WO2020100410A1 - Dispositif de climatisation pour véhicule - Google Patents

Dispositif de climatisation pour véhicule Download PDF

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Publication number
WO2020100410A1
WO2020100410A1 PCT/JP2019/036224 JP2019036224W WO2020100410A1 WO 2020100410 A1 WO2020100410 A1 WO 2020100410A1 JP 2019036224 W JP2019036224 W JP 2019036224W WO 2020100410 A1 WO2020100410 A1 WO 2020100410A1
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WIPO (PCT)
Prior art keywords
refrigerant
temperature
heat
compressor
heat exchanger
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PCT/JP2019/036224
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English (en)
Japanese (ja)
Inventor
竜 宮腰
耕平 山下
貴司 戸山
雄満 山崎
Original Assignee
サンデン・オートモーティブクライメイトシステム株式会社
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.)
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Application filed by サンデン・オートモーティブクライメイトシステム株式会社 filed Critical サンデン・オートモーティブクライメイトシステム株式会社
Priority to CN201980074263.8A priority Critical patent/CN113015638A/zh
Publication of WO2020100410A1 publication Critical patent/WO2020100410A1/fr

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices

Definitions

  • the present invention relates to a heat pump type air conditioner for air conditioning the interior of a vehicle.
  • a heat exchanger for the battery is separately provided in the refrigerant circuit, the refrigerant circulating in the refrigerant circuit and the refrigerant (heat medium) for the battery are heat-exchanged by the heat exchanger for the battery, and the heat medium thus heat-exchanged is used.
  • a heat exchanger for the battery is separately provided in the refrigerant circuit, the refrigerant circulating in the refrigerant circuit and the refrigerant (heat medium) for the battery are heat-exchanged by the heat exchanger for the battery, and the heat medium thus heat-exchanged is used.
  • Patent Documents 2 and 3 There has also been developed one that can execute an operation mode in which the battery is circulated to circulate the battery.
  • the refrigerant circuit is provided with a plurality of valve devices (solenoid valves etc.) for controlling the flow of the refrigerant.
  • the radiator is provided with a pressure sensor
  • the heat absorber is provided with a temperature sensor
  • the compressor is controlled by the pressure (parameter) of the radiator detected by the pressure sensor in the heating mode, for example, and in the cooling mode. Is controlled by the temperature (parameter) of the heat absorber detected by the temperature sensor, but the valve device that controls the flow of the refrigerant to the refrigerant circuit at the location where these sensors are attached remains closed due to, for example, disconnection or short circuit. (Closed failure), the value (parameter) detected by the sensor becomes invalid, so that the compressor cannot be normally controlled.
  • the present invention has been made to solve such a conventional technical problem, and reduces the reliability of the compressor due to the parameter used for controlling the compressor becoming invalid due to a closing failure of the valve device or the like.
  • An object is to provide a vehicle air conditioner that can be prevented.
  • the vehicle air conditioner of the present invention is a compressor for compressing a refrigerant, an indoor heat exchanger for exchanging heat between the air supplied to the passenger compartment and the refrigerant, an outdoor heat exchanger provided outside the passenger compartment, and a refrigerant.
  • the refrigerant circuit configured to have a plurality of valve devices for controlling the flow of the, and a control device, by controlling the compressor and the valve device, by switching a plurality of operation modes
  • the invention is characterized in that the compressor is stopped when at least one of the occurrence of a closing failure of the device and the state of the valve device being unknown.
  • a vehicle air conditioner detects a radiator as an indoor heat exchanger for radiating the refrigerant to heat the air supplied to the vehicle compartment in the above invention, and detects the pressure of the radiator.
  • the control device is provided with a pressure sensor, and the control device has a heating mode as an operation mode in which the heat discharged from the compressor is radiated by the radiator, the pressure of the radiated refrigerant is reduced, and the heat is absorbed by the outdoor heat exchanger. , In this heating mode, when the valve device that controls the compressor based on the pressure of the radiator detected by the pressure sensor and also controls the flow of the refrigerant to the radiator has a closed failure, or the state of the valve device is If unknown, the compressor is stopped.
  • a radiator as an indoor heat exchanger for radiating the heat of the refrigerant to heat the air supplied to the vehicle interior, and a vehicle interior for absorbing the heat of the refrigerant.
  • a heat absorber as an indoor heat exchanger for cooling the air supplied to the, and a pressure sensor for detecting the pressure of the radiator, the control device, the refrigerant discharged from the compressor radiates heat in the radiator, After decompressing the heat-dissipated refrigerant, it has a dehumidifying and heating mode as an operation mode in which the outdoor heat exchanger and the heat absorber absorb heat.
  • the compressor is based on the pressure of the radiator detected by the pressure sensor.
  • the compressor is stopped when the valve device that controls the flow of the refrigerant to the radiator fails to close or the state of the valve device is unknown.
  • a vehicle air conditioner according to a fourth aspect of the present invention is a vehicle air conditioner according to the first or second aspect of the present invention, wherein the heat absorber is an indoor heat exchanger for cooling the air supplied to the vehicle interior by absorbing the heat of the refrigerant, and the vehicle. Equipped with an auxiliary heating device for heating the air supplied to the room and a temperature sensor that detects the temperature of the heat absorber, the control device radiated the refrigerant discharged from the compressor by the outdoor heat exchanger and radiated it.
  • depressurizing the refrigerant After depressurizing the refrigerant, it has a dehumidifying heating mode as an operation mode in which it absorbs heat with a heat absorber and heats the auxiliary heating device, and in this dehumidifying heating mode, compression is performed based on the temperature of the heat absorber detected by the temperature sensor.
  • the compressor is stopped when the valve device for controlling the machine and controlling the flow of the refrigerant to the heat absorber has a closed failure or the state of the valve device is unknown.
  • a vehicle air conditioner provides a radiator as an indoor heat exchanger for radiating the refrigerant to heat the air supplied to the vehicle compartment in each of the above inventions, and a vehicle interior for absorbing the refrigerant to absorb heat.
  • a heat absorber as an indoor heat exchanger for cooling the air supplied to the air conditioner, and a temperature sensor for detecting the temperature of the heat absorber, and the control device controls the refrigerant discharged from the compressor to the radiator and the outdoor heat exchanger.
  • Has a dehumidifying and cooling mode as an operation mode in which the heat is absorbed, and the refrigerant is decompressed, and then the heat is absorbed by a heat absorber.
  • the valve device that controls the flow of the refrigerant to the heat absorber has a closing failure or the state of the valve device is unknown, the compressor is stopped.
  • a vehicle air conditioner detects a heat absorber as an indoor heat exchanger for absorbing the heat of the refrigerant and cooling the air supplied to the vehicle interior in each of the above inventions, and detecting the temperature of the heat absorber.
  • the control device has a cooling mode as an operation mode in which the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, the radiated refrigerant is decompressed, and the heat is absorbed by the heat absorber.
  • the heat absorber as an indoor heat exchanger for absorbing the refrigerant and cooling the air supplied to the vehicle interior in each of the above inventions, and the heat mounted on the vehicle.
  • Heat exchanger for controlled temperature for cooling the controlled object
  • valve device for heat absorber for controlling the flow of refrigerant to the heat absorber, and control flow of refrigerant to the heat exchanger for controlled temperature For controlling the temperature controlled object
  • a temperature sensor for the temperature controlled object which detects the temperature of the heat exchanger for the temperature controlled object or the object cooled by the heat exchanger for the temperature controlled object, and the control device controls the temperature controlled object.
  • a vehicle air conditioner is a heat exchanger for a temperature controlled object, which is mounted on a vehicle in each of the above inventions, for cooling the temperature controlled object, and the heat exchanger for a temperature controlled object.
  • a temperature controlled object valve device for controlling the flow of the refrigerant to the temperature controlled object heat exchanger or a temperature controlled object temperature sensor for detecting the temperature of the object cooled by it, control The device opens the valve device for the temperature controlled object, and the operation mode for controlling the compressor based on the temperature of the heat exchanger for the temperature controlled object detected by the temperature sensor for the temperature controlled object or the temperature of the object cooled by it. If the valve device for temperature control has a closed failure, or if the state of the valve device for temperature control is unknown, the compressor is stopped. It is characterized by
  • a vehicle air conditioner is a heat absorber as an indoor heat exchanger for absorbing the refrigerant to cool the air supplied into the vehicle compartment in each of the above inventions, and a warmer mounted on the vehicle.
  • Heat exchanger for controlled temperature for cooling the controlled object valve device for heat absorber for controlling the flow of refrigerant to the heat absorber, and control flow of refrigerant to the heat exchanger for controlled temperature
  • the temperature control target valve device for, and a heat absorber temperature sensor for detecting the temperature of the heat absorber, the control device opens the heat absorber valve device, based on the temperature of the heat absorber detected by the heat absorber temperature sensor.
  • the present invention is characterized by having a cooling mode and stopping the compressor when the heat absorber valve device has a closing failure or when the state of the heat absorber valve device is unknown.
  • An air conditioner for a vehicle is a radiator as an indoor heat exchanger for radiating a refrigerant to heat air supplied to a vehicle compartment in each of the above inventions, and detects a pressure of the radiator.
  • the control device is provided with a pressure sensor that allows the refrigerant discharged from the compressor to flow into the outdoor heat exchanger through the radiator, and the defrosting mode as an operation mode in which the outdoor heat exchanger radiates heat to defrost.
  • the valve device that controls the compressor based on the pressure of the radiator detected by the pressure sensor and also controls the flow of the refrigerant to the radiator has a closed failure, or If the state of is unknown, the compressor is stopped.
  • control device is configured such that when the valve device closes and the refrigerant circuit is closed, or the state of the valve device becomes unknown.
  • the compressor is stopped when the refrigerant circuit may be blocked.
  • a compressor for compressing a refrigerant an indoor heat exchanger for exchanging heat between the air supplied to the vehicle interior and the refrigerant, an outdoor heat exchanger provided outside the vehicle interior, and controlling the circulation of the refrigerant
  • a refrigerant circuit having a plurality of valve devices for controlling the compressor and a control device are provided. By controlling the compressor and the valve device by the control device, a plurality of operation modes are switched to perform air conditioning in the vehicle interior.
  • the control device is a valve device that controls the flow of the refrigerant to a location where a sensor for detecting a parameter used for controlling the compressor is provided or a location that affects the sensor.
  • the compressor is stopped.
  • the state of the device is not known and the detected value of the sensor for detecting the parameter used for controlling the compressor becomes invalid, the inconvenience of stopping the compressor and putting the compressor into an abnormal control state is obviated. Therefore, the reliability can be improved.
  • the control device is provided with a radiator as an indoor heat exchanger for radiating the refrigerant to heat the air supplied into the vehicle interior, and a pressure sensor for detecting the pressure of the radiator.
  • a heating mode as an operation mode in which the refrigerant discharged from the compressor is radiated by a radiator, the radiated refrigerant is decompressed, and then the outdoor heat exchanger absorbs the heat.
  • the pressure sensor is When controlling the compressor based on the detected pressure of the radiator, stop the compressor if the valve device that controls the flow of refrigerant to the radiator has a closed failure or if the state of the valve device is unknown. By doing so, it is possible to avoid the disadvantage that the compressor falls into an abnormal control state in the heating mode and improve reliability.
  • a radiator as an indoor heat exchanger for radiating heat from the refrigerant to heat the air to be supplied to the vehicle interior, and absorbing the refrigerant to cool the air to be supplied to the vehicle interior.
  • a heat absorber as an indoor heat exchanger for, and a pressure sensor that detects the pressure of the radiator are provided, and the control device radiates the refrigerant discharged from the compressor by the radiator and decompresses the radiated refrigerant.
  • a dehumidification heating mode as an operation mode for absorbing heat in the outdoor heat exchanger and the heat absorber, and when controlling the compressor based on the pressure of the radiator detected by the pressure sensor in this dehumidification heating mode, If the valve device that controls the flow of the refrigerant to the radiator fails to close, or if the state of the valve device is unknown, stopping the compressor causes the compressor to enter an abnormal control state in the dehumidifying and heating mode. It becomes possible to avoid the inconvenience and to improve the reliability.
  • a heat absorber as an indoor heat exchanger for absorbing the heat of the refrigerant to cool the air supplied to the vehicle interior, and an auxiliary heating device for heating the air supplied to the vehicle interior.
  • the control device causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger, decompresses the radiated refrigerant, and then causes the heat absorber to absorb heat.
  • a dehumidification heating mode as an operation mode for causing the auxiliary heating device to generate heat
  • this dehumidification heating mode when the compressor is controlled based on the temperature of the heat absorber detected by the temperature sensor, the flow of the refrigerant to the heat absorber. If the valve device that controls the air conditioner fails to close, or if the state of the valve device is unknown, stop the compressor to avoid the inconvenience that the compressor falls into an abnormal control state in the dehumidifying and heating mode in this case. However, the reliability can be improved.
  • a radiator as an indoor heat exchanger for radiating the heat of the refrigerant to heat the air to be supplied to the vehicle interior, and absorbing the refrigerant to cool the air to be supplied to the vehicle interior.
  • the heat sink as an indoor heat exchanger for, and a temperature sensor that detects the temperature of the heat absorber, the control device, the refrigerant discharged from the compressor was radiated by the radiator and the outdoor heat exchanger, and radiated.
  • the refrigerant After depressurizing the refrigerant, it has a dehumidifying cooling mode as an operation mode in which it absorbs heat with a heat absorber, and in this dehumidifying cooling mode also when controlling the compressor based on the temperature of the heat absorber detected by the temperature sensor, If the valve device that controls the flow of the refrigerant to the heat absorber has a closed failure, or if the state of the valve device is unknown, by stopping the compressor, the compressor is in an abnormal control state in dehumidifying and cooling mode. It becomes possible to avoid the inconvenience and to improve the reliability.
  • a heat absorber as an indoor heat exchanger for absorbing the heat of the refrigerant to cool the air supplied to the vehicle interior, and a temperature sensor for detecting the temperature of the heat absorber are provided and controlled.
  • the device has a cooling mode as an operation mode in which the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, the radiated refrigerant is decompressed, and the heat is absorbed by the heat absorber.
  • a heat absorber as an indoor heat exchanger for absorbing the heat of the refrigerant to cool the air supplied to the vehicle interior, and for cooling the temperature controlled object mounted on the vehicle
  • Heat exchanger for temperature controlled heat absorber valve device for controlling the flow of refrigerant to the heat absorber
  • temperature controlled target for controlling the flow of refrigerant to the heat exchanger for temperature controlled
  • a temperature control target temperature sensor that detects the temperature of the temperature control target heat exchanger or the target to be cooled by the heat control target temperature exchanger, and the control device opens the temperature control target valve device.
  • a heat exchanger for temperature control which is mounted on a vehicle for cooling a temperature control target, and a flow of a refrigerant to the heat exchanger for temperature control are controlled.
  • the control device For controlling the temperature control target, and a temperature sensor for the temperature control target for detecting the temperature of the heat exchanger for the temperature control target or the object cooled by the heat exchanger for the temperature control target, the control device, the temperature control target.
  • Temperature control target cooling as an operation mode in which the valve device is opened and the compressor is controlled based on the temperature of the temperature control target heat exchanger detected by the temperature control target temperature sensor or the target cooled by it.
  • a heat absorber as an indoor heat exchanger for absorbing the heat of the refrigerant to cool the air supplied into the vehicle interior, and for cooling the temperature-controlled object mounted on the vehicle
  • Heat exchanger for temperature controlled heat absorber valve device for controlling the flow of refrigerant to the heat absorber, temperature controlled target for controlling the flow of refrigerant to the heat exchanger for temperature controlled
  • a valve device and a heat absorber temperature sensor for detecting the temperature of the heat absorber the control device opens the valve device for the heat absorber, controls the compressor based on the temperature of the heat absorber detected by the heat absorber temperature sensor,
  • an air conditioning (priority) + temperature controlled target cooling mode as an operation mode for controlling the temperature controlled target valve device based on the temperature of the temperature controlled target heat exchanger or the target cooled by it, heat absorption
  • the valve device for the air conditioner has a closed failure, or the state of the valve device for the heat absorber is unknown, the compressor is stopped, and the compressor is in an abnormal control
  • a heat radiator as an indoor heat exchanger for radiating the heat of the refrigerant to heat the air supplied to the vehicle interior, and a pressure sensor for detecting the pressure of the heat radiator are provided and controlled.
  • the device has a defrost mode as an operation mode in which the refrigerant discharged from the compressor is caused to flow into the outdoor heat exchanger via the radiator and is radiated by the outdoor heat exchanger for defrosting.
  • the refrigerant circuit may be closed due to the closing failure of the valve device, or the refrigerant circuit may be closed due to the unknown state of the valve device. If there is a problem, if the compressor is stopped, it is possible to avoid the inconvenience of operating the compressor in a state where the refrigerant circuit is blocked and further improve the reliability. become.
  • FIG. 1 It is a block diagram of the air conditioning apparatus for vehicles of one Embodiment to which this invention is applied (Example 1). It is a block diagram of an electric circuit of a control device of an air harmony device for vehicles of Drawing 1. It is a figure explaining the driving mode which the control apparatus of FIG. 2 performs. It is a block diagram of the air conditioning apparatus for vehicles explaining the heating mode by the heat pump controller of the control apparatus of FIG. It is a block diagram of the vehicle air conditioner explaining the dehumidification heating mode by the heat pump controller of the control apparatus of FIG. It is a block diagram of the air conditioning apparatus for vehicles explaining the dehumidification cooling mode by the heat pump controller of the control apparatus of FIG.
  • FIG. 3 is a control block diagram relating to compressor control of a heat pump controller of the control device of FIG. 2.
  • FIG. 4 is another control block diagram related to compressor control of the heat pump controller of the control device in FIG. 2. It is a block diagram explaining control of the solenoid valve 69 in air conditioning (priority) + battery cooling mode of the heat pump controller of the control apparatus of FIG.
  • FIG. 7 is yet another control block diagram related to compressor control of the heat pump controller of the control device in FIG. 2. It is a block diagram explaining control of the solenoid valve 35 in battery cooling (priority) + air conditioning mode of the heat pump controller of the control apparatus of FIG. It is a block diagram of the air conditioning apparatus for vehicles of other embodiment to which this invention is applied (Example 2). It is a block diagram of the air conditioning apparatus for vehicles of another another embodiment to which this invention is applied (Example 3).
  • FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to an embodiment of the present invention.
  • a vehicle of an embodiment to which the present invention is applied is an electric vehicle (EV) in which an engine (internal combustion engine) is not mounted, and electric power charged in a battery 55 mounted in the vehicle is used as a traveling motor (electric motor). (Not shown) to drive and run, and the compressor 2 of the vehicle air conditioner 1 of the present invention, which will be described later, is also driven by the electric power supplied from the battery 55. ..
  • EV electric vehicle
  • an engine internal combustion engine
  • electric motor traveling motor
  • the vehicle air conditioner 1 of this embodiment is a heating mode, a dehumidification heating mode, a dehumidification cooling mode, a cooling mode, and a defrosting mode in a heat pump operation using the refrigerant circuit R in an electric vehicle that cannot be heated by engine waste heat.
  • Mode air conditioning (priority) + battery cooling mode, battery cooling (priority) + air conditioning mode, and battery cooling (single) operation mode are switched and executed to control the air conditioning in the vehicle compartment and the temperature of the battery 55. It is something to do.
  • the air conditioning (priority) + battery cooling mode is an embodiment of the air conditioning (priority) + temperature controlled target cooling mode in the present invention
  • the battery cooling (priority) + air conditioning mode is the temperature controlled target cooling
  • An example of (priority) + air conditioning mode and a battery cooling (single) mode are examples of the temperature controlled cooling (single) mode of the present invention.
  • the present invention is effective not only for electric vehicles but also for so-called hybrid vehicles that use an engine and a running motor.
  • the vehicle to which the vehicle air conditioner 1 of the embodiment is applied is one in which the battery 55 can be charged from an external charger (a quick charger or a normal charger).
  • the battery 55, the traveling motor, the inverter controlling the same, and the like described above are the objects of temperature adjustment mounted on the vehicle in the present invention, but in the following embodiments, the battery 55 will be taken as an example for description.
  • the vehicle air conditioner 1 of the embodiment is for performing air conditioning (heating, cooling, dehumidification, and ventilation) of a vehicle interior of an electric vehicle, and an electric compressor 2 for compressing a refrigerant and an interior of the vehicle interior.
  • a radiator 4 as an indoor heat exchanger (to release the heat of the refrigerant), an outdoor expansion valve 6 as a valve device composed of a motor-operated valve (electronic expansion valve) for decompressing and expanding the refrigerant during heating, and a refrigerant radiating during cooling.
  • the outdoor heat exchanger 7 that functions as a heat radiator that allows heat to be exchanged between the refrigerant and the outside air to function as an evaporator that absorbs the heat of the refrigerant (absorbs heat in the refrigerant) during heating, and decompresses and expands the refrigerant.
  • An indoor expansion valve 8 which is a mechanical expansion valve, and an indoor heat exchanger which is provided in the air flow passage 3 to evaporate the refrigerant during cooling and dehumidification so that the refrigerant absorbs heat from the inside and outside of the vehicle (the refrigerant absorbs heat).
  • the heat absorber 9 and the accumulator 12 are sequentially connected by the refrigerant pipe 13 to form the refrigerant circuit R.
  • the outdoor expansion valve 6 decompresses and expands the refrigerant flowing out of the radiator 4 and flowing into the outdoor heat exchanger 7, and can be fully closed. Further, in the embodiment, the indoor expansion valve 8 using the mechanical expansion valve decompresses and expands the refrigerant flowing into the heat absorber 9, and adjusts the degree of superheat of the refrigerant in the heat absorber 9.
  • the outdoor heat exchanger 7 is provided with an outdoor blower 15.
  • the outdoor blower 15 exchanges heat between the outdoor air and the refrigerant by forcibly ventilating the outdoor air through the outdoor heat exchanger 7, whereby the outdoor air is discharged while the vehicle is stopped (that is, the vehicle speed is 0 km / h).
  • the heat exchanger 7 is configured to ventilate outside air.
  • the outdoor heat exchanger 7 has a receiver dryer section 14 and a supercooling section 16 sequentially on the downstream side of the refrigerant, and the refrigerant pipe 13A on the refrigerant outlet side of the outdoor heat exchanger 7 is used when flowing the refrigerant to the heat absorber 9.
  • the refrigerant pipe 13B on the outlet side of the supercooling unit 16 is connected to the receiver dryer unit 14 via an electromagnetic valve 17 (for cooling) as a valve device that is opened, and the check valve 18, the indoor expansion valve 8, and the heat absorption It is connected to the refrigerant inlet side of the heat absorber 9 through an electromagnetic valve 35 (for cabin) as a device valve device (valve device) in order.
  • the receiver dryer unit 14 and the supercooling unit 16 structurally form a part of the outdoor heat exchanger 7.
  • the check valve 18 has the forward direction of the indoor expansion valve 8.
  • the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is branched into a refrigerant pipe 13D, and the branched refrigerant pipe 13D is passed through an electromagnetic valve 21 (for heating) as a valve device opened during heating. It is connected to the refrigerant pipe 13C on the refrigerant outlet side of the heat absorber 9 for communication.
  • the refrigerant pipe 13C is connected to the inlet side of the accumulator 12, and the outlet side of the accumulator 12 is connected to the refrigerant suction side refrigerant pipe 13K of the compressor 2.
  • a strainer 19 is connected to the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4, and the refrigerant pipe 13E is connected to the refrigerant pipes 13J and 13F before the outdoor expansion valve 6 (refrigerant upstream side).
  • One of the branched and branched refrigerant pipes 13J is connected to the refrigerant inlet side of the outdoor heat exchanger 7 via the outdoor expansion valve 6.
  • the other branched refrigerant pipe 13F is connected to the refrigerant downstream side of the check valve 18 and the refrigerant upstream side of the indoor expansion valve 8 via an electromagnetic valve 22 (for dehumidification) as a valve device that is opened during dehumidification. It is communicatively connected to the located refrigerant pipe 13B.
  • the refrigerant pipe 13F is connected in parallel to the series circuit of the outdoor expansion valve 6, the outdoor heat exchanger 7 and the check valve 18, and the outdoor expansion valve 6, the outdoor heat exchanger 7 and the check valve are connected. It becomes a bypass circuit that bypasses 18. Further, an electromagnetic valve 20 as a bypass valve device is connected in parallel to the outdoor expansion valve 6.
  • an intake switching damper 26 is provided at 25 for switching the air introduced into the air flow passage 3 between the inside air (inside air circulation) which is the air inside the vehicle interior and the outside air (outside air introduction) which is the air outside the vehicle interior.
  • an indoor blower (blower fan) 27 for feeding the introduced inside air or outside air to the air flow passage 3 is provided.
  • the intake switching damper 26 of the embodiment opens and closes the outside air intake port and the inside air intake port of the intake port 25 at an arbitrary ratio to remove the air (outside air and inside air) flowing into the heat absorber 9 of the air flow passage 3. It is configured so that the ratio of inside air can be adjusted between 0% and 100% (the ratio of outside air can also be adjusted between 100% and 0%).
  • an auxiliary heater 23 as an auxiliary heating device including a PTC heater (electric heater) is provided in the embodiment, and passes through the radiator 4. It is possible to heat the air supplied to the passenger compartment. Further, in the air flow passage 3 on the air upstream side of the radiator 4, the air (inside air or outside air) flowing into the air flow passage 3 and passing through the heat absorber 9 is radiated. An air mix damper 28 that adjusts the ratio of ventilation to the device 4 and the auxiliary heater 23 is provided.
  • the vehicle air conditioner 1 of this embodiment is provided with an equipment temperature adjusting device 61 for adjusting the temperature of the battery 55 by circulating a heat medium in the battery 55 (object to be temperature adjusted).
  • the device temperature adjusting device 61 of the embodiment includes a circulation pump 62 as a circulating device for circulating a heat medium in the battery 55, a refrigerant-heat medium heat exchanger 64 as a heat exchanger for temperature control, and a heating device.
  • a heat medium heater 63 as a device is provided, and these and the battery 55 are annularly connected by a heat medium pipe 66.
  • the inlet of the heat medium passage 64A of the refrigerant-heat medium heat exchanger 64 is connected to the discharge side of the circulation pump 62, and the outlet of this heat medium passage 64A is connected to the inlet of the heat medium heater 63.
  • the outlet of the heat medium heater 63 is connected to the inlet of the battery 55, and the outlet of the battery 55 is connected to the suction side of the circulation pump 62.
  • the heat medium used in the device temperature adjusting device 61 for example, water, a refrigerant such as HFO-1234yf, a liquid such as coolant, or a gas such as air can be adopted.
  • water is used as the heat medium.
  • the heat medium heater 63 is composed of an electric heater such as a PTC heater. Further, it is assumed that, for example, a jacket structure is provided around the battery 55 so that a heat medium can flow in a heat exchange relationship with the battery 55.
  • the heat medium discharged from the circulation pump 62 flows into the heat medium flow passage 64A of the refrigerant-heat medium heat exchanger 64.
  • the heat medium exiting the heat medium flow passage 64A of the refrigerant-heat medium heat exchanger 64 reaches the heat medium heating heater 63, and if the heat medium heating heater 63 is generating heat, the heat medium heating heater 63 heats the heat medium heating heater 63 and then the battery. 55, where the heat medium exchanges heat with the battery 55.
  • the heat medium that has exchanged heat with the battery 55 is sucked into the circulation pump 62 and circulated in the heat medium pipe 66.
  • a branch pipe 67 as a branch circuit is provided in the refrigerant pipe 13B located on the refrigerant downstream side of the connecting portion between the refrigerant pipe 13F and the refrigerant pipe 13B of the refrigerant circuit R and on the refrigerant upstream side of the indoor expansion valve 8.
  • auxiliary expansion valve 68 as a valve device composed of a mechanical expansion valve in the embodiment and an electromagnetic valve (for chiller) 69 as a valve device (valve device) for temperature control are sequentially installed. It is provided.
  • the auxiliary expansion valve 68 decompresses and expands the refrigerant flowing into a later-described refrigerant passage 64B of the refrigerant-heat medium heat exchanger 64, and adjusts the degree of superheat of the refrigerant in the refrigerant passage 64B of the refrigerant-heat medium heat exchanger 64. To do.
  • the other end of the branch pipe 67 is connected to the refrigerant flow passage 64B of the refrigerant-heat medium heat exchanger 64, and one end of the refrigerant pipe 71 is connected to the outlet of the refrigerant flow passage 64B.
  • the other end is connected to a refrigerant pipe 13C on the refrigerant upstream side (refrigerant upstream side of the accumulator 12) from the confluence with the refrigerant pipe 13D.
  • the auxiliary expansion valve 68, the electromagnetic valve 69, the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and the like also form a part of the refrigerant circuit R and, at the same time, a part of the device temperature adjusting device 61. It will be.
  • the refrigerant (a part or all of the refrigerant) from the outdoor heat exchanger 7 or the like flows into the branch pipe 67, the pressure is reduced by the auxiliary expansion valve 68, and then the refrigerant is passed through the electromagnetic valve 69.
  • the refrigerant flows into the refrigerant channel 64B of the heat medium heat exchanger 64 and evaporates there.
  • the refrigerant absorbs heat from the heat medium flowing through the heat medium passage 64A while flowing through the refrigerant passage 64B, and then is sucked into the compressor 2 through the refrigerant pipe 13K through the branch pipe 71, the refrigerant pipe 13C, and the accumulator 12.
  • FIG. 2 shows a block diagram of the control device 11 of the vehicle air conditioner 1 of the embodiment.
  • the control device 11 includes an air conditioning controller 45 and a heat pump controller 32, each of which is composed of a microcomputer, which is an example of a computer including a processor, and these are a CAN (Controller Area Network) and a LIN (Local Interconnect Network). Is connected to the vehicle communication bus 65 that constitutes the. Further, the compressor 2 and the auxiliary heater 23, the circulation pump 62 and the heat medium heating heater 63 are also connected to the vehicle communication bus 65, and the air conditioning controller 45, the heat pump controller 32, the compressor 2, the auxiliary heater 23, the circulation pump 62 and the heat generator.
  • the medium heater 64 is configured to send and receive data via the vehicle communication bus 65.
  • the vehicle communication bus 65 includes a vehicle controller 72 (ECU) that controls the entire vehicle including traveling, a battery controller (BMS: Battery Management System) 73 that controls the charging and discharging of the battery 55, and a GPS navigation device 74.
  • the vehicle controller 72, the battery controller 73, and the GPS navigation device 74 are also configured by a microcomputer that is an example of a computer including a processor.
  • the air conditioning controller 45 and the heat pump controller 32 that configure the control device 11 connect the vehicle communication bus 65 to each other. Information (data) is transmitted and received to and from the vehicle controller 72, the battery controller 73, and the GPS navigation device 74 via the above.
  • the air conditioning controller 45 is a higher-level controller that controls the vehicle interior air conditioning.
  • the inputs of the air conditioning controller 45 are an outside air temperature sensor 33 that detects the outside air temperature Tam of the vehicle and an outside air humidity that detects outside air humidity.
  • the sensor 34, the HVAC suction temperature sensor 36 that detects the temperature of the air that is sucked into the air flow passage 3 from the suction port 25 and flows into the heat absorber 9, and the inside air temperature sensor 37 that detects the temperature of the air (inside air) in the vehicle compartment.
  • An inside air humidity sensor 38 for detecting the humidity of the air in the vehicle compartment
  • an indoor CO 2 concentration sensor 39 for detecting the carbon dioxide concentration in the vehicle compartment
  • an outlet temperature sensor 41 for detecting the temperature of the air blown into the vehicle compartment.
  • An air conditioning operation unit 53 for performing air conditioning setting operations in the vehicle interior such as mode switching and information display is connected.
  • 53A is a display as a display output device provided in the air conditioning operation unit 53.
  • the output of the air conditioning controller 45 is connected to the outdoor blower 15, the indoor blower (blower fan) 27, the suction switching damper 26, the air mix damper 28, and the outlet switching damper 31, which are connected to the air conditioning controller 45. Controlled by.
  • the heat pump controller 32 is a controller that mainly controls the refrigerant circuit R, and the heat pump controller 32 has an input that releases heat to detect the refrigerant inlet temperature Tcxin of the radiator 4 (which is also the refrigerant temperature discharged from the compressor 2).
  • Radiator pressure sensor 47 for detecting the refrigerant pressure (pressure of radiator 4; radiator pressure Pci), and heat absorber for detecting the temperature of heat absorber 9 (temperature of heat absorber 9 itself: hereinafter, heat absorber temperature Te)
  • Outputs of the auxiliary heater temperature sensors 50A (driver's seat side) and 50B (passenger seat side) for detecting the temperature are connected.
  • the radiator pressure sensor 47 is provided in the refrigerant pipe 13E on the refrigerant outlet side immediately after exiting the radiator 4, and the heat absorber temperature sensor 48 is provided in the heat absorber 9.
  • the output of the heat pump controller 32 includes the outdoor expansion valve 6, the solenoid valve 22 (for dehumidification), the solenoid valve 17 (for cooling), the solenoid valve 21 (for heating), the solenoid valve 20 (for bypass), and the solenoid valve 35.
  • the electromagnetic valves (for the cabin) and the electromagnetic valve 69 (for the chiller) are connected, and they are controlled by the heat pump controller 32.
  • the compressor 2, the auxiliary heater 23, the circulation pump 62, and the heat medium heating heater 63 each have a built-in controller, and in the embodiment, the controller of the compressor 2, the auxiliary heater 23, the circulation pump 62, and the heat medium heating heater 63. Transmits and receives data to and from the heat pump controller 32 via the vehicle communication bus 65, and is controlled by the heat pump controller 32.
  • the circulation pump 62 and the heat medium heater 63 that constitute the device temperature adjusting device 61 may be controlled by the battery controller 73. Further, in the battery controller 73, the temperature of the heat medium on the outlet side of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 of the device temperature adjusting device 61 (heat medium temperature Tw: heat exchanger for temperature controlled).
  • the remaining amount of the battery 55 (the amount of stored electricity), the information regarding the charging of the battery 55 (the information that the battery is being charged, the charging completion time, the remaining charging time, etc.), the heat medium temperature Tw, and the battery temperature Tcell are It is transmitted from the battery controller 73 to the air conditioning controller 45 and the vehicle controller 72 via the vehicle communication bus 65.
  • the information regarding the charge completion time and the remaining charge time when the battery 55 is charged is information supplied from an external charger such as a quick charger described later.
  • the heat medium temperature sensor 76 is provided in the heat medium pipe 66 immediately after exiting the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64, and the battery temperature sensor 77 is provided in the battery 55. ing.
  • the heat pump controller 32 and the air conditioning controller 45 send and receive data to and from each other via the vehicle communication bus 65, and control each device based on the output of each sensor and the setting input by the air conditioning operation unit 53.
  • Air volume Ga of air flowing into the air flow passage 3 and flowing in the air flow passage 3 (calculated by the air conditioning controller 45), air flow rate SW by the air mix damper 28 (calculated by the air conditioning controller 45), voltage of the indoor blower 27 (BLV), the information from the battery controller 73, the information from the GPS navigation device 74, and the output of the air conditioning operation unit 53 are transmitted from the air conditioning controller 45 to the heat pump controller 32 via the vehicle communication bus 65, and the heat pump controller 32 controls the heat pump controller 32. It is configured to be used for control.
  • the heat pump controller 32 also transmits data (information) regarding the control of the refrigerant circuit R to the air conditioning controller 45 via the vehicle communication bus 65.
  • the control device 11 controls the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, the cooling mode, and the air conditioning operation of the air conditioning (priority) + battery cooling mode, and the battery cooling.
  • Each battery cooling operation of (priority) + air conditioning mode and battery cooling (single) mode and defrosting mode are switched and executed. These are shown in FIG.
  • the battery 55 is not charged in the embodiment, and the ignition of the vehicle is performed. This is executed when (IGN) is turned on and the air conditioning switch of the air conditioning operation unit 53 is turned on. However, it is executed even when the ignition is OFF during remote operation (pre-air conditioning, etc.). Even when the battery 55 is being charged, there is no battery cooling request, and the process is executed when the air conditioning switch is ON.
  • each battery cooling operation in the battery cooling (priority) + air conditioning mode and the battery cooling (single) mode is executed, for example, when the plug of the quick charger (external power source) is connected and the battery 55 is charged. It is something.
  • the battery cooling (single) mode is executed when the air conditioning switch is OFF and there is a battery cooling request (during traveling at a high outside air temperature, etc.) other than during charging of the battery 55.
  • the heat pump controller 32 operates the circulation pump 62 of the device temperature adjusting device 61 when the ignition is turned on, or when the battery 55 is being charged even when the ignition is turned off. It is assumed that the heat medium is circulated in the heat medium pipe 66 as indicated by broken lines in FIGS. Further, although not shown in FIG. 3, the heat pump controller 32 of the embodiment also executes a battery heating mode for heating the battery 55 by causing the heat medium heating heater 63 of the device temperature adjusting device 61 to generate heat.
  • FIG. 4 shows how the refrigerant flows in the refrigerant circuit R in the heating mode (solid arrow).
  • the heat pump controller 32 opens the solenoid valve 21 and the solenoid valve 17 , The solenoid valve 20, the solenoid valve 22, the solenoid valve 35, and the solenoid valve 69 are closed. Then, the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is ventilated through the radiator 4, the air in the air flow passage 3 is heated by exchanging heat with the high temperature refrigerant in the radiator 4. On the other hand, the refrigerant in the radiator 4 is cooled by being deprived of heat by the air and condensed and liquefied.
  • the liquefied refrigerant in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 via the refrigerant pipes 13E and 13J.
  • the refrigerant flowing into the outdoor expansion valve 6 is decompressed there, and then flows into the outdoor heat exchanger 7.
  • the refrigerant that has flowed into the outdoor heat exchanger 7 evaporates and pumps up heat from the outside air ventilated by traveling or by the outdoor blower 15 (heat absorption). That is, the refrigerant circuit R serves as a heat pump.
  • the low-temperature refrigerant that has exited the outdoor heat exchanger 7 reaches the refrigerant pipe 13C via the refrigerant pipes 13A and 13D, the solenoid valve 21, and further enters the accumulator 12 via this refrigerant pipe 13C, where it is gas-liquid separated.
  • the circulation in which the gas refrigerant is sucked into the compressor 2 from the refrigerant pipe 13K is repeated.
  • the air heated by the radiator 4 is blown out from the air outlet 29, so that the interior of the vehicle is heated.
  • the heat pump controller 32 calculates a target heater temperature TCO (of the radiator 4) calculated from a target outlet temperature TAO, which will be described later, which is a target temperature of the air blown into the vehicle interior (a target value of the temperature of the air blown into the vehicle interior).
  • the target radiator pressure PCO is calculated from the target temperature), and the target radiator pressure PCO and the radiator pressure Pci (high pressure of the refrigerant circuit R: parameter) detected by the radiator pressure sensor 47 are calculated based on the compressor 2.
  • the valve opening degree of the outdoor expansion valve 6 is controlled based on the refrigerant outlet temperature Tci of the radiator 4 detected by the radiator outlet temperature sensor 44 and the radiator pressure Pci detected by the radiator pressure sensor 47. Then, the degree of supercooling of the refrigerant at the outlet of the radiator 4 is controlled.
  • the heat pump controller 32 supplements this shortage with the heat generated by the auxiliary heater 23. As a result, the vehicle interior is heated without any trouble even when the outside temperature is low.
  • FIG. 5 shows how the refrigerant flows in the refrigerant circuit R in the dehumidifying and heating mode (solid arrow).
  • the heat pump controller 32 opens the solenoid valve 21, the solenoid valve 22, and the solenoid valve 35, and closes the solenoid valve 17, the solenoid valve 20, and the solenoid valve 69.
  • the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is ventilated through the radiator 4, the air in the air flow passage 3 is heated by exchanging heat with the high temperature refrigerant in the radiator 4. On the other hand, the refrigerant in the radiator 4 is cooled by being deprived of heat by the air and condensed and liquefied.
  • the refrigerant liquefied in the radiator 4 exits the radiator 4, a part of it enters the refrigerant pipe 13J through the refrigerant pipe 13E and reaches the outdoor expansion valve 6.
  • the refrigerant flowing into the outdoor expansion valve 6 is decompressed there, and then flows into the outdoor heat exchanger 7.
  • the refrigerant that has flowed into the outdoor heat exchanger 7 evaporates and pumps up heat from the outside air ventilated by traveling or by the outdoor blower 15 (heat absorption).
  • the low-temperature refrigerant leaving the outdoor heat exchanger 7 reaches the refrigerant pipe 13C via the refrigerant pipes 13A and 13D and the solenoid valve 21, enters the accumulator 12 via the refrigerant pipe 13C, and is separated into gas and liquid there. After that, the circulation in which the gas refrigerant is sucked into the compressor 2 from the refrigerant pipe 13K is repeated.
  • the rest of the condensed refrigerant flowing through the radiator pipe 13E via the radiator 4 is diverted, and the diverted refrigerant flows into the refrigerant pipe 13F via the solenoid valve 22 and reaches the refrigerant pipe 13B.
  • the refrigerant reaches the indoor expansion valve 8, is decompressed by the indoor expansion valve 8, then flows into the heat absorber 9 via the electromagnetic valve 35, and is evaporated.
  • the water in the air blown out from the indoor blower 27 is condensed and adheres to the heat absorber 9 due to the heat absorbing action of the refrigerant generated in the heat absorber 9, so that the air is cooled and dehumidified.
  • the refrigerant evaporated in the heat absorber 9 flows out into the refrigerant pipe 13C, joins the refrigerant from the refrigerant pipe 13D (refrigerant from the outdoor heat exchanger 7), and then is sucked into the compressor 2 from the refrigerant pipe 13K via the accumulator 12. Repeat the cycle.
  • the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4 and the auxiliary heater 23 (when heat is generated), so that dehumidification and heating of the vehicle interior is performed.
  • the heat pump controller 32 is based on the target radiator pressure PCO calculated from the target heater temperature TCO and the radiator pressure Pci (high pressure of the refrigerant circuit R: parameter) detected by the radiator pressure sensor 47. Of the compressor 2 or the rotation of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te: parameter) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO which is its target value. Control the number. At this time, the heat pump controller 32 controls the compressor 2 by selecting whichever of the radiator target pressure Pci and the heat absorber temperature Te, whichever is lower than the target compressor speed obtained from the calculation. Further, the valve opening degree of the outdoor expansion valve 6 is controlled based on the heat absorber temperature Te.
  • the heat pump controller 32 supplements the shortage with the heat generated by the auxiliary heater 23. .. As a result, the vehicle interior is dehumidified and heated even when the outside temperature is low.
  • FIG. 6 shows how the refrigerant flows in the refrigerant circuit R in the dehumidifying and cooling mode (solid arrow).
  • the heat pump controller 32 opens the solenoid valve 17 and the solenoid valve 35, and closes the solenoid valve 20, the solenoid valve 21, the solenoid valve 22, and the solenoid valve 69.
  • the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is ventilated through the radiator 4, the air in the air flow passage 3 is heated by exchanging heat with the high temperature refrigerant in the radiator 4. On the other hand, the refrigerant in the radiator 4 is cooled by being deprived of heat by the air, and is condensed and liquefied.
  • the refrigerant exiting the radiator 4 reaches the outdoor expansion valve 6 via the refrigerant pipes 13E and 13J, and then passes through the outdoor expansion valve 6 controlled to open more (a larger valve opening area) than the heating mode or the dehumidifying and heating mode. It flows into the outdoor heat exchanger 7.
  • the refrigerant that has flowed into the outdoor heat exchanger 7 is condensed by being cooled there by traveling or by the outside air ventilated by the outdoor blower 15.
  • the refrigerant discharged from the outdoor heat exchanger 7 enters the refrigerant pipe 13B via the refrigerant pipe 13A, the electromagnetic valve 17, the receiver dryer unit 14, and the supercooling unit 16, and reaches the indoor expansion valve 8 via the check valve 18.
  • the refrigerant is decompressed by the indoor expansion valve 8, then flows into the heat absorber 9 through the electromagnetic valve 35, and evaporates. Due to the heat absorbing action at this time, moisture in the air blown out from the indoor blower 27 is condensed and attached to the heat absorber 9, and the air is cooled and dehumidified.
  • the refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 via the refrigerant pipe 13C, and is repeatedly sucked into the compressor 2 from the refrigerant pipe 13K via the refrigerant pipe 13K.
  • the air cooled and dehumidified by the heat absorber 9 is reheated (has a lower heating capacity than that during dehumidification heating) in the process of passing through the radiator 4 and the auxiliary heater 23 (when heat is generated). As a result, dehumidification and cooling of the vehicle interior are performed.
  • the heat pump controller 32 is based on the temperature of the heat absorber 9 (heat absorber temperature Te: parameter) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO which is the target temperature of the heat absorber 9 (target value of the heat absorber temperature Te). , The rotational speed of the compressor 2 is controlled so that the heat absorber temperature Te becomes the target heat absorber temperature TEO, and the radiator pressure Pci (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47 and the target radiator Based on the pressure PCO (the target value of the radiator pressure Pci), by controlling the valve opening of the outdoor expansion valve 6 so that the radiator pressure Pci becomes the target radiator pressure PCO, the reheat amount required by the radiator 4 ( Reheat amount).
  • the heat pump controller 32 supplements the shortage with the heat generated by the auxiliary heater 23. To do. As a result, dehumidifying and cooling are performed without lowering the temperature inside the vehicle compartment too much.
  • FIG. 7 shows how the refrigerant flows in the refrigerant circuit R in the cooling mode (solid arrow).
  • the heat pump controller 32 opens the solenoid valve 17, the solenoid valve 20, and the solenoid valve 35, and closes the solenoid valve 21, the solenoid valve 22, and the solenoid valve 69.
  • the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23.
  • the auxiliary heater 23 is not energized.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4.
  • the air in the air flow passage 3 is ventilated through the radiator 4, since the proportion thereof is small (because of only reheating (reheating) during cooling), it almost passes through the radiator 4,
  • the discharged refrigerant reaches the refrigerant pipe 13J via the refrigerant pipe 13E.
  • the electromagnetic valve 20 is opened, the refrigerant passes through the electromagnetic valve 20 and flows into the outdoor heat exchanger 7 as it is, and is cooled there by traveling or by the outside air ventilated by the outdoor blower 15 to be condensed and liquefied. To do.
  • the refrigerant discharged from the outdoor heat exchanger 7 enters the refrigerant pipe 13B via the refrigerant pipe 13A, the solenoid valve 17, the receiver dryer unit 14, and the supercooling unit 16, and reaches the indoor expansion valve 8 via the check valve 18.
  • the refrigerant is decompressed by the indoor expansion valve 8, then flows into the heat absorber 9 through the electromagnetic valve 35, and evaporates. Due to the heat absorbing action at this time, the air blown out from the indoor blower 27 and exchanging heat with the heat absorber 9 is cooled.
  • the refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 via the refrigerant pipe 13C, and is sucked into the compressor 2 via the refrigerant pipe 13K.
  • the air cooled by the heat absorber 9 is blown into the vehicle interior from the air outlet 29, so that the vehicle interior is cooled.
  • the heat pump controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te: parameter) detected by the heat absorber temperature sensor 48.
  • Air conditioning (priority) + battery cooling mode air conditioning (priority) + temperature controlled cooling mode
  • the air conditioning (priority) + battery cooling mode will be described with reference to FIG. FIG. 8 shows how the refrigerant flows in the refrigerant circuit R (solid arrow) in the air conditioning (priority) + battery cooling mode.
  • the heat pump controller 32 opens the electromagnetic valve 17, the electromagnetic valve 20, the electromagnetic valve 35, and the electromagnetic valve 69, and closes the electromagnetic valves 21 and 22.
  • the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23.
  • the auxiliary heater 23 is not energized.
  • the heat medium heater 63 is not energized.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4.
  • the air in the air flow passage 3 is ventilated through the radiator 4, since the proportion thereof is small (because of only reheating (reheating) during cooling), it almost passes through the radiator 4,
  • the discharged refrigerant reaches the refrigerant pipe 13J via the refrigerant pipe 13E.
  • the electromagnetic valve 20 since the electromagnetic valve 20 is open, the refrigerant passes through the electromagnetic valve 20 and flows into the outdoor heat exchanger 7 as it is, and is cooled there by traveling or by the outside air ventilated by the outdoor blower 15 to be condensed and liquefied. To do.
  • the refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B through the refrigerant pipe 13A, the solenoid valve 17, the receiver dryer unit 14, and the supercooling unit 16.
  • the refrigerant flowing into the refrigerant pipe 13B is branched after passing through the check valve 18, and one of the refrigerant flows through the refrigerant pipe 13B as it is to reach the indoor expansion valve 8.
  • the refrigerant flowing into the indoor expansion valve 8 is decompressed there, then flows into the heat absorber 9 through the electromagnetic valve 35, and is evaporated. Due to the heat absorbing action at this time, the air blown out from the indoor blower 27 and exchanging heat with the heat absorber 9 is cooled.
  • the refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 via the refrigerant pipe 13C, and then is sucked into the compressor 2 via the refrigerant pipe 13K.
  • the air cooled by the heat absorber 9 is blown into the vehicle interior from the air outlet 29, so that the vehicle interior is cooled.
  • the rest of the refrigerant that has passed through the check valve 18 is split, flows into the branch pipe 67, and reaches the auxiliary expansion valve 68.
  • the refrigerant is decompressed, then flows into the refrigerant channel 64B of the refrigerant-heat medium heat exchanger 64 via the electromagnetic valve 69, and evaporates there. At this time, it exerts an endothermic effect.
  • the refrigerant evaporated in the refrigerant passage 64B repeats the circulation in which the refrigerant is sucked into the compressor 2 from the refrigerant pipe 13K through the refrigerant pipe 71, the refrigerant pipe 13C and the accumulator 12 in sequence (shown by a solid arrow in FIG. 8).
  • the heat medium discharged from the circulation pump 62 reaches the heat medium flow passage 64A of the refrigerant-heat medium heat exchanger 64 in the heat medium pipe 66, and the refrigerant flow passage there.
  • the heat medium is cooled by exchanging heat with the refrigerant that evaporates in 64B and absorbing heat.
  • the heat medium exiting the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 reaches the heat medium heater 63.
  • the heat medium heating heater 63 does not generate heat in this operation mode, the heat medium passes through as it is to the battery 55 and exchanges heat with the battery 55. As a result, the battery 55 is cooled, and the heat medium after cooling the battery 55 is repeatedly sucked into the circulation pump 62 and repeatedly circulated (indicated by a dashed arrow in FIG. 8).
  • the heat pump controller 32 maintains the electromagnetic valve 35 in the open state, and based on the temperature of the heat absorber 9 (heat absorber temperature Te: parameter) detected by the heat absorber temperature sensor 48.
  • the rotation speed of the compressor 2 is controlled as shown in FIG.
  • the solenoid valve 69 is controlled to open and close as follows based on the temperature of the heat medium detected by the heat medium temperature sensor 76 (heat medium temperature Tw: transmitted from the battery controller 73).
  • the heat absorber temperature Te is the temperature of the heat absorber 9 in the embodiment.
  • the heat medium temperature Tw is adopted as the temperature of the object (heat medium) cooled by the refrigerant-heat medium heat exchanger 64 (heat exchanger for temperature adjustment) in the embodiment, but the temperature adjustment is performed. It is also an index showing the temperature of the target battery 55 (hereinafter the same).
  • FIG. 13 shows a block diagram of opening / closing control of the solenoid valve 69 in this air conditioning (priority) + battery cooling mode.
  • the heat medium temperature Tw detected by the heat medium temperature sensor 76 and a predetermined target heat medium temperature TWO as a target value of the heat medium temperature Tw are input to the temperature controlled target electromagnetic valve control unit 90 of the heat pump controller 32. It Then, the temperature controlled target electromagnetic valve control unit 90 sets the upper limit value TwUL and the lower limit value TwLL with a predetermined temperature difference above and below the target heat medium temperature TWO, and from the state where the electromagnetic valve 69 is closed.
  • the solenoid valve 69 is opened (instruction to open the solenoid valve 69).
  • the refrigerant flows into the refrigerant channel 64B of the refrigerant-heat medium heat exchanger 64, evaporates, and cools the heat medium flowing through the heat medium channel 64A. Therefore, the battery 55 is cooled by the cooled heat medium. To be done.
  • the solenoid valve 69 is closed (instruction to close the solenoid valve 69). After that, the solenoid valve 69 is repeatedly opened and closed as described above to control the heat medium temperature Tw to the target heat medium temperature TWO while giving priority to the cooling in the vehicle compartment, to cool the battery 55.
  • the heat pump controller 32 calculates the above-mentioned target outlet temperature TAO from the following formula (I).
  • the target outlet temperature TAO is a target value of the temperature of the air blown into the vehicle compartment from the outlet 29.
  • TAO (Tset-Tin) ⁇ K + Tbal (f (Tset, SUN, Tam)) .. (I)
  • Tset is the set temperature of the vehicle interior set by the air conditioning operation unit 53
  • Tin is the temperature of the vehicle interior air detected by the inside air temperature sensor 37
  • K is a coefficient
  • Tbal is the set temperature Tset
  • the solar radiation sensor 51 detects the temperature. It is a balance value calculated from the amount of solar radiation SUN and the outside air temperature Tam detected by the outside air temperature sensor 33.
  • the target outlet temperature TAO is higher as the outside air temperature Tam is lower, and is decreased as the outside air temperature Tam is increased.
  • the heat pump controller 32 selects any one of the above air conditioning operations based on the outside air temperature Tam detected by the outside air temperature sensor 33 and the target outlet temperature TAO at the time of startup. Further, after the start-up, each of the air conditioning operations is selected and switched according to changes in operating conditions such as the outside air temperature Tam, the target outlet temperature TAO, and the heat medium temperature Tw, environmental conditions, and setting conditions. For example, the transition from the cooling mode to the air conditioning (priority) + battery cooling mode is executed based on the input of the battery cooling request from the battery controller 73. In this case, the battery controller 73 outputs a battery cooling request and transmits it to the heat pump controller 32 and the air conditioning controller 45, for example, when the heat medium temperature Tw or the battery temperature Tcell rises above a predetermined value.
  • Battery cooling (priority) + air conditioning mode (cooling subject to temperature control (priority) + air conditioning mode)
  • the operation during charging of the battery 55 will be described. For example, when the plug for charging a quick charger (external power source) is connected and the battery 55 is being charged (these information is transmitted from the battery controller 73), the ignition (IGN) of the vehicle is turned on / off. Regardless of the above, when there is a battery cooling request and the air conditioning switch of the air conditioning operation unit 53 is turned on, the heat pump controller 32 executes battery cooling (priority) + air conditioning mode.
  • the way the refrigerant flows in the refrigerant circuit R in the battery cooling (priority) + air conditioning mode is the same as in the air conditioning (priority) + battery cooling mode shown in FIG.
  • the heat pump controller 32 maintains the electromagnetic valve 69 in an open state, and the heat detected by the heat medium temperature sensor 76 (transmitted from the battery controller 73) is detected. Based on the medium temperature Tw (the temperature of the object cooled by the refrigerant-heat medium heat exchanger 64: parameter), the rotation speed of the compressor 2 is controlled as shown in FIG. 14 described later.
  • the solenoid valve 35 is controlled to open and close as follows based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48.
  • FIG. 15 shows a block diagram of opening / closing control of the solenoid valve 35 in this battery cooling (priority) + air conditioning mode.
  • the heat absorber electromagnetic valve control unit 95 of the heat pump controller 32 is input with the heat absorber temperature Te detected by the heat absorber temperature sensor 48 and a predetermined target heat absorber temperature TEO as a target value of the heat absorber temperature Te. Then, the heat absorber electromagnetic valve control unit 95 sets the upper limit value TeUL and the lower limit value TeLL with a predetermined temperature difference above and below the target heat absorber temperature TEO, and sets the heat absorber temperature from the state in which the solenoid valve 35 is closed.
  • the solenoid valve 35 is closed (instruction to close the solenoid valve 35). Thereafter, such opening / closing of the solenoid valve 35 is repeated to control the heat absorber temperature Te to the target heat absorber temperature TEO while prioritizing the cooling of the battery 55 to cool the vehicle interior.
  • Battery cooling (independent) mode controlled cooling target (independent) mode
  • the heat pump controller 32 executes the battery cooling (single) mode. However, it is executed when the air conditioning switch is OFF and there is a battery cooling request (during traveling at a high outside air temperature) other than during charging of the battery 55.
  • FIG. 9 shows how the refrigerant flows in the refrigerant circuit R (solid arrow) in the battery cooling (single) mode.
  • the heat pump controller 32 opens the solenoid valve 17, the solenoid valve 20, and the solenoid valve 69, and closes the solenoid valve 21, the solenoid valve 22, and the solenoid valve 35.
  • the compressor 2 and the outdoor blower 15 are operated.
  • the indoor blower 27 is not operated and the auxiliary heater 23 is not energized. Further, the heat medium heater 63 is not energized in this operation mode.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is not ventilated to the radiator 4, it passes only here, and the refrigerant exiting the radiator 4 reaches the refrigerant pipe 13J via the refrigerant pipe 13E. At this time, since the electromagnetic valve 20 is open, the refrigerant passes through the electromagnetic valve 20 and flows into the outdoor heat exchanger 7 as it is, where it is air-cooled by the outside air ventilated by the outdoor blower 15 to be condensed and liquefied.
  • the refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B through the refrigerant pipe 13A, the solenoid valve 17, the receiver dryer unit 14, and the supercooling unit 16. After passing through the check valve 18, all of the refrigerant flowing into the refrigerant pipe 13B flows into the branch pipe 67 and reaches the auxiliary expansion valve 68. Here, the refrigerant is decompressed, then flows into the refrigerant channel 64B of the refrigerant-heat medium heat exchanger 64 via the electromagnetic valve 69, and evaporates there. At this time, it exerts an endothermic effect.
  • the refrigerant evaporated in the refrigerant flow path 64B repeatedly passes through the refrigerant pipe 71, the refrigerant pipe 13C, and the accumulator 12 and is repeatedly sucked into the compressor 2 from the refrigerant pipe 13K (represented by a solid arrow in FIG. 9).
  • the heat medium discharged from the circulation pump 62 reaches the heat medium flow passage 64A of the refrigerant-heat medium heat exchanger 64 in the heat medium pipe 66, and the refrigerant flow passage there.
  • the heat medium is cooled by being absorbed by the refrigerant evaporated in 64B.
  • the heat medium exiting the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 reaches the heat medium heater 63.
  • the heat medium heating heater 63 does not generate heat in this operation mode, the heat medium passes through as it is to the battery 55 and exchanges heat with the battery 55. As a result, the battery 55 is cooled, and the heat medium after cooling the battery 55 is repeatedly sucked into the circulation pump 62 and repeatedly circulated (indicated by a dashed arrow in FIG. 9).
  • the heat pump controller 32 will be described later based on the heat medium temperature Tw detected by the heat medium temperature sensor 76 (temperature of the object cooled by the refrigerant-heat medium heat exchanger 64: parameter). By controlling the rotation speed of the compressor 2 as described above, the battery 55 is cooled.
  • FIG. 10 shows how the refrigerant flows in the refrigerant circuit R in the defrosting mode (solid arrow).
  • the refrigerant evaporates in the outdoor heat exchanger 7 and absorbs heat from the outside air to reach a low temperature, so that the moisture in the outside air adheres to the outdoor heat exchanger 7 as frost.
  • the defrosting mode of the outdoor heat exchanger 7 is executed as follows.
  • the heat pump controller 32 sets the refrigerant circuit R to the heating mode described above, and then fully opens the valve opening degree of the outdoor expansion valve 6. Then, the compressor 2 is operated, the high-temperature refrigerant discharged from the compressor 2 is caused to flow into the outdoor heat exchanger 7 via the radiator 4 and the outdoor expansion valve 6, and is radiated by the outdoor heat exchanger 7. As a result, the frost formed on the outdoor heat exchanger 7 is melted and defrosted (FIG. 10).
  • the heat pump controller 32 sets a predetermined target radiator pressure PCO in the defrosting mode, and the target radiator pressure PCO and the radiator pressure Pci detected by the radiator pressure sensor 47 (high pressure of the refrigerant circuit R: parameter).
  • the rotation speed of the compressor 2 is controlled based on The heat pump controller 32 defrosts the outdoor heat exchanger 7 when the outdoor heat exchanger temperature TXO detected by the outdoor heat exchanger temperature sensor 49 becomes higher than a predetermined defrosting end temperature (for example, + 3 ° C.). Is completed and the defrosting mode is terminated.
  • a predetermined defrosting end temperature for example, + 3 ° C.
  • the heat pump controller 32 executes the battery heating mode when the air conditioning operation is executed or when the battery 55 is charged. In this battery heating mode, the heat pump controller 32 operates the circulation pump 62 to energize the heat medium heating heater 63. The solenoid valve 69 is closed.
  • the heat medium discharged from the circulation pump 62 reaches the heat medium flow passage 64A of the refrigerant-heat medium heat exchanger 64 through the heat medium pipe 66, and passes therethrough to reach the heat medium heater 63.
  • the heat medium heating heater 63 is generating heat, the heat medium is heated by the heat medium heating heater 63 to increase its temperature, and then reaches the battery 55 to exchange heat with the battery 55.
  • the battery 55 is heated, and the heat medium after heating the battery 55 is repeatedly circulated by being sucked into the circulation pump 62.
  • the heat pump controller 32 controls the energization of the heat medium heating heater 63 based on the heat medium temperature Tw detected by the heat medium temperature sensor 76 to set the heat medium temperature Tw to the predetermined target heat medium temperature. Adjust to TWO and heat battery 55.
  • the heat pump controller 32 is a control block diagram of FIG. 11 based on radiator pressure Pci (parameter which the compressor 2 controls) in the heating mode and the defrosting mode.
  • the target rotation speed of the compressor 2 (compressor target rotation speed) TGNCh is calculated by the following, and in the dehumidifying cooling mode, the cooling mode, and the air conditioning (priority) + battery cooling mode, the heat absorber temperature Te (the compressor 2 is the control target) is calculated.
  • the target rotation speed of the compressor 2 (compressor target rotation speed) TGNCc is calculated by the control block diagram of FIG.
  • the lower direction of the compressor target rotation speed TGNCh and the compressor target rotation speed TGNc is selected.
  • the battery cooling (priority) + air conditioning mode and the battery cooling (single) mode based on the heat medium temperature Tw (parameter controlled by the compressor 2), the target rotation of the compressor 2 is controlled by the control block diagram of FIG.
  • the number (compressor target rotation speed) TGNCw is calculated.
  • FIG. 11 is a control block diagram of the heat pump controller 32 that calculates the target rotation speed (compressor target rotation speed) TGNCh of the compressor 2 based on the radiator pressure Pci.
  • the air flow rate SW obtained by the air mix damper 28, the target supercooling degree TGSC that is the target value of the supercooling degree SC of the refrigerant at the outlet of the radiator 4, and the target heater described above that is the target value of the heater temperature Thp.
  • the F / F operation amount TGNChff of the compressor target rotation speed is calculated.
  • the heater temperature Thp is an air temperature (estimated value) on the leeward side of the radiator 4, and the radiator pressure Pci detected by the radiator pressure sensor 47 and the refrigerant outlet of the radiator 4 detected by the radiator outlet temperature sensor 44. It is calculated (estimated) from the temperature Tci.
  • the degree of supercooling SC is calculated from the refrigerant inlet temperature Tcxin and the refrigerant outlet temperature Tci of the radiator 4 detected by the radiator inlet temperature sensor 43 and the radiator outlet temperature sensor 44.
  • the target radiator pressure PCO is calculated by the target value calculator 79 based on the target supercooling degree TGSC and the target heater temperature TCO. In the defrosting mode, a preset target radiator temperature PCO is used. Further, the F / B (feedback) manipulated variable calculation unit 81 calculates the F / B manipulated variable TGNChfb of the compressor target rotational speed by PID calculation or PI calculation based on the target radiator pressure PCO and the radiator pressure Pci.
  • the F / F operation amount TGNChff calculated by the F / F operation amount calculation unit 78 and the F / B operation amount TGNChfb calculated by the F / B operation amount calculation unit 81 are added by the adder 82 to obtain a limit setting unit as TGNCh00. 83 is input.
  • the lower limit speed ECNpdLimLo and the upper limit speed ECNpdLimHi for control are set to TGNCh0, and then the compressor OFF control unit 84 is used to determine the target compressor speed TGNCh. That is, the rotation speed of the compressor 2 is limited to the upper limit rotation speed ECNpdLimHi or less.
  • the heat pump controller 32 controls the operation of the compressor 2 so that the radiator pressure Pci becomes the target radiator pressure PCO by the compressor target rotation speed TGNCh calculated based on the radiator pressure Pci.
  • the compressor OFF control unit 84 sets the compressor target rotation speed TGNCh to the above-described lower limit rotation speed ECNpdLimLo and sets the radiator pressure Pci to a predetermined upper limit value PUL and lower limit value PLL set above and below the target radiator pressure PCO.
  • the compressor 2 is stopped and the ON-OFF mode for ON-OFF controlling the compressor 2 is entered.
  • the compressor 2 In the ON-OFF mode of the compressor 2, when the radiator pressure Pci decreases to the lower limit value PLL, the compressor 2 is started to operate the compressor target rotation speed TGNCh as the lower limit rotation speed ECNpdLimLo, and heat is released in that state.
  • the container pressure Pci rises to the upper limit value PUL, the compressor 2 is stopped again. That is, the operation (ON) and the stop (OFF) of the compressor 2 at the lower limit rotation speed ECNpdLimLo are repeated.
  • the radiator pressure Pci decreases to the lower limit value PUL and the compressor 2 is started, and the radiator pressure Pci does not become higher than the lower limit value PUL for a predetermined time th2, the compressor 2 is turned on and off. Is completed and the normal mode is restored.
  • FIG. 12 is a control block diagram of the heat pump controller 32 that calculates the target rotation speed (compressor target rotation speed) TGNCc of the compressor 2 based on the heat absorber temperature Te.
  • the F / F operation amount calculation unit 86 of the heat pump controller 32 has an outside air temperature Tam, an air flow amount Ga of air flowing through the air flow passage 3 (may be a blower voltage BLV of the indoor blower 27), a target radiator pressure PCO, The F / F operation amount TGNCcff of the compressor target rotation speed is calculated based on the target heat absorber temperature TEO which is the target value of the heat absorber temperature Te.
  • the F / B manipulated variable calculation unit 87 also calculates the F / B manipulated variable TGNCcfb of the compressor target rotation speed by PID calculation or PI calculation based on the target heat absorber temperature TEO and the heat absorber temperature Te. Then, the F / F operation amount TGNCcff calculated by the F / F operation amount calculation unit 86 and the F / B operation amount TGNCcfb calculated by the F / B operation amount calculation unit 87 are added by the adder 88 to obtain a limit setting unit as TGNCc00. It is input to 89.
  • the lower limit rotational speed TGNCcLimLo and the upper limit rotational speed TGNCcLimHi for control are set to TGNCc0, and then the compressor OFF control unit 91 is used to determine the target compressor rotational speed TGNCc. Therefore, if the value TGNCc00 added by the adder 88 is within the upper limit rotational speed TGNCcLimHi and the lower limit rotational speed TGNCcLimLo and the ON-OFF mode described later does not occur, this value TGNCc00 is the target compressor rotational speed TGNCc (compressor 2 Will be the number of rotations).
  • the heat pump controller 32 controls the operation of the compressor 2 so that the heat absorber temperature Te becomes the target heat absorber temperature TEO by the compressor target rotation speed TGNCc calculated based on the heat absorber temperature Te.
  • the compressor OFF control unit 91 determines that the compressor target rotation speed TGNCc becomes the above-described lower limit rotation speed TGNCcLimLo, and the heat absorber temperature Te is set between the upper limit value TeUL and the lower limit value TeLL set above and below the target heat sink temperature TEO.
  • the compressor 2 is stopped and the ON-OFF mode in which the compressor 2 is ON-OFF controlled is entered.
  • FIG. 14 is a control block diagram of the heat pump controller 32 that calculates the target rotation speed (compressor target rotation speed) TGNCw of the compressor 2 based on the heat medium temperature Tw.
  • the F / F operation amount calculation unit 92 of the heat pump controller 32 uses the outside air temperature Tam, the flow rate Gw of the heat medium in the device temperature adjustment device 61 (calculated from the output of the circulation pump 62), and the heat generation amount of the battery 55 (battery). (Transmitted from the controller 73), battery temperature Tcell (transmitted from the battery controller 73), and target heat medium temperature TWO that is the target value of the heat medium temperature Tw, based on the F / F operation of the compressor target rotation speed. Calculate the quantity TGNCcwff.
  • the F / B operation amount calculation unit 93 performs the PID calculation or the PI calculation based on the target heat medium temperature TWO and the heat medium temperature Tw (transmitted from the battery controller 73) to perform the F / B operation amount TGNCwfb of the compressor target rotation speed. To calculate. Then, the F / F operation amount TGNCwff calculated by the F / F operation amount calculation unit 92 and the F / B operation amount TGNCwfb calculated by the F / B operation amount calculation unit 93 are added by the adder 94 to obtain a limit setting unit as TGNCw00. 96 is input.
  • the lower limit speed TGNCwLimLo for control and the upper limit speed TGNCwLimHi are set to TGNCw0, and then the compressor OFF control unit 97 is used to determine the target compressor speed TGNCw. Therefore, if the value TGNCw00 added by the adder 94 is within the upper limit rotation speed TGNCwLimHi and the lower limit rotation speed TGNCwLimLo and the ON-OFF mode described later does not occur, this value TGNCw00 is the target compressor rotation speed TGNCw (compressor 2 Will be the number of rotations). In the normal mode, the heat pump controller 32 controls the operation of the compressor 2 so that the heat medium temperature Tw becomes the target heat medium temperature TWO by the compressor target rotation speed TGNCw calculated based on the heat medium temperature Tw.
  • the compressor OFF control unit 97 determines that the compressor target rotation speed TGNCw becomes the above-described lower limit rotation speed TGNCwLimLo, and the heat medium temperature Tw is the upper limit value TwUL and the lower limit value TwLL set above and below the target heat medium temperature TWO.
  • the compressor 2 is stopped and the ON-OFF mode for ON-OFF controlling the compressor 2 is entered.
  • the compressor 2 In the ON-OFF mode of the compressor 2 in this case, when the heat medium temperature Tw rises to the upper limit value TwUL, the compressor 2 is started and the compressor target rotation speed TGNCw is operated as the lower limit rotation speed TGNCwLimLo, and the state is maintained. If the heat medium temperature Tw has dropped to the lower limit value TwLL, the compressor 2 is stopped again. That is, the operation (ON) and the stop (OFF) of the compressor 2 at the lower limit rotation speed TGNCwLimLo are repeated.
  • (12-1) Fail-Safe Control in Heating Mode and Defrosting Mode For example, in the heating mode of FIG. 4 and the defrosting mode of FIG. 10 described above, the outdoor expansion valve 6 and the solenoid valve (for heating) 21 are disconnected or short-circuited. When a closing failure occurs in which the refrigerant remains closed, the refrigerant circuit R is closed because the other valve devices are closed, and the circulation of the refrigerant to the radiator 4 is delayed.
  • the radiator pressure Pci detected by the radiator pressure sensor 47 is input to the F / B operation amount calculation unit 81 in FIG. 11 and used for controlling the compressor 2. That is, the outdoor expansion valve 6 and the electromagnetic valve 21 serve as a valve device that controls the flow of the refrigerant to the location where the radiator pressure sensor 47 for detecting the parameter used to control the compressor 2 in the heating mode is provided.
  • the heat pump controller 32 stops the compressor 2 when the outdoor expansion valve 6 or the electromagnetic valve 21 fails to close in the heating mode and the defrosting mode, or when their states become unknown. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the outdoor expansion valve 6 and the electromagnetic valve 21 are valves that control the flow of the refrigerant to the location where the radiator pressure sensor 47 for detecting the parameter used for controlling the compressor 2 in the dehumidifying and heating mode is provided. It becomes a device.
  • radiator pressure Pci which is a parameter used for controlling the compressor 2 in the dehumidifying and heating mode
  • the F / B control cannot be performed and the compressor 2 is normally operated. Out of control.
  • the compressor 2 cannot be normally controlled in the same manner.
  • the heat pump controller 32 stops the compressor 2 when the outdoor expansion valve 6 or the electromagnetic valve 21 fails to close, or when their states become unknown. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the outdoor expansion valve 6, the solenoid valve 17, and the solenoid valve 35 control the flow of the refrigerant to the location where the heat absorber temperature sensor 48 for detecting the parameter used for controlling the compressor 2 in the dehumidifying and cooling mode is provided. It becomes a valve device.
  • the heat pump controller 32 stops the compressor 2 when the outdoor expansion valve 6, the solenoid valve 17, or the solenoid valve 35 has a closing failure, or when their states become unknown. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the flow of the refrigerant to the location where the outdoor expansion valve 6, the solenoid valve 20, the solenoid valve 17, and the solenoid valve 35 are provided with the heat absorber temperature sensor 48 for detecting the parameters used for controlling the compressor 2 in the cooling mode. It becomes a valve device for controlling the.
  • the compressor 2 When the refrigerant circuit R is closed due to the closing failure of the outdoor expansion valve 6, the electromagnetic valve 20, the electromagnetic valve 17, and the electromagnetic valve 35, and the refrigerant does not flow to the heat absorber 9, the compressor 2 is also operated in the cooling mode.
  • the heat absorber temperature Te which is a parameter used for the control of, is not appropriate, and the F / B control cannot be performed, so that the compressor 2 cannot be normally controlled.
  • the solenoid valve 20 the solenoid valve 17, and the solenoid valve 35, and their states become unknown, the compressor 2 is normally operated normally. Out of control.
  • the heat absorber temperature Te detected by the heat absorber temperature sensor 48 is input to the F / B operation amount calculation unit 87 in FIG. 12 and used for controlling the compressor 2. That is, the outdoor expansion valve 6, the solenoid valve 20, the solenoid valve 17, and the solenoid valve 35 are provided with the heat absorber temperature sensor 48 for detecting a parameter used for controlling the compressor 2 in the air conditioning (priority) + battery cooling mode. It serves as a valve device that controls the flow of the refrigerant to the location.
  • the compressor 2 When the refrigerant does not flow to the heat absorber 9 due to the closing failure of the outdoor expansion valve 6, the solenoid valve 20, the solenoid valve 17, and the solenoid valve 35, the compressor 2 is similarly controlled in the air conditioning (priority) + battery cooling mode.
  • the heat absorber temperature Te which is a parameter used for, is not appropriate, and F / B control cannot be performed, so that the compressor 2 cannot be controlled normally.
  • the solenoid valve 20, the solenoid valve 17, and the solenoid valve 35, and their states become unknown, the compressor 2 is normally operated normally. Out of control.
  • the heat pump controller 32 closes the outdoor expansion valve 6 and the solenoid valve 20, or closes the solenoid valve 17, or closes the solenoid valve 35. Or, if their state becomes unknown, the compressor 2 is stopped. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the heat medium temperature Tw detected by the heat medium temperature sensor 76 is input to the F / B operation amount calculation unit 93 in FIG. 14 and used for controlling the compressor 2. That is, the outdoor expansion valve 6, the solenoid valve 20, the solenoid valve 17, and the solenoid valve 69 affect the heat medium temperature sensor 76 for detecting the parameter used to control the compressor 2 in the battery cooling (priority) + air conditioning mode.
  • the valve device serves to control the flow of the refrigerant to the location (refrigerant-heat medium heat exchanger 64).
  • the battery cooling (priority) + air conditioning mode is similarly set.
  • the heat medium temperature Tw which is a parameter used for controlling the compressor 2
  • F / B control cannot be performed, so that the compressor 2 cannot be normally controlled.
  • the heat pump controller 32 closes the outdoor expansion valve 6 and the solenoid valve 20, or closes the solenoid valve 17, or closes the solenoid valve 69. Or, if their state becomes unknown, the compressor 2 is stopped. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the heat medium temperature Tw detected by the heat medium temperature sensor 76 is input to the F / B operation amount calculation unit 93 in FIG. 14 and used for controlling the compressor 2. That is, the location where the outdoor expansion valve 6, the solenoid valve 20, the solenoid valve 17, and the solenoid valve 69 affect the heat medium temperature sensor 76 for detecting the parameter used to control the compressor 2 in the battery cooling (single) mode ( The valve device controls the flow of the refrigerant to the refrigerant + heat medium heat exchanger 64).
  • the compressor 2 When the outdoor expansion valve 6, the solenoid valve 20, the solenoid valve 17, and the solenoid valve 69 are closed, the refrigerant circuit R is closed, and the refrigerant does not flow to the refrigerant-heat medium heat exchanger 64.
  • the heat medium temperature Tw which is a parameter used for controlling the compressor 2 in the cooling (single) mode, is also invalid, and F / B control cannot be performed, so that the compressor 2 cannot be normally controlled. Further, even when an abnormality occurs in the communication of the control signals to the outdoor expansion valve 6, the solenoid valve 20, the solenoid valve 17, and the solenoid valve 69, and their states become unknown, the compressor 2 is normally operated in the same manner. Out of control.
  • the heat pump controller 32 causes a closing failure of the outdoor expansion valve 6 and the solenoid valve 20, or a closing failure of the solenoid valve 17, or a closing failure of the solenoid valve 69, or The compressor 2 is stopped when those states become unknown. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the heat pump controller 32 supplies the refrigerant to the location where the sensor for detecting the parameter used to control the compressor 2 is provided or the location that affects the sensor. If the valve device that controls the flow of the valve has a closing failure, or if the state of the valve device is unknown, the compressor 2 is stopped, so that the valve device fails to close or the state of the valve device. When the value detected by the sensor for detecting the parameter used for controlling the compressor 2 becomes invalid, the compressor 2 is stopped and the compressor 2 falls into an abnormal control state. Therefore, the reliability can be improved.
  • FIG. 16 shows a configuration diagram of a vehicle air conditioner 1 according to another embodiment of the present invention.
  • the vehicle air conditioner 1 of this embodiment is not provided with the device temperature adjustment device 61 of the first embodiment and is not provided with the solenoid valve 35.
  • Other configurations are the same as in the case of FIG.
  • the heat pump controller 32 switches between the heating mode, the dehumidifying and heating mode, the dehumidifying and cooling mode, the cooling mode, and the defrosting mode as in the case of the above-described first embodiment and executes the operation.
  • the air conditioner is performed in the vehicle interior (However, since the solenoid valve 35 is not provided, its control is not performed).
  • the heat pump controller 32 also performs fail-safe control in the heating mode (12-1), fail-safe control in the dehumidifying heating mode (12-2), and (12-3) dehumidifying and cooling mode in this embodiment.
  • Fail safe control, (12-4) Perform fail safe control in the cooling mode.
  • FIG. 17 shows a configuration diagram of a vehicle air conditioner 1 according to another embodiment of the present invention.
  • the same reference numerals as those in FIG. 16 have the same or similar functions.
  • the refrigerant pipe 13F, the solenoid valve 22, and the solenoid valve 20 do not exist
  • the refrigerant pipe 13E is connected to the refrigerant pipe 13J
  • the outdoor expansion valve 6 is connected to this refrigerant pipe 13J.
  • the check valve 18 does not exist at the outlet of the supercooling unit 16 and is directly connected to the refrigerant pipe 13B.
  • an internal heat exchanger 30 for exchanging heat between the refrigerants flowing through the refrigerant pipes 13B and 13C is provided (the muffler 5 and the strainer 19 are not shown but are provided similarly). ..
  • an electromagnetic valve 98 as a valve device that is closed during dehumidifying heating and MAX cooling described later is provided in the refrigerant pipe 13G between the discharge side of the compressor 2 and the inlet side of the radiator 4.
  • the refrigerant pipe 13G is branched to the bypass pipe 75 on the upstream side of the solenoid valve 98, and the bypass pipe 75 is connected to the outdoor expansion valve via the solenoid valve 99 which is opened during dehumidification heating and MAX cooling. 6 is connected to the refrigerant pipe 13J on the downstream side.
  • the bypass device 100 is constituted by the bypass pipe 75, the solenoid valve 98, and the solenoid valve 99.
  • the electromagnetic valves 98 and 99 are also connected to and controlled by the heat pump controller 32 shown in FIG. Further, the device temperature adjusting device 61 as in the first embodiment is not provided, and the solenoid valve 35 does not exist.
  • the dehumidifying and heating mode in which the refrigerant discharged from the compressor 2 directly flows into the outdoor heat exchanger 7 or MAX This makes it possible to smoothly switch between the cooling mode and the heating mode in which the refrigerant discharged from the compressor 2 flows into the radiator 4, the dehumidifying cooling mode, or the cooling mode.
  • the auxiliary heater 23 (PTC heater) forming the auxiliary heating device is located on the windward side (air upstream side) of the radiator 4 with respect to the air flow in the air flow passage 3. It is provided in.
  • the heat pump controller 32 switches between and executes the heating mode, the dehumidifying and heating mode, the dehumidifying and cooling mode, the cooling mode, and the MAX cooling mode (maximum cooling mode).
  • the heating mode, the dehumidifying cooling mode, and the cooling mode are selected, the operation and the flow of the refrigerant in the defrosting mode are the same as those in the above-described first and second embodiments, and thus the description thereof will be omitted.
  • the solenoid valve 98 is opened and the solenoid valve 99 is closed in these heating mode, dehumidifying and cooling mode, cooling mode and defrosting mode.
  • the opening degree of the outdoor expansion valve 6 is fully opened. Further, since the above-mentioned blowing modes and introduction modes are the same, the description thereof will be omitted.
  • the heat pump controller 32 opens the solenoid valve 17 and opens the solenoid valve 21. close. Further, the solenoid valve 98 is closed, the solenoid valve 99 is opened, and the valve opening degree of the outdoor expansion valve 6 is fully closed. Then, the compressor 2 is operated.
  • the heat pump controller 32 operates each of the blowers 15 and 27, and the air mix damper 28 basically blows all the air in the air flow passage 3 blown out from the indoor blower 27 and passed through the heat absorber 9 to the auxiliary heater 23 and the radiator. Although it is in a state of ventilating to 4, the air volume is also adjusted.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 2 to the refrigerant pipe 13G flows into the bypass pipe 75 without going to the radiator 4, passes through the solenoid valve 99, and is located downstream of the outdoor expansion valve 6 in the refrigerant pipe. It reaches 13J.
  • the outdoor expansion valve 6 since the outdoor expansion valve 6 is fully closed, the refrigerant flows into the outdoor heat exchanger 7.
  • the refrigerant that has flowed into the outdoor heat exchanger 7 is condensed by being cooled there by traveling or by the outside air ventilated by the outdoor blower 15.
  • the refrigerant discharged from the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13A through the solenoid valve 17 into the receiver dryer section 14 and the supercooling section 16. Here, the refrigerant is supercooled.
  • the refrigerant is decompressed by the indoor expansion valve 8, then flows into the heat absorber 9 and evaporates. Due to the heat absorbing action at this time, the air blown out from the indoor blower 27 is cooled, and the moisture in the air is condensed and attached to the heat absorber 9, so that the air in the air flow passage 3 is cooled, and Dehumidified.
  • the heat pump controller 32 energizes the auxiliary heater 23 to generate heat. As a result, the air cooled by the heat absorber 9 and dehumidified is further heated in the process of passing through the auxiliary heater 23, and the temperature rises, so that dehumidification and heating of the vehicle interior is performed.
  • the heat pump controller 32 performs compression based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO which is the target value of the heat absorber temperature Te.
  • the rotation speed of the machine 2 and controlling energization (heating by heat generation) of the auxiliary heater 23 based on the temperature of the auxiliary heater 23 detected by the auxiliary heater temperature sensors 50A and 50B and the target heater temperature TCO, While properly cooling and dehumidifying the air in the device 9, the temperature of the air blown into the vehicle interior from the air outlet 29 by the heating by the auxiliary heater 23 is accurately prevented. This makes it possible to control the temperature of the air blown into the vehicle compartment to an appropriate heating temperature while dehumidifying the air, and to realize comfortable and efficient dehumidification and heating of the vehicle compartment.
  • the auxiliary heater 23 Since the auxiliary heater 23 is arranged on the air upstream side of the radiator 4, the air heated by the auxiliary heater 23 passes through the radiator 4, but in this dehumidifying and heating mode, the refrigerant is fed to the radiator 4. Since the heat is not flowed, the disadvantage that the radiator 4 absorbs heat from the air heated by the auxiliary heater 23 is also eliminated. That is, the radiator 4 is prevented from lowering the temperature of the air blown into the vehicle compartment, and the COP is also improved.
  • MAX cooling mode maximum cooling mode of the vehicle air conditioner 1 of FIG.
  • the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valve 21. Further, the solenoid valve 98 is closed, the solenoid valve 99 is opened, and the valve opening degree of the outdoor expansion valve 6 is fully closed. Then, the compressor 2 is operated and the auxiliary heater 23 is not energized.
  • the heat pump controller 32 drives the blowers 15 and 27, and the air mix damper 28 causes the air in the air flow passage 3 that has been blown out from the indoor blower 27 and passed through the heat absorber 9 to be ventilated to the auxiliary heater 23 and the radiator 4. Adjust the ratio to be adjusted.
  • the high-temperature high-pressure gas refrigerant discharged from the compressor 2 to the refrigerant pipe 13G flows into the bypass pipe 75 without going to the radiator 4, passes through the solenoid valve 99, and is located downstream of the outdoor expansion valve 6 in the refrigerant pipe. It reaches 13J.
  • the outdoor expansion valve 6 since the outdoor expansion valve 6 is fully closed, the refrigerant flows into the outdoor heat exchanger 7.
  • the refrigerant that has flowed into the outdoor heat exchanger 7 is condensed by being cooled there by traveling or by the outside air ventilated by the outdoor blower 15.
  • the refrigerant discharged from the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13A through the solenoid valve 17 into the receiver dryer section 14 and the supercooling section 16. Here, the refrigerant is supercooled.
  • the refrigerant exiting the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 30, and reaches the indoor expansion valve 8.
  • the refrigerant is decompressed by the indoor expansion valve 8, then flows into the heat absorber 9 and evaporates.
  • the air blown from the indoor blower 27 is cooled by the heat absorbing action at this time. Further, the water in the air is condensed and attached to the heat absorber 9, so that the air in the air flow passage 3 is dehumidified.
  • the refrigerant evaporated in the heat absorber 9 flows out into the refrigerant pipe 13C, reaches the accumulator 12 via the internal heat exchanger 19, and is repeatedly sucked into the compressor 2 through the circulation.
  • the heat pump controller 32 is similar to the case of FIG. 12, and the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48 (heat absorber temperature Te) and the target heat absorber described above which is its target value.
  • the rotation speed of the compressor 2 is controlled based on the temperature TEO.
  • the solenoid valve 21, and the solenoid valve 98 are provided with the radiator pressure sensor 47 for detecting the parameter used for controlling the compressor 2 in the heating mode and the defrosting mode in this case.
  • the valve device controls the flow of the refrigerant.
  • the radiator pressure Pci which is a parameter, is not appropriate, F / B control cannot be performed, and the compressor 2 cannot be normally controlled. Further, even when an abnormality occurs in the communication of the control signal to the outdoor expansion valve 6, the solenoid valve 21, and the solenoid valve 98, and their states become unknown, the compressor 2 cannot be controlled normally in the same manner.
  • the heat pump controller 32 operates the compressor 2 when the outdoor expansion valve 6, the electromagnetic valve 21 or the electromagnetic valve 98 has a closing failure or when their states become unknown. Stop. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the heat absorber temperature Te detected by the heat absorber temperature sensor 48 is input to the F / B operation amount calculation unit 87 in FIG. 12 and used for controlling the compressor 2. That is, the flow of the refrigerant to the location where the heat absorber temperature sensor 48 for detecting the parameters used by the solenoid valve 17 and the solenoid valve 99 in this case to control the compressor 2 in the dehumidifying heating mode and the MAX cooling mode is provided. It becomes the valve device to control.
  • the heat pump controller 32 stops the compressor 2 when the electromagnetic valve 17 or the electromagnetic valve 99 fails to close in the dehumidifying heating mode and the MAX cooling mode, or when their states become unknown. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the flow of the refrigerant to the place where the heat absorber temperature sensor 48 for detecting the parameters used by the outdoor expansion valve 6, the solenoid valve 17, and the solenoid valve 98 to control the compressor 2 in the dehumidifying cooling mode and the cooling mode is provided. It becomes a valve device for controlling the.
  • the compressor 2 When the refrigerant circuit R is closed due to the closed failure of the outdoor expansion valve 6, the solenoid valve 17, and the solenoid valve 98, and the refrigerant does not flow to the heat absorber 9, the compressor 2 is similarly operated in the dehumidifying cooling mode and the cooling mode.
  • the heat absorber temperature Te which is a parameter used for the control of, is not appropriate, and the F / B control cannot be performed, so that the compressor 2 cannot be normally controlled. Further, even if the communication of the control signals to the outdoor expansion valve 6, the solenoid valve 17, and the solenoid valve 98 becomes abnormal and the states thereof become unknown, the compressor 2 cannot be controlled normally in the same manner.
  • the heat pump controller 32 causes the closing failure of the outdoor expansion valve 6, the closing failure of the solenoid valve 17, or the closing failure of the solenoid valve 98, or the state thereof.
  • the compressor 2 is stopped. This avoids the inconvenience that the compressor 2 falls into an abnormal control state and improves reliability.
  • the valve device that controls the flow of the refrigerant to the location where the sensor for detecting the parameter used by the heat pump controller 32 to control the compressor 2 is provided has a closing failure. If at least one of the following has occurred, or the state of the valve device is unknown, the compressor 2 is stopped, so that the valve device fails to close or the valve device is closed. When the state of is not known and the detection value of the sensor for detecting the parameter used for controlling the compressor 2 becomes invalid, the compressor 2 is stopped and the compressor 2 falls into an abnormal control state. It is possible to avoid the above and improve the reliability.
  • the heat medium temperature Tw is adopted as the temperature of the object (heat medium) cooled by the refrigerant-heat medium heat exchanger 64 (heat exchanger for temperature adjustment), but the battery temperature Tcell is used. May be adopted as the temperature of the object cooled by the refrigerant-heat medium heat exchanger 64 (heat exchanger for temperature control), and the temperature of the refrigerant-heat medium heat exchanger 64 (refrigerant-heat medium heat exchange The temperature of the container 64 itself, the temperature of the refrigerant flowing out of the refrigerant channel 64B, etc.) may be adopted as the temperature of the refrigerant-heat medium heat exchanger 64 (heat exchanger for temperature adjustment).
  • the heat medium is circulated to control the temperature of the battery 55, but the present invention is not limited to this, and the heat exchange for the temperature-controlled object in which the refrigerant and the battery 55 (the temperature-controlled object) are directly heat-exchanged. May be provided.
  • the battery temperature Tcell becomes the temperature of the object to be cooled by the heat exchanger for temperature adjustment
  • the battery temperature sensor 77 becomes the temperature sensor for temperature adjustment in the present invention.
  • the battery 55 can be cooled while cooling the vehicle interior in the air conditioning (priority) + battery cooling mode and the battery cooling (priority) + air conditioning mode for simultaneously cooling the vehicle interior and cooling the battery 55.
  • the cooling of the battery 55 is not limited to during cooling, but other air conditioning operation, such as the dehumidifying and heating operation described above and the cooling of the battery 55, can be performed. You may make it perform simultaneously.
  • the solenoid valve 69 is opened, and a part of the refrigerant flowing toward the heat absorber 9 via the refrigerant pipe 13F is caused to flow into the branch pipe 67 and flow into the refrigerant-heat medium heat exchanger 64.
  • the electromagnetic valve 35 is the heat absorber valve device (valve device) and the electromagnetic valve 69 is the temperature controlled valve device (valve device).
  • the indoor expansion valve 8 and the auxiliary expansion valve 68 are fully closed.
  • the solenoid valves 35 and 69 are not necessary, the indoor expansion valve 8 serves as the heat absorber valve device (valve device) of the present invention, and the auxiliary expansion valve 68 serves as a temperature control target. It becomes a valve device (valve device).
  • the method for detecting the closing failure of each valve device includes not only the case of detecting electrically as in the embodiment but also the method of detecting mechanically. Further, it goes without saying that the configuration and the numerical values of the refrigerant circuit R described in the embodiments are not limited thereto and can be changed without departing from the spirit of the present invention.

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

La présente invention aborde le problème de la réalisation d'un dispositif de climatisation pour véhicule qui est capable d'empêcher un déclin de la fiabilité du compresseur provoqué lorsque les paramètres à utiliser dans la commande du compresseur deviennent inappropriés en raison d'une défaillance de fermeture ou analogue d'un dispositif de vanne. La solution selon l'invention porte sur un compresseur (2), un radiateur (4), un dispositif d'absorption de chaleur (9), un échangeur de chaleur extérieur (7), un circuit de réfrigérant (R) qui comprend une pluralité de dispositifs de vanne, et un dispositif de commande (11). Le dispositif de commande arrête le compresseur (2) dans le cas d'une défaillance de fermeture d'un dispositif de vanne pour réguler le débit de réfrigérant vers une zone où se trouvent un capteur de pression de radiateur (47) et un capteur de température de dispositif d'absorption de chaleur (48) destinés à détecter les paramètres à utiliser dans une commande de compresseur, ou lorsque l'état dudit dispositif de vanne n'est pas clair.
PCT/JP2019/036224 2018-11-13 2019-09-13 Dispositif de climatisation pour véhicule WO2020100410A1 (fr)

Priority Applications (1)

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JP2018212969A JP2020079004A (ja) 2018-11-13 2018-11-13 車両用空気調和装置
JP2018-212969 2018-11-13

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JP7480690B2 (ja) 2020-12-09 2024-05-10 株式会社デンソー 車両用空調装置

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JP7476779B2 (ja) 2020-12-09 2024-05-01 株式会社デンソー 車両用空調装置
JP2022148724A (ja) * 2021-03-24 2022-10-06 サンデン・オートモーティブクライメイトシステム株式会社 車両用空調装置

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JP2017116154A (ja) * 2015-12-22 2017-06-29 ダイキン工業株式会社 空気調和装置
WO2018198581A1 (fr) * 2017-04-26 2018-11-01 サンデン・オートモーティブクライメイトシステム株式会社 Dispositif de conditionnement d'air pour véhicule

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JP5772764B2 (ja) * 2011-10-05 2015-09-02 株式会社デンソー 統合弁およびヒートポンプサイクル
JP6470026B2 (ja) * 2014-12-04 2019-02-13 サンデンホールディングス株式会社 車両用空気調和装置
JP6831209B2 (ja) * 2016-10-27 2021-02-17 サンデン・オートモーティブクライメイトシステム株式会社 車両用空気調和装置
CN106904058B (zh) * 2017-03-10 2019-12-31 安徽江淮汽车集团股份有限公司 热泵空调系统中电子膨胀阀控制方法及装置

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JP2017116154A (ja) * 2015-12-22 2017-06-29 ダイキン工業株式会社 空気調和装置
WO2018198581A1 (fr) * 2017-04-26 2018-11-01 サンデン・オートモーティブクライメイトシステム株式会社 Dispositif de conditionnement d'air pour véhicule

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7480690B2 (ja) 2020-12-09 2024-05-10 株式会社デンソー 車両用空調装置

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