performing S20, it is possible to prevent overcooling and frosting of the cooler core 26 while maintaining the heating performance in the dehumidifying heating mode. Furthermore, the vehicle air conditioner 1 can prevent a decrease in the air volume due to frost formation on the cooler core 26.
  • the operations of the refrigeration cycle apparatus 10, the high-temperature cooling water circuit 21, and the low-temperature cooling water circuit 22 are controlled as in the first embodiment.
  • appropriate cooling, heating, and dehumidifying heating in the passenger compartment can be performed, and comfortable air conditioning in the passenger compartment can be realized.
  • the side heat exchanger 16 is connected in parallel to the refrigerant flow.
  • the control device 40 when it is determined that the cooler core 26 may be supercooled (S10: YES), the control device 40 performs the superheat degree control (S20). Specifically, the superheat degree of the refrigerant flowing out from the low-pressure side heat exchanger 16 is increased by increasing the ratio of the pressure reduction amount of the second expansion valve 15 to the pressure reduction amount of the first expansion valve 13 from the normal state. . Thereby, the refrigerating-cycle apparatus 10 can reduce the temperature efficiency between the refrigerant
  • the refrigeration cycle apparatus 10 can maintain the temperature of the cooling water for cooling the cooler core 26 at a certain level or more by reducing the temperature efficiency between the refrigerant and the cooling water in the low-pressure side heat exchanger 16.
  • the refrigeration cycle apparatus 10 is cooled by the cooling water while maintaining the amount of heat absorbed from the outside air in the outdoor heat exchanger 14 even when operated in the dehumidifying heating mode in a low temperature environment. Overcooling and frosting of the cooler core 26 can be suppressed.
  • the refrigeration cycle apparatus 10 can suppress overcooling and frost formation of the cooler core 26 without requiring another configuration such as a constant pressure valve. That is, this refrigeration cycle apparatus 10 also does not increase the number of parts or complicate the cycle configuration.
  • the refrigeration cycle apparatus 10 can also determine with high accuracy whether or not the cooler core 26 may be supercooled.
  • the opening of the second expansion valve 15 is made smaller than the normal state without changing the opening of the first expansion valve 13, but this It is not limited to the embodiment.
  • the superheat degree of the refrigerant flowing out from the low pressure side heat exchanger 16 may be controlled by the combined opening degree of the first expansion valve 13 and the second expansion valve 15.
  • the refrigerant flow distribution to the outdoor heat exchanger 14 and the low pressure side heat exchanger 16 is adjusted according to the ratio of the pressure reduction amount in the first expansion valve 13 and the pressure reduction amount in the second expansion valve 15, and the superheat of the refrigerant flowing out from each is adjusted.
  • the degree may be controlled.
  • the refrigeration cycle apparatus 10 according to the third embodiment constitutes the vehicle air conditioner 1 together with the high-temperature cooling water circuit 21 and the low-temperature cooling water circuit 22 as in the above-described embodiments.
  • the configurations and arrangements of the refrigeration cycle apparatus 10, the high-temperature cooling water circuit 21, the low-temperature cooling water circuit 22, and the indoor air conditioning unit 30 are basically the same as those in the second embodiment.
  • the content of the superheat degree control in S20 mainly differs.
  • Refrigeration cycle apparatus 10 according to the third embodiment is basically the same arrangement as in the second embodiment. That is, as shown in FIG. 7, in the refrigeration cycle apparatus 10 according to the third embodiment, on the downstream side of the high-pressure side heat exchanger 12, the first expansion valve 13, the outdoor heat exchanger 14, and the second expansion valve 15.
  • the low-pressure side heat exchanger 16 is connected in parallel to the refrigerant flow.
  • control device 40 when operating in the dehumidifying heating mode, the control device 40 reads the control program shown in FIG. 3 from the ROM of the control device 40 and executes it.
  • control device 40 determines whether or not the cooler core 26 may be supercooled.
  • the processing content related to this determination is the same as in the above-described embodiment.
  • S20 superheat control is executed in order to make the superheat degree of the refrigerant flowing out from the low pressure side heat exchanger 16 larger than the normal state.
  • the processing content of this superheat degree control is different from that of the second embodiment.
  • the control device 40 periodically opens the opening of the second expansion valve 15 without changing the opening of the first expansion valve 13 (that is, the flow path area). (That is, the flow path area) is changed to be small. Specifically, the control device 40 controls the refrigerant to flow intermittently through the low-pressure heat exchanger 16 by periodically fully closing the second expansion valve 15.
  • the state in which the opening degree of each of the first expansion valve 13 and the second expansion valve 15 is a predetermined opening degree corresponds to the normal state in the present disclosure.
  • the opening degree of the 1st expansion valve 13 is a predetermined opening degree, and the state where the 2nd expansion valve 15 is fully closed corresponds to the superheat degree increase state in this indication.
  • the superheat degree of the refrigerant flowing out from the low-pressure side heat exchanger 16 periodically varies between the normal state superheat degree and the superheat degree immediately before full closure. Bigger than.
  • the temperature efficiency in the low-pressure side heat exchanger 16 can be reduced on a time average basis by executing the superheat degree control (S20).
  • the refrigeration cycle apparatus 10 suppresses the temperature drop of the cooling target device cooled by the cooling water. can do.
  • the refrigeration cycle apparatus 10 can ensure the amount of heat absorbed in the outdoor heat exchanger 14 even when the device to be cooled is suppressed from being supercooled.
  • the refrigeration cycle apparatus 10 by performing S20, it is possible to prevent overcooling and frosting of the cooler core 26 while maintaining the heating performance in the dehumidifying heating mode. Furthermore, the vehicle air conditioner 1 can prevent a decrease in the air volume due to frost formation on the cooler core 26.
  • the operations of the refrigeration cycle apparatus 10, the high-temperature cooling water circuit 21, and the low-temperature cooling water circuit 22 are controlled as in the second embodiment.
  • appropriate cooling, heating, and dehumidifying heating in the passenger compartment can be performed, and comfortable air conditioning in the passenger compartment can be realized.
  • the first expansion valve 13 and the outdoor heat exchanger 14 are The refrigerant flows are connected in parallel to each other.
  • the control device 40 determines the ratio of the opening of the second expansion valve 15 to the opening of the first expansion valve 13. Is periodically changed between a normal state in which a predetermined value is present and a superheat increase state in which the ratio of the second expansion valve 15 to the opening of the first expansion valve 13 is smaller than that in the normal state (S20).
  • the refrigeration cycle apparatus 10 can greatly reduce the temperature efficiency between the refrigerant and the cooling water in the low-pressure side heat exchanger 16 as in the second embodiment.
  • the refrigeration cycle apparatus 10 even when operated in the dehumidifying and heating mode in a low temperature environment, the amount of heat absorbed from the outside air in the outdoor heat exchanger 14 is maintained while the cooling water is used. Overcooling and frost formation of the cooled cooler core 26 can be suppressed.
  • the refrigeration cycle apparatus 10 according to the third embodiment can exhibit the same effects as those of the second embodiment described above.
  • the opening degree of the second expansion valve 15 is periodically fully closed without changing the opening degree of the first expansion valve 13. It is not limited to the embodiment. That is, various modes can be adopted as long as the ratio of the opening of the second expansion valve 15 to the opening of the first expansion valve 13 can be periodically reduced as compared with the normal state.
  • the opening degree of the first expansion valve 13 when the opening degree of the first expansion valve 13 is not changed, it is not limited to the case where the second expansion valve 15 is fully closed, and the opening degree of the second expansion valve 15 is made smaller than the normal state. There may be. Further, the opening of the first expansion valve 13 may be periodically made larger than the normal state without changing the opening of the second expansion valve 15.
  • the 2nd expansion valve 15 was used as a 2nd pressure reduction part in this indication, it is not limited to this aspect. In the present disclosure, various modes can be adopted as long as the decompression amount of the refrigerant can be changed on the refrigerant flow path flowing from the high pressure side heat exchanger 12 toward the low pressure side heat exchanger 16.
  • an on-off valve 15a and a box-type expansion valve 15b located on the downstream side of the on-off valve 15a may be employed.
  • the on-off valve 15a opens or blocks the refrigerant flow path from the high-pressure side heat exchanger 12 toward the low-pressure side heat exchanger 16.
  • the box-type expansion valve 15b decompresses and expands the liquid-phase refrigerant that has flowed out of the on-off valve 15a to form a low-pressure refrigerant.
  • the present invention is not limited to the combination of the on-off valve 15a and the box-type expansion valve 15b in FIG. 9, and various modes can be adopted.
  • a fixed throttle may be arranged on the downstream side of the refrigerant flow with respect to the on-off valve 15a. Even if it is this structure, the effect similar to the refrigerating-cycle apparatus 10 which concerns on 3rd Embodiment can be exhibited.
  • the cooling object apparatus cooled with the cooling water in the low-temperature cooling water circuit 22 is not limited to the cooler core 26 in the above-described embodiment.
  • a fourth embodiment in which a vehicle running battery 27 is employed as a cooling target device in the present disclosure will be described with reference to FIG.
  • the refrigeration cycle apparatus 10 includes a compressor 11, an outdoor heat exchanger 12a, a first expansion valve 13, a vehicle cooler 14a, a second expansion valve 15, a low-pressure side heat.
  • An exchange 16 is included.
  • the second expansion valve 15 and the low pressure side heat exchanger 16 are arranged in series in this order.
  • the outdoor heat exchanger 12a in the fourth embodiment dissipates the heat of condensation obtained by condensing the refrigerant discharged from the compressor 11 to the outside of the passenger compartment. That is, the outdoor heat exchanger 12a according to the fourth embodiment functions as a radiator in the present disclosure.
  • the vehicle cooler 14a is installed in place of the cooler core 26 installed in the indoor air conditioning unit 30, and cools the vehicle interior by exchanging heat between the refrigerant and the air. That is, the vehicle cooler 14a functions as an evaporator in the present disclosure.
  • the low-temperature cooling water circuit 22 in the fourth embodiment includes the low-pressure side heat exchanger 16 and the low-temperature side pump 25 described above, and includes a battery 27 as a cooling target device. That is, the low-temperature cooling water circuit 22 according to the fourth embodiment can cool the battery 27 by circulating the cooling water as the cooling heat medium by driving the low-temperature side pump 25.
  • the flow path of the cooling water is arranged along the outer surface of the battery 27 for traveling the vehicle. Therefore, the heat generated in the battery 27 is radiated to the cooling water cooled by the low-pressure side heat exchanger 16 via the cooling water flow path in the low-temperature cooling water circuit 22.
  • control apparatus 40 reads the control program shown in FIG. 3 from ROM of the control apparatus 40, and performs it.
  • the control device 40 determines whether or not the battery 27 may be overcooled. Specifically, in the fourth embodiment, the temperature of the battery 27 detected by the battery temperature sensor 49 is compared with a reference value (for example, around 10 ° C.) stored in the ROM.
  • a reference value for example, around 10 ° C.
  • the superheat degree control (S20) is executed as in the first embodiment.
  • the execution of the control program is terminated as it is.
  • control device 40 performs superheat degree control as in the first embodiment. That is, the control device 40 increases the degree of superheat of the refrigerant flowing out from the low-pressure side heat exchanger 16 by increasing the amount of pressure reduction in the first expansion valve 13 from the normal state.
  • the refrigeration cycle apparatus 10 is the cooling which circulates the low temperature cooling water circuit 22 containing the low voltage
  • the refrigeration cycle apparatus 10 can suppress the battery 27 that is cooled by the cooling water from being supercooled, and can suppress a decrease in the input and output performance of the battery 27.
  • the control device 40 determines that the battery 27 may be supercooled (S10: YES), the superheat degree control (S20). Execute.
  • the refrigerating cycle device 10 makes refrigerant and cooling in low-pressure side heat exchanger 16 by making superheat degree of the refrigerant which flows out from low-pressure side heat exchanger 16 larger than a normal state like 1st Embodiment.
  • the temperature efficiency with water can be greatly reduced.
  • the temperature of the cooling water for cooling the battery 27 can be maintained at a certain level or more by reducing the temperature efficiency between the refrigerant and the cooling water in the low pressure side heat exchanger 16. .
  • the battery 27 cooled by the cooling water is supercooled while maintaining the heat absorption amount from the outside air in the vehicle cooler 14a even in a low temperature environment. Can be suppressed.
  • the possibility that the battery 27 is supercooled is determined by comparing the temperature of the battery 27 detected by the battery temperature sensor 49 with a reference value. That is, the refrigeration cycle apparatus 10 according to the fourth embodiment can determine with high accuracy whether or not the battery 27 may be supercooled.
  • the battery 27 is suppressed from being supercooled by the configuration corresponding to the first embodiment and the superheat degree control, but is not limited to this mode. You may suppress the supercooling of the battery 27 by the structure and superheat degree control corresponding to 2nd Embodiment or 3rd Embodiment.
  • the refrigeration cycle apparatus 10 configures the vehicle air conditioner 1 together with the high-temperature cooling water circuit 21 and the low-temperature cooling water circuit 22 as in the first embodiment.
  • the refrigeration cycle apparatus 10 includes a compressor 11, a high-pressure side heat exchanger 12, a first expansion valve 13, and a low-pressure side heat exchanger 16, as shown in FIG.
  • the second embodiment is different from the first embodiment in that the outdoor heat exchanger 14 and the second expansion valve 15 are not provided.
  • the control system in the fifth embodiment is the same as that in the first embodiment described above except that the second expansion valve 15 is excluded from the control target device connected to the output side of the control device 40. It is a configuration.
  • the control device 40 executes the control program shown in FIG. 3 when suppressing the cooler core 26 from being overcooled.
  • each structure of the high temperature cooling water circuit 21, the low temperature cooling water circuit 22, and the indoor air conditioning unit 30 in a 5th implementation liquid it is the structure similar to 1st Embodiment. Accordingly, in the following description, the same reference numerals as those in the first embodiment indicate the same configuration, and the preceding description is referred to.
  • the refrigeration cycle apparatus 10 is configured as a vapor compression refrigerator, and as illustrated in FIG. 11, the compressor 11, the high-pressure side heat exchanger 12, The first expansion valve 13 and the low-pressure side heat exchanger 16 are provided.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12 as in the first embodiment, and the high-temperature cooling water circuit 21.
  • the heat is exchanged with the cooling water in order to dissipate heat.
  • the cooling water of the high temperature cooling water circuit 21 is heated. Therefore, the compressor 11 functions as a compressor in the present disclosure, and the high-pressure side heat exchanger 12 functions as a radiator in the present disclosure.
  • the refrigerant flowing out from the high pressure side heat exchanger 12 flows into the first expansion valve 13 and is depressurized until it becomes a low pressure refrigerant.
  • the refrigerant whose pressure has been reduced to the low-pressure refrigerant in the first expansion valve 13 flows into the low-pressure side heat exchanger 16 as it is, and exchanges heat with the cooling water circulating in the low-temperature cooling water circuit 22. That is, the first expansion valve 13 functions as a pressure reducing unit in the present disclosure, and the low pressure side heat exchanger 16 functions as a heat medium cooling evaporator in the present disclosure.
  • the cooler core 26 is cooled by the cooling water of the low-temperature cooling water circuit 22. That is, the cooler core 26 corresponds to a cooling target device in the present disclosure. Then, the refrigerant that has flowed out of the low-pressure side heat exchanger 16 flows into the compressor 11 again and circulates through the refrigeration cycle apparatus 10.
  • control device 40 reads the control program shown in FIG. 3 from the ROM of the control device 40 and executes it, thereby suppressing the cooler core 26 from being overcooled.
  • control device 40 determines whether or not the cooler core 26 may be supercooled in S10. Specifically, also in the fifth embodiment, the temperature of the cooler core 26 detected by the cooler core temperature sensor 44 is compared with a reference value (for example, around 0 ° C.) stored in the ROM.
  • a reference value for example, around 0 ° C.
  • control device 40 changes the superheat degree of the refrigerant flowing out from the low-pressure side heat exchanger 16 to a value larger than the normal state (for example, 5K or more) as superheat degree control.
  • the amount of pressure reduction in the first expansion valve 13 is made larger than that in the normal state.
  • control device 40 controls the degree of superheat of the refrigerant flowing out from the low pressure side heat exchanger 16 from the normal state by controlling the opening degree (that is, the flow path area) of the first expansion valve 13 to be smaller than that in the normal state. Is also changed to a large value (for example, 5K or more).
  • the temperature efficiency in the low-pressure side heat exchanger 16 can be reduced.
  • the said refrigeration cycle apparatus 10 can suppress that the cooler core 26 is overcooled by suppressing the temperature fall of the cooling water which circulates through the low temperature cooling water circuit 22 including the low pressure side heat exchanger 16.
  • the compressor 11 As described above, according to the refrigeration cycle apparatus 10 according to the fifth embodiment, similarly to the first embodiment, the compressor 11, the high-pressure side heat exchanger 12, the first expansion valve 13, and the low-pressure side heat exchanger.
  • the high-temperature cooling water circuit 21, and the low-temperature cooling water circuit 22 that are configured of 16, comfortable air conditioning in the passenger compartment can be realized.
  • the control device 40 when it is determined that the cooler core 26 may be supercooled (S10: YES), the control device 40 performs the superheat degree control (S20). Specifically, the degree of superheat of the refrigerant flowing out from the low pressure side heat exchanger 16 is increased by increasing the amount of pressure reduction in the first expansion valve 13 from the normal state.
  • the refrigeration cycle apparatus 10 can greatly reduce the temperature efficiency between the refrigerant and the cooling water in the low-pressure side heat exchanger 16 as in the first embodiment.
  • the refrigeration cycle apparatus 10 can maintain the temperature of the cooling water that cools the cooler core 26 at a certain level or more by reducing the temperature efficiency between the refrigerant and the cooling water in the low-pressure side heat exchanger 16.
  • the refrigeration cycle apparatus 10 can suppress overcooling and frost formation of the cooler core 26 cooled by the cooling water. Moreover, the refrigerating cycle apparatus 10 which concerns on 5th Embodiment can suppress that the cooler core 26 is overcooled, without requiring other structures, such as a constant pressure valve. That is, this refrigeration cycle apparatus 10 also does not increase the number of parts or complicate the cycle configuration.
  • the cooling target device in the present disclosure is not limited to the cooler core 26 and the battery 27 in each of the above-described embodiments.
  • the following devices can be employed as the cooling target devices in the present disclosure.
  • an inverter that mutually converts electricity into direct current and alternating current may be employed as the cooling target device in the present disclosure. This is because when the inverter is supercooled by the cooling water, the switching element is supercooled and the possibility of condensation is increased.
  • a DC-DC converter that converts voltage may be employed as the cooling target device in the present disclosure. This is because when the DC-DC converter is supercooled by the cooling water, the switching element is supercooled and the possibility of dew condensation increases.
  • a water-cooled intercooler for cooling the sucked supercharger may be adopted as the cooling target device in the present disclosure. This is because when the water-cooled intercooler is supercooled by the cooling water, the condensed water generated by the supercooling flows into the engine and causes engine failure.
  • the cooler core temperature sensor 44 detects whether or not the cooler core 26 as the cooling target device may be supercooled. Although it determined using the temperature of the cooler core 26, it is not limited to this. If it is possible to determine whether or not the cooler core 26 may be supercooled, various modes can be adopted.
  • the temperature of the air that has passed through the cooler core 26 detected by the cold air blowing temperature sensor 45 shown in FIG. 2 is compared with a reference value (for example, around 0 ° C.) stored in the ROM. You may go by.
  • a reference value for example, around 0 ° C.
  • the temperature of the cooling water circulating through the low-temperature cooling water circuit 22 detected by the cooling water temperature sensor 46 shown in FIG. 2 and the reference value stored in the ROM (for example, around 0 ° C.) It may be done by comparing with.
  • the pressure of the refrigerant flowing on the low pressure side of the refrigeration cycle detected by the refrigerant pressure sensor 47 shown in FIG. It may be done by comparing with.
  • the temperature of the refrigerant flowing on the low pressure side of the refrigeration cycle detected by the refrigerant temperature sensor 48 shown in FIG. 2 and a reference value (for example, around 0 ° C.) stored in the ROM are calculated. You may carry out by comparing.
  • the overcooling of the cooler core 26 may be comprehensively determined using a plurality of physical quantities detected by various sensors.
  • the high-temperature cooling water generated in the high-pressure side heat exchanger 12 is supplied to the heater core 24 by the high-temperature side pump 23, and heat is exchanged by the indoor blower 32 to perform heating. It is not limited to this aspect.
  • an indoor heat exchanger for exchanging heat between the high-pressure refrigerant and the air may be installed in the indoor air conditioning unit 30, and the indoor fan 32 may be operated to perform heat exchange to perform heating.
  • cooling water is used as a heat medium for cooling the device to be cooled, but various media such as oil may be used as the heat medium.
  • Nanofluid may be used as the heat medium.
  • a nanofluid is a fluid in which nanoparticles having a particle size of the order of nanometers are mixed.
  • the effect of improving the thermal conductivity in a specific temperature range the effect of increasing the heat capacity of the heat medium, the effect of preventing the corrosion of metal pipes and the deterioration of rubber pipes, and the heat medium at an extremely low temperature
  • liquidity of can be acquired.
  • Such an effect varies depending on the particle configuration, particle shape, blending ratio, and additional substance of the nanoparticles.
  • the thermal conductivity can be improved, it is possible to obtain the same cooling efficiency even with a small amount of heat medium as compared with the cooling water using ethylene glycol.
  • the heat capacity of the heat medium can be increased, the amount of cold storage heat due to the sensible heat of the heat medium itself can be increased.
  • the aspect ratio of the nanoparticles is preferably 50 or more. This is because sufficient thermal conductivity can be obtained.
  • the aspect ratio is a shape index representing the aspect ratio of the nanoparticles.
  • Nanoparticles containing any of Au, Ag, Cu and C can be used. Specifically, Au nanoparticle, Ag nanowire, CNT, graphene, graphite core-shell nanoparticle, Au nanoparticle-containing CNT, and the like can be used as the constituent atoms of the nanoparticle.
  • the CNT is a carbon nanotube.
  • the graphite core-shell nanoparticle is a particle body having a structure such as a carbon nanotube surrounding the atom.
  • a chlorofluorocarbon refrigerant is used as the refrigerant, but the type of refrigerant is not limited to this.
  • a refrigerant in the present disclosure a natural refrigerant such as carbon dioxide, a hydrocarbon refrigerant, or the like may be used.
  • the refrigeration cycle apparatus 10 in each embodiment described above constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant
  • the supercritical state in which the high-pressure side refrigerant pressure exceeds the critical pressure of the refrigerant You may comprise the refrigerating cycle.

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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 de réfrigération comprend un compresseur (11), un radiateur (12, 12a), un décompresseur (13, 15), un évaporateur (14, 14a), un évaporateur de refroidissement de milieu caloporteur (16), un dispositif (26, 27) à refroidir, un détecteur (44, 45, 46, 47, 48, 49), et un dispositif de commande (40). L'évaporateur de refroidissement de milieu caloporteur (16) refroidit un milieu caloporteur de refroidissement en effectuant un échange de chaleur entre le fluide frigorigène décomprimé par le décompresseur et le milieu caloporteur de refroidissement ayant une chaleur spécifique supérieure à l'air. Le dispositif à refroidir est refroidi avec le milieu caloporteur de refroidissement qui a subi un échange de chaleur avec le fluide frigorigène à travers l'évaporateur de refroidissement de milieu caloporteur. Le détecteur détecte un état sur-refroidi dans lequel le dispositif à refroidir devient une température de référence prédéterminée ou moins. Lorsque l'état sur-refroidi du dispositif à refroidir est détecté par le détecteur, le dispositif de commande augmente le degré de surchauffe du fluide frigorigène s'écoulant hors de l'évaporateur de refroidissement de milieu caloporteur par rapport au moment où l'état sur-refroidi du dispositif à refroidir n'est pas détecté.
PCT/JP2017/027371 2016-08-30 2017-07-28 Dispositif à cycle de réfrigération WO2018042969A1 (fr)

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CN201780052588.7A CN109642755B (zh) 2016-08-30 2017-07-28 制冷循环装置
DE112017004350.6T DE112017004350B4 (de) 2016-08-30 2017-07-28 Kältekreisvorrichtung
US16/285,269 US11014430B2 (en) 2016-08-30 2019-02-26 Refrigeration cycle device

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JP2016-167743 2016-08-30
JP2017-103377 2017-05-25
JP2017103377A JP6673294B2 (ja) 2016-08-30 2017-05-25 冷凍サイクル装置

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JP2017110898A (ja) * 2015-12-10 2017-06-22 株式会社デンソー 冷凍サイクル装置

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JPH10264646A (ja) * 1997-03-21 1998-10-06 Denso Corp 車両用空気調和装置
WO2000007836A1 (fr) * 1998-08-03 2000-02-17 Zexel Corporation Conditionneur d'air pour vehicules
JP2014189141A (ja) * 2013-03-27 2014-10-06 Panasonic Corp 車両用ヒートポンプ装置
JP2014213609A (ja) * 2013-04-22 2014-11-17 株式会社デンソー 車両用熱管理装置
JP2014234094A (ja) * 2013-06-04 2014-12-15 株式会社デンソー 車両用熱管理システム
JP2015168297A (ja) * 2014-03-05 2015-09-28 株式会社デンソー 車両用熱管理システム
JP2016003828A (ja) * 2014-06-18 2016-01-12 株式会社デンソー 冷凍サイクル装置

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Publication number Priority date Publication date Assignee Title
JPH10264646A (ja) * 1997-03-21 1998-10-06 Denso Corp 車両用空気調和装置
WO2000007836A1 (fr) * 1998-08-03 2000-02-17 Zexel Corporation Conditionneur d'air pour vehicules
JP2014189141A (ja) * 2013-03-27 2014-10-06 Panasonic Corp 車両用ヒートポンプ装置
JP2014213609A (ja) * 2013-04-22 2014-11-17 株式会社デンソー 車両用熱管理装置
JP2014234094A (ja) * 2013-06-04 2014-12-15 株式会社デンソー 車両用熱管理システム
JP2015168297A (ja) * 2014-03-05 2015-09-28 株式会社デンソー 車両用熱管理システム
JP2016003828A (ja) * 2014-06-18 2016-01-12 株式会社デンソー 冷凍サイクル装置

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JP2017110898A (ja) * 2015-12-10 2017-06-22 株式会社デンソー 冷凍サイクル装置

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