WO2019150832A1 - 車両用空気調和装置 - Google Patents

車両用空気調和装置 Download PDF

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Publication number
WO2019150832A1
WO2019150832A1 PCT/JP2018/047131 JP2018047131W WO2019150832A1 WO 2019150832 A1 WO2019150832 A1 WO 2019150832A1 JP 2018047131 W JP2018047131 W JP 2018047131W WO 2019150832 A1 WO2019150832 A1 WO 2019150832A1
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WIPO (PCT)
Prior art keywords
dehumidifying
heating
temperature
mode
heat
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PCT/JP2018/047131
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English (en)
French (fr)
Japanese (ja)
Inventor
耕平 山下
竜 宮腰
徹也 石関
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
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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 CN201880086816.7A priority Critical patent/CN111601724B/zh
Publication of WO2019150832A1 publication Critical patent/WO2019150832A1/ja

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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 that air-conditions the interior of a vehicle, and more particularly to a vehicle air conditioner suitable for a hybrid vehicle or an electric vehicle.
  • Hybrid vehicles and electric vehicles have come into widespread use due to the emergence of environmental problems in recent years.
  • a compressor that compresses and discharges the refrigerant
  • a radiator that is provided on the vehicle interior side and dissipates the refrigerant, and is provided on the vehicle interior side.
  • a heat absorber that absorbs the refrigerant and an outdoor heat exchanger that is provided outside the passenger compartment to dissipate or absorb the heat of the refrigerant are provided, and the refrigerant discharged from the compressor is dissipated in the heat radiator, and the refrigerant dissipated in the radiator is Heating mode in which heat is absorbed in the heat exchanger, dehumidifying heating mode in which the refrigerant discharged from the compressor is dissipated in the radiator, and the refrigerant dissipated in the radiator is absorbed in the heat absorber and the outdoor heat exchanger, and discharged from the compressor In the outdoor heat exchanger, the dehumidifying and cooling mode for dissipating heat in the radiator and the outdoor heat exchanger and absorbing heat in the heat absorber, and the refrigerant discharged from the compressor in the outdoor heat exchanger was heated, which was capable of switching cooling mode to heat absorption have been developed in the heat sink (e.g., see Patent Document 1).
  • an outdoor expansion valve is provided at the inlet of the outdoor heat exchanger, and an indoor expansion valve is provided at the inlet of the heat absorber.
  • a bypass circuit is provided in parallel with the series circuit of the outdoor expansion valve and the outdoor heat exchanger.
  • switching of the operation mode when shifting from the dehumidifying and heating mode to the dehumidifying and cooling mode can achieve the required cooling capacity during the operation in the dehumidifying and heating mode. It was done when it became impossible.
  • the switching of the operation mode when shifting from the dehumidifying and cooling mode to the dehumidifying and heating mode realizes the heating capacity required for the dehumidifying and heating mode based on the environmental conditions and operating conditions during operation in the dehumidifying and cooling mode. Therefore, it is difficult to make a transition from the dehumidifying and cooling mode to the dehumidifying and heating mode because the required cooling capacity can be realized.
  • an auxiliary heater (auxiliary heating device comprising an electric heater) is provided and energized to generate heat to assist reheating in the dehumidifying and cooling mode. I was going. Therefore, power consumption increases and COP (coefficient of performance) decreases. Thereby, especially in the case of a vehicle that runs on a battery, there is a disadvantage that the running distance is shortened.
  • a mechanical expansion valve is used as the indoor expansion valve, the conditions for shifting to the dehumidifying and heating mode described above are set more severely in consideration of excessively reducing the refrigerant due to variations (individual differences). Therefore, it becomes more difficult to shift to the dehumidifying and heating mode.
  • the dehumidifying heating mode may be executed.
  • a vehicle not provided with the outside air humidity sensor it is determined that the dehumidifying heating mode can be executed. I can't.
  • the present invention has been made to solve the conventional technical problem, and when switching between the dehumidifying and heating mode and the dehumidifying and cooling mode, the dehumidifying and heating mode can be executed more efficiently.
  • An object of the present invention is to provide a vehicle air conditioner that can be used.
  • the vehicle air conditioner of the present invention heats the compressor that compresses the refrigerant, the air flow passage through which the air supplied to the vehicle interior flows, and the air that dissipates the refrigerant and is supplied from the air flow passage to the vehicle interior.
  • a dehumidifying and heating mode in which at least the refrigerant discharged from the compressor is radiated by a radiator, and the radiated refrigerant is decompressed and then absorbed by a heat absorber and an outdoor heat exchanger.
  • the control device When operating in the humidifying and heating mode, when the predetermined dehumidifying and cooling transition conditions are met, the mode is shifted to the dehumidifying and cooling mode. When operating in the dehumidifying and cooling mode, when the predetermined dehumidifying and heating conditions are met, the mode is shifted to the dehumidifying and heating mode.
  • the dehumidifying and heating mode is shifted regardless of whether or not the dehumidifying and heating mode is satisfied.
  • the predetermined fluctuation of the operating condition or operating condition in the above invention can realize the heating capacity required even in the dehumidifying heating mode, and is required. It is characterized by fluctuations in operating conditions or operating conditions that suggest that the cooling capacity can be realized.
  • the air conditioner for a vehicle is the vehicle air conditioner according to each of the above inventions, wherein when the control device is operating in the dehumidifying and cooling mode and the set temperature Tset in the passenger compartment is increased by a predetermined value or more within a predetermined period, Regardless of whether or not the heating transition condition is satisfied, the present invention is characterized by shifting to the dehumidifying heating mode.
  • a vehicle air conditioner according to the above-described invention, wherein the control device operates within the predetermined period during the operation in the dehumidifying and cooling mode while the target blowing temperature TAO, which is the target temperature of the air blown into the passenger compartment.
  • the dehumidifying and heating mode is shifted regardless of whether or not the dehumidifying and heating condition is satisfied.
  • the air conditioner for a vehicle according to each of the inventions described above, wherein the control device operates in the dehumidifying and cooling mode, and the target heater temperature TCO, which is the target temperature of the radiator increases within a predetermined period by a predetermined value or more. In this case, the dehumidifying and heating mode is shifted regardless of whether or not the dehumidifying and heating condition is satisfied.
  • the air conditioner for a vehicle is the vehicle air conditioner according to any of the above aspects, wherein when the control device operates in the dehumidifying and cooling mode and the target heat absorber temperature TEO, which is the target temperature of the heat absorber, has a predetermined fluctuation, the dehumidifying device Regardless of whether or not the heating transition condition is satisfied, the present invention is characterized by shifting to the dehumidifying heating mode.
  • the vehicle air conditioner according to the invention of claim 8 is characterized in that, in each of the above inventions, the dehumidifying and cooling transition condition is that the required cooling capacity cannot be realized during operation in the dehumidifying and heating mode.
  • the dehumidifying and cooling transition condition in the above-described invention is that the heat sink by the heat sink in the dehumidifying and heating mode achieves the target heat absorber temperature TEO that is the target temperature of the heat sink. It is characterized by being unable to do so.
  • the vehicle air conditioner according to the invention of claim 10 is the heating that is also required as the dehumidifying heating mode based on the environmental conditions and / or operating conditions during operation in the dehumidifying and cooling mode in the above-described invention. It is characterized in that it is possible to realize the capacity and to achieve the required cooling capacity.
  • the dehumidifying and heating transition condition in the above invention can achieve a target heater temperature TCO that is a target temperature of the radiator by heat radiation by the radiator in the dehumidifying and heating mode.
  • the target heat absorber temperature TEO which is the target temperature of the said heat absorber can be implement
  • the vehicle air conditioner according to a twelfth aspect of the invention is characterized in that, in the invention of the fifth or eleventh aspect, the target heater temperature TCO is a target value of the air temperature on the leeward side of the radiator.
  • a vehicle air conditioner includes an auxiliary heating device for heating the air supplied from the air flow passage to the vehicle interior in each of the above inventions, and the control device is necessary during operation in the dehumidifying and cooling mode. In the case where it is impossible to realize the heating capacity, the auxiliary heating device is caused to generate heat.
  • the control device causes the refrigerant discharged from the compressor to dissipate heat with a radiator, depressurizes the dissipated refrigerant, and then to the outdoor heat exchanger.
  • Heating mode that absorbs heat
  • dehumidifying heating mode dehumidifying and cooling mode
  • cooling that causes the refrigerant discharged from the compressor to dissipate heat in the outdoor heat exchanger, depressurizes the dissipated refrigerant, and then absorbs heat in the heat absorber
  • Each operation mode has a mode, and these operation modes are switched and executed.
  • a compressor for compressing a refrigerant, an air flow passage through which air to be supplied to the vehicle interior flows, and a radiator for heating the air to be radiated from the refrigerant and supplied to the vehicle interior from the air flow passage.
  • a vehicle air conditioner having a dehumidifying and cooling mode in which heat is released by a radiator and an outdoor heat exchanger, the refrigerant that has been radiated is depressurized, and heat is absorbed by a heat absorber.
  • the control unit When operating in the humidifying and heating mode, when the predetermined dehumidifying and cooling transition conditions are met, the mode is shifted to the dehumidifying and cooling mode. When operating in the dehumidifying and cooling mode, when the predetermined dehumidifying and heating conditions are met, the mode is shifted to the dehumidifying and heating mode.
  • the dehumidifying and heating mode when operating in the dehumidifying and cooling mode, if there is a predetermined fluctuation in the operating conditions or operating conditions, the dehumidifying and heating mode is entered regardless of whether or not the dehumidifying and heating condition is satisfied. Therefore, when there is a predetermined change in the operating conditions or operating conditions during operation in the dehumidifying and cooling mode, the dehumidifying heating mode is entered regardless of whether the dehumidifying heating transition condition is satisfied or not. You will be able to try running the mode. This eliminates the inconvenience that the dehumidifying and heating mode cannot be transferred to the dehumidifying and heating mode because the dehumidifying and heating mode is not satisfied even though the dehumidifying and heating mode can be actually executed.
  • the auxiliary heating device generates heat and continues the dehumidifying and cooling mode as in the invention of claim 13 is reduced, and the coefficient of performance is reduced. It is possible to improve (COP) and reduce power consumption.
  • the predetermined fluctuation in the operating conditions or operating conditions during the operation in the dehumidifying and cooling mode can realize the heating capacity required even in the dehumidifying heating mode as in the invention of claim 2 and is necessary. This is a change in operating conditions or operating conditions which suggests that the cooling capacity assumed to be achieved.
  • the set temperature Tset in the vehicle interior as in the invention of claim 3 is raised by a predetermined value or more within a predetermined period due to the predetermined fluctuation of the operating condition during the operation in the dehumidifying and cooling mode. Conceivable.
  • the target blowing temperature TAO which is the target temperature of the air blown into the vehicle interior as in the invention of claim 4 is a predetermined value within a predetermined period.
  • the target heater temperature TCO which is the target temperature of the radiator
  • the invention of claim 6 is otherwise considered.
  • the index indicating the air volume of the air flowing through the air flow passage as described above or there is a predetermined fluctuation in the target heat absorber temperature TEO which is the target temperature of the heat absorber as in the invention of claim 7.
  • TEO the target temperature of the heat absorber as in the invention of claim 7.
  • the dehumidifying and cooling transition condition described above is that the required cooling capacity cannot be realized during operation in the dehumidifying and heating mode as in the invention of claim 8, and more specifically, the claim.
  • the target heat absorber temperature TEO which is the target temperature of the heat absorber cannot be realized by the heat absorption by the heat absorber in the dehumidifying heating mode.
  • the dehumidifying and heating transition condition can realize the heating capacity required even in the dehumidifying and heating mode based on the environmental conditions and / or the operating conditions during operation in the dehumidifying and cooling mode as in the invention of claim 10.
  • the required cooling capacity can be realized. More specifically, as in the invention of claim 11, heat dissipation by the radiator in the dehumidifying heating mode is performed.
  • the target heater temperature TCO that is the target temperature can be realized, and the target heat absorber temperature TEO that is the target temperature of the heat absorber can be realized by the heat absorption by the heat absorber. Further, if the target heater temperature TCO is set to the target value of the air temperature on the lee side of the radiator as in the invention of claim 12, the controllability is improved.
  • the control device causes the refrigerant discharged from the compressor to radiate heat with a radiator, depressurizes the radiated refrigerant, and then absorbs heat with an outdoor heat exchanger.
  • FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to an embodiment of the present invention.
  • a vehicle according to 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 mounted in the vehicle is used as a traveling electric motor (both The vehicle air conditioner 1 of the present invention is also driven by the power of the battery.
  • EV electric vehicle
  • engine internal combustion engine
  • the vehicle air conditioner 1 of the present invention is also driven by the power of the battery.
  • the vehicle air conditioner 1 is a heating mode, a dehumidifying heating mode, a dehumidifying cooling mode, a cooling mode, and an auxiliary mode by a heat pump operation using the refrigerant circuit R in an electric vehicle that cannot be heated by engine waste heat.
  • the vehicle interior is air-conditioned and further has a defrosting mode for defrosting the outdoor heat exchanger 7 described above.
  • the present invention is effective not only for electric vehicles but also for so-called hybrid vehicles that use an engine and an electric motor for traveling, and is also applicable to ordinary vehicles that run on an engine. Needless to say.
  • the vehicle air conditioner 1 performs air conditioning (heating, cooling, dehumidification, and ventilation) in a vehicle interior of an electric vehicle, and includes an electric compressor 2 that compresses refrigerant and vehicle interior air. Is provided in the air flow passage 3 of the HVAC unit 10 through which air is circulated, and the high-temperature and high-pressure refrigerant discharged from the compressor 2 flows in through the refrigerant pipe 13G, and dissipates the refrigerant into the vehicle compartment.
  • an outdoor expansion valve 6 comprising an electric valve (electronic expansion valve) that decompresses and expands the refrigerant during heating, a refrigerant that functions as a radiator that radiates the refrigerant during cooling, and an evaporator that absorbs the refrigerant during heating.
  • An outdoor heat exchanger 7 that exchanges heat with the outside air
  • an indoor expansion valve 8 that is a mechanical expansion valve that decompresses and expands the refrigerant
  • a vehicle interior that is provided in the air flow passage 3 during cooling and dehumidification
  • 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.
  • the indoor expansion valve 8 using a 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 outside air and the refrigerant by forcibly passing outside air through the outdoor heat exchanger 7, so that the outdoor air blower 15 can also be used outdoors even when the vehicle is stopped (that is, the vehicle speed is 0 km / h).
  • the outdoor heat exchanger 7 has a receiver dryer section 14 and a supercooling section 16 in order on the downstream side of the refrigerant, and the refrigerant pipe 13 ⁇ / b> A exiting from the outdoor heat exchanger 7 is opened when the refrigerant flows through the heat absorber 9.
  • the refrigerant pipe 13B on the outlet side of the supercooling unit 16 is connected to the checker valve 18 and the indoor expansion valve 8 in this order via an electromagnetic valve 17 (for cooling) as an on-off valve. It is connected to the inlet side of the heat absorber 9.
  • the receiver dryer part 14 and the supercooling part 16 structurally constitute a part of the outdoor heat exchanger 7.
  • the check valve 18 has a forward direction of the indoor expansion valve 8.
  • the refrigerant pipe 13B between the supercooling section 16 and the check valve 18 is provided in a heat exchange relationship with the refrigerant pipe 13C on the outlet side of the heat absorber 9, and constitutes an internal heat exchanger 19 together.
  • the refrigerant flowing into the indoor expansion valve 8 through the refrigerant pipe 13B is cooled (supercooled) by the low-temperature refrigerant that has exited the heat absorber 9.
  • the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is branched into a refrigerant pipe 13D, and this branched refrigerant pipe 13D is passed through an electromagnetic valve 21 (for heating) as an on-off valve that is opened during heating.
  • the refrigerant pipe 13 ⁇ / b> C is connected to the downstream side of the internal heat exchanger 19.
  • the refrigerant pipe 13 ⁇ / b> C is connected to the accumulator 12, and the accumulator 12 is connected to the refrigerant suction side of the compressor 2.
  • the refrigerant pipe 13E on the outlet side of the radiator 4 is branched into a refrigerant pipe 13J and a refrigerant pipe 13F before the outdoor expansion valve 6 (the refrigerant upstream side), and one of the branched refrigerant pipes 13J is the outdoor expansion valve 6. Is connected to the refrigerant inlet side of the outdoor heat exchanger 7.
  • 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) that is opened and closed during dehumidification.
  • the refrigerant pipe 13B is connected in communication.
  • 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.
  • This is a bypass circuit that bypasses 18.
  • the outdoor expansion valve 6 is connected in parallel with a solenoid valve 20 as an on-off valve for bypass.
  • the air flow passage 3 on the air upstream side of the heat absorber 9 is formed with each of an outside air inlet and an inside air inlet (represented by the inlet 25 in FIG. 1).
  • a suction switching damper 26 for switching the air introduced into the air flow passage 3 between the inside air (inside air circulation) which is air inside the vehicle compartment and the outside air (outside air introduction) which is outside the vehicle compartment.
  • an indoor blower (blower fan) 27 for supplying the introduced inside air or outside air to the air flow passage 3 is provided on the air downstream side of the suction switching damper 26.
  • an auxiliary heater 23 as an auxiliary heating device including a PTC heater (electric heater) is provided in the embodiment. It is possible to heat the air supplied into the passenger compartment.
  • 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 a microcomputer that is an example of a computer including a processor, and these include a CAN (Controller Area Network) and a LIN (Local Interconnect Network). Is connected to a vehicle communication bus 65.
  • the compressor 2 and the auxiliary heater 23 are also connected to the vehicle communication bus 65, and the air conditioning controller 45, the heat pump controller 32, the compressor 2 and the auxiliary heater 23 are configured to transmit and receive data via the vehicle communication bus 65.
  • the air conditioning controller 45 is a host controller that controls the air conditioning of the vehicle interior of the vehicle.
  • the input of the air conditioning controller 45 includes an outside air temperature sensor 33 that detects the outside air temperature Tam of the vehicle, and an air flow path from the suction port 25. 3, an HVAC suction temperature sensor 36 that detects the temperature of the air that is sucked into the heat sink 9 and flows into the heat absorber 9 (suction air temperature Tas), and an inside air temperature sensor that detects the temperature of the air (inside air) in the vehicle interior (inside temperature Tin).
  • the output of the air conditioning controller 45 is connected to an outdoor blower 15, an indoor blower (blower fan) 27, a suction switching damper 26, an air mix damper 28, and an outlet switching damper 31, which are air conditioning controllers. 45.
  • the heat pump controller 32 is a controller that mainly controls the refrigerant circuit R.
  • the input of the heat pump controller 32 includes a discharge temperature sensor 43 that detects a discharge refrigerant temperature Td of the compressor 2 and a suction refrigerant of the compressor 2.
  • a suction pressure sensor 44 that detects the pressure Ps, a suction temperature sensor 55 that detects the suction refrigerant temperature Ts of the compressor 2, and a radiator that detects the refrigerant temperature (radiator inlet temperature TCIin) on the refrigerant inlet side of the radiator 4.
  • a heat sink temperature sensor 48 for detecting the temperature of the heat absorber 9 (the refrigerant temperature of the heat absorber 9: the heat absorber temperature Te).
  • a heat absorber pressure sensor 49 that detects the refrigerant pressure of the heat absorber 9, an auxiliary heater temperature sensor 50 that detects the temperature of the auxiliary heater 23 (auxiliary heater temperature Theat), and the refrigerant temperature (outdoor heat) at the outlet of the outdoor heat exchanger 7.
  • An outdoor heat exchanger temperature sensor 54 for detecting the refrigerant evaporation temperature TXO and the outdoor heat exchanger temperature TXO) of the exchanger 7, and the refrigerant pressure at the outlet of the outdoor heat exchanger 7 (the refrigerant evaporation pressure PXO of the outdoor heat exchanger 7)
  • Each output of the outdoor heat exchanger pressure sensor 56 for detecting the outdoor heat exchanger pressure PXO) is connected.
  • the auxiliary heater temperature sensor 50 may detect the temperature of the air on the leeward side (immediately after) of the auxiliary heater 23, or may detect the temperature of the auxiliary heater 23 itself.
  • the air temperature on the leeward side of 23 is preferable. Therefore, in this embodiment, the auxiliary heater temperature sensor 50 is provided on the leeward side of the auxiliary heater 23 with a slight clearance, and detects the air temperature on the leeward side (immediately after) of the auxiliary heater 23.
  • the auxiliary heater temperature Theat the air temperature on the leeward side of the auxiliary heater 23 is adopted.
  • the output of the heat pump controller 32 includes an electromagnetic valve such as the outdoor expansion valve 6, the electromagnetic valve 22 (for dehumidification), the electromagnetic valve 17 (for cooling), the electromagnetic valve 21 (for heating), and the electromagnetic valve 20 (for bypass).
  • an electromagnetic valve such as the outdoor expansion valve 6, the electromagnetic valve 22 (for dehumidification), the electromagnetic valve 17 (for cooling), the electromagnetic valve 21 (for heating), and the electromagnetic valve 20 (for bypass).
  • the compressor 2 and the auxiliary heater 23 each have a built-in controller, and the controllers of the compressor 2 and the auxiliary heater 23 send and receive data to and from the heat pump controller 32 via the vehicle communication bus 65. Be controlled.
  • the heat pump controller 32 and the air conditioning controller 45 transmit / receive data to / 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.
  • the outside air temperature sensor 33, the discharge pressure sensor 42, the vehicle speed sensor 52, the air flow rate Ga flowing into the air flow passage 3 and flowing through the air flow passage 3 (calculated by the air conditioning controller 45),
  • the air volume ratio SW (calculated by the air conditioning controller 45) by the air mix damper 28 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 are subjected to control by the heat pump controller 32. It is configured.
  • the control device 11 (the air conditioning controller 45 and the heat pump controller 32) performs switching between the air conditioning modes of the heating mode, the dehumidifying and heating mode, the dehumidifying and cooling mode, the cooling mode, and the auxiliary heater single mode.
  • the defrosting mode for defrosting the outdoor heat exchanger 7 is also executed.
  • the heat pump controller 32 When the heating mode is selected by the heat pump controller 32 (auto mode) or the manual air conditioning setting operation (manual mode) to the air conditioning operation unit 53 of the air conditioning controller 45, the heat pump controller 32 opens the electromagnetic valve 21 and the electromagnetic valve 17 The solenoid valve 20 and the solenoid valve 22 are closed. Then, the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 is in a state of adjusting the ratio of the air blown out from the indoor blower 27 to the heat radiator 4 and the auxiliary heater 23. Thereby, 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 passed through the radiator 4, the air in the air flow passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. Deprived, cooled, and condensed into liquid.
  • the refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 through 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 flowing into the outdoor heat exchanger 7 evaporates, and pumps up heat from the outside air that is ventilated by traveling or by the outdoor blower 15 (heat absorption).
  • the refrigerant circuit R becomes a heat pump. Then, the low-temperature refrigerant exiting the outdoor heat exchanger 7 enters the accumulator 12 through the refrigerant pipe 13C through the refrigerant pipe 13A, the refrigerant pipe 13D, and the electromagnetic valve 21, and is separated into gas and liquid there. Repeated circulation inhaled. Since the air heated by the radiator 4 is blown out from the air outlet 29, the vehicle interior is thereby heated.
  • the heat pump controller 32 has a target heater temperature TCO (a heater temperature Thp described later) calculated from a target blowing temperature TAO which is a target temperature of air blown into the vehicle interior (a target value of the temperature of air blown into the vehicle interior).
  • the target radiator pressure PCO is calculated from the target value (target temperature of the radiator 4), and the target radiator pressure PCO and the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator outlet pressure sensor 47 are calculated.
  • the rotation speed of the compressor 2 is controlled based on the temperature of the refrigerant outlet side of the radiator 4 detected by the radiator outlet temperature sensor 46A and the radiator pressure PCI detected by the radiator outlet pressure sensor 47.
  • the valve opening degree of the expansion valve 6 is controlled, and the supercooling degree of the refrigerant at the outlet of the radiator 4 is controlled.
  • the heat pump controller 32 supplements the shortage with the heat generated by the auxiliary heater 23.
  • FIG. 3 shows the refrigerant flow (solid arrow) in the refrigerant circuit R in the dehumidifying heating mode.
  • the heat pump controller 32 opens the solenoid valve 21 and the solenoid valve 22, and the solenoid valve 17 and the solenoid valve 20 are closed. Then, the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 is in a state of adjusting the ratio of the air blown out from the indoor blower 27 to the heat 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 passed through the radiator 4, the air in the air flow passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. Deprived, cooled, and condensed into liquid. After the refrigerant liquefied in the radiator 4 exits the radiator 4, a part of the refrigerant 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 flowing into the outdoor heat exchanger 7 evaporates, and pumps up heat from the outside air that is ventilated by traveling or by the outdoor blower 15 (heat absorption). Then, the low-temperature refrigerant exiting the outdoor heat exchanger 7 enters the accumulator 12 through the refrigerant pipe 13C through the refrigerant pipe 13A, the refrigerant pipe 13D, and the electromagnetic valve 21, and is separated into gas and liquid there. Repeated circulation inhaled. On the other hand, the remaining condensed refrigerant flowing through the refrigerant pipe 13E via the radiator 4 is divided, and the divided refrigerant flows into the refrigerant pipe 13F via the electromagnetic valve 22 and reaches the refrigerant pipe 13B.
  • the refrigerant reaches the indoor expansion valve 8, is decompressed by the indoor expansion valve 8, and then flows into the heat absorber 9 to evaporate.
  • moisture in the air blown out from the indoor blower 27 is condensed and attached to the heat absorber 9 by the heat absorption 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 and joins with the refrigerant from the refrigerant pipe 13D (the refrigerant from the outdoor heat exchanger 7), and then repeats circulation that is sucked into the compressor 2 through the accumulator 12.
  • the heat pump controller 32 controls the number of rotations of the compressor 2 based on the target radiator pressure PCO and the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator outlet pressure sensor 47, and the heat absorber temperature sensor 48.
  • the valve opening degree of the outdoor expansion valve 6 is controlled based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by.
  • the heat pump controller 32 supplements the shortage with the heat generated by the auxiliary heater 23. .
  • the vehicle interior is dehumidified and heated even when the outside air temperature is low.
  • FIG. 4 shows the refrigerant flow (solid arrow) in the refrigerant circuit R in the dehumidifying and cooling mode.
  • the heat pump controller 32 opens the electromagnetic valve 17 and closes the electromagnetic valve 20, the electromagnetic valve 21, and the electromagnetic valve 22.
  • the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 is in a state of adjusting the ratio of the air blown out from the indoor blower 27 to the heat 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 passed through the radiator 4, the air in the air flow passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. It is deprived and cooled, and condensates.
  • the refrigerant exiting the radiator 4 reaches the outdoor expansion valve 6 through the refrigerant pipes 13E and 13J, and flows into the outdoor heat exchanger 7 through the outdoor expansion valve 6 controlled in an open manner.
  • the refrigerant flowing into the outdoor heat exchanger 7 is cooled and condensed by running there or by the outside air ventilated by the outdoor blower 15.
  • the refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B through the refrigerant pipe 13A, the electromagnetic valve 17, the receiver dryer section 14, and the supercooling section 16, and passes through the internal heat exchanger 19 and the check valve 18 to the indoor expansion valve. 8 is reached. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates.
  • the heat pump controller 32 absorbs heat 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 temperature of the heat absorber 9 (target value of the heat absorber temperature Te).
  • the rotation speed of the compressor 2 is controlled so that the radiator 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 outlet pressure sensor 47 and the target radiator pressure Based on the PCO (target value of the radiator pressure PCI), the amount of reheat required by the radiator 4 is controlled by controlling the valve opening degree of the outdoor expansion valve 6 so that the radiator pressure PCI becomes the target radiator pressure PCO. Heating amount).
  • the heat pump controller 32 supplements the shortage with the heat generated by the auxiliary heater 23. To do. Thereby, dehumidifying and cooling are performed without excessively reducing the temperature in the passenger compartment.
  • FIG. 5 shows the refrigerant flow (solid arrow) in the refrigerant circuit R in the cooling mode.
  • the heat pump controller 32 opens the electromagnetic valve 17 and the electromagnetic valve 20, and closes the electromagnetic valve 21 and the electromagnetic valve 22.
  • the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 is in a state of adjusting the ratio of the air blown out from the indoor blower 27 to the heat 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 to the radiator 4, the ratio is small (because of only reheating (reheating) at the time of cooling).
  • the discharged refrigerant reaches the refrigerant pipe 13J through the refrigerant pipe 13E.
  • the refrigerant passes through the solenoid valve 20 and flows into the outdoor heat exchanger 7 as it is, where it is cooled by air or by the outside air ventilated by the outdoor blower 15 and condensed. Liquefaction.
  • the refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B through the refrigerant pipe 13A, the electromagnetic valve 17, the receiver dryer section 14, and the supercooling section 16, and passes through the internal heat exchanger 19 and the check valve 18 to the indoor expansion valve. 8 is reached. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates.
  • the defrosting mode of the outdoor heat exchanger 7 will be described.
  • the heat pump controller 32 executes the defrosting mode of the outdoor heat exchanger 7 as follows.
  • the heat pump controller 32 sets the refrigerant circuit R in the heating mode state of FIG. 1 and opens the valve opening degree of the outdoor expansion valve 6, and the air mix damper 28 includes the radiator 4 and the auxiliary heater 23. No ventilation.
  • the compressor 2 is operated, and the high-temperature refrigerant discharged from the compressor 2 is caused to flow into the outdoor heat exchanger 7 through the radiator 4 and the outdoor expansion valve 6 to melt frost on the outdoor expansion valve 7.
  • the heat pump controller 32 detects that the temperature of the outdoor heat exchanger 7 (outdoor heat exchanger temperature TXO) detected by the outdoor heat exchanger temperature sensor 54 is higher than a predetermined defrosting end temperature (for example, + 3 ° C. or the like).
  • a predetermined defrosting end temperature for example, + 3 ° C. or the like.
  • the heat pump controller 32 of the embodiment stops the compressor 2 and the outdoor blower 15 of the refrigerant circuit R and energizes the auxiliary heater 23 when the overheat frost is generated in the outdoor heat exchanger 7.
  • the auxiliary heater single mode for heating the passenger compartment with only 23 is provided.
  • the heat pump controller 32 determines the auxiliary heater 23 based on the auxiliary heater temperature Theat detected by the auxiliary heater temperature sensor 50 and the target auxiliary heater temperature THO that is the target temperature of the auxiliary heater 23 (target value of the auxiliary heater temperature Theat). Control energization (heat generation).
  • the heat pump controller 32 operates the indoor blower 27, and the air mix damper 28 causes the air in the air flow passage 3 blown out from the indoor blower 27 to pass through the auxiliary heater 23 to adjust the air volume. Since the air heated by the auxiliary heater 23 is blown out into the vehicle interior from the air outlet 29, the vehicle interior is thereby heated. (7) Calculation of each target temperature (target value) / capacity by the heat pump controller 32 Next, calculation of each target temperature (target value) and ability by the heat pump controller 32 will be described with reference to FIG. The heat pump controller 32 calculates the above-described target blowing temperature TAO (target temperature of air blown into the vehicle compartment from the blowout port 29) from the following formula (I).
  • TAO target temperature of air blown into the vehicle compartment from the blowout port 29
  • TAO (Tset ⁇ Tin) ⁇ K + Tbal (f (Tset, SUN, Tam)) .. (I)
  • Tset is the set temperature in the passenger compartment set by the air conditioning operation unit 53
  • Tin is the temperature of the passenger compartment air detected by the inside air temperature sensor 37
  • K is a coefficient
  • Tbal is the set temperature Tset
  • this target blowing temperature TAO is so high that the outside temperature Tam is low, and it falls as the outside temperature Tam rises.
  • the heat pump controller 32 uses the following formula (II) and the formula (III) and the target heater temperature TCO (target value of the heater temperature Thp. Target temperature of the radiator 4) and The target auxiliary heater temperature THO (the target value of the auxiliary heater temperature Theat detected by the auxiliary heater temperature sensor 50. The target temperature of the auxiliary heater 23) is calculated.
  • TCO f (TAO) (II)
  • THO f (TAO) ⁇ ⁇ (III)
  • f in the above formulas (II) and (III) means control restrictions, offsets, etc., but f in formula (III) is different from f in formula (ii). is there.
  • the heat pump controller 32 calculates and estimates the heater temperature Thp described above as the temperature of the radiator 4 using the following formula (IV).
  • the heater temperature Thp may be the air temperature on the leeward side of the radiator 4 or the temperature of the radiator 4 itself, but the air temperature on the leeward side of the radiator 4 is more suitable in consideration of controllability. Therefore, in the embodiment, the air temperature on the leeward side of the radiator 4 is calculated (estimated) using the following formula (IV), and this is set as the heater temperature Thp that is the temperature of the radiator 4.
  • Thp f (PCI, TCIout) (IV)
  • PCI is a radiator pressure detected by the radiator outlet pressure sensor 47
  • TCIout is a radiator outlet temperature detected by the radiator outlet temperature sensor 46B.
  • the target heater temperature TCO is a target value of the air temperature (Thp) on the leeward side of the radiator 4 in the embodiment.
  • the heat pump controller 32 uses the following formula (V), formula (VI), and formula (VII), the target heating capacity TGQ (kW) that is the required heating capacity, and the maximum heating capacity of the radiator 4.
  • An HP heating capacity predicted value Qmax (kW), which is a predicted value, and an HP heating capacity measured value Qhp (kW), which is a heating capacity actually generated by the radiator 4, are calculated.
  • THO is the target auxiliary heater temperature
  • Te is the heat absorber temperature detected by the heat absorber temperature sensor 48
  • Ga is the air volume (m 3 / S)
  • Tam is the outside air temperature detected by the outside air temperature sensor 33
  • NC is the rotational speed of the compressor 2
  • Thp is the heater temperature.
  • the heat pump controller 32 calculates the difference ⁇ Qmax between the target heating capacity TGQ and the HP heating capacity predicted value Qmax and the target heating capacity TGQ and the HP heating capacity measured value Qhp using the following formulas (VIII) and (IX).
  • the difference ⁇ Qhp is calculated.
  • ⁇ Qmax TGQ ⁇ Qmax (VVIII)
  • ⁇ Qhp TGQ ⁇ Qhp (IX)
  • the total heating capacity actually generated by the radiator 4 and the auxiliary heater 23 is the total capacity Qtotal (kW), and the relationship between these respective capacities and differences is shown in FIG.
  • the auxiliary heater 23 is provided in the air flow passage 3 on the leeward side (downstream side of the air) of the radiator 4, the auxiliary heater temperature Heat detected by the auxiliary heater temperature sensor 50 is the heat absorber. 9, the temperature of the air in the air flow passage 3 that has passed through the radiator 4 and the auxiliary heater 23.
  • Operation mode switching control switching control of the operation mode among the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, and the cooling mode by the heat pump controller 32 will be described with reference to FIGS. 7 and 8.
  • the heat pump controller 32 includes an outside air temperature Tam, a target blowing temperature TAO, a heater temperature Thp, a target heater temperature TCO, an auxiliary heater temperature Theat, a target auxiliary heater temperature THO, a heat absorber temperature Te, a target heat absorber temperature TEO, a vehicle interior. Based on parameters such as whether or not there is a dehumidification request, switching between each operation mode of heating mode, dehumidifying heating mode, dehumidifying cooling mode, and cooling mode can be performed according to the environmental conditions and necessity of dehumidification in the passenger compartment. These operation modes are switched to control the temperature of the air blown into the passenger compartment to the target outlet temperature TAO, thereby realizing a comfortable and efficient air conditioning in the passenger compartment.
  • the mode is shifted to the heating mode.
  • the auxiliary heater temperature Heat detected by the auxiliary heater temperature sensor 50 becomes equal to or higher than the target heater temperature TCO (TCO ⁇ Theat), and the auxiliary heater temperature Heat is established. When heating is no longer necessary, the mode is changed to the cooling mode.
  • the auxiliary heater temperature Theat detected by the auxiliary heater temperature sensor 50 becomes lower than the target heater temperature TCO (TCO> Theat), and the auxiliary heater temperature Theat is not established.
  • TCO target heater temperature
  • the auxiliary heater temperature Theat is not established.
  • the dehumidifying and cooling mode is entered.
  • the dehumidifying and cooling transition condition in this case is that the cooling capacity required in the heat absorber 9 cannot be realized during operation in the dehumidifying and heating mode. More specifically, the target heat absorber temperature TEO can no longer be realized by the heat absorption by the heat absorber 9, and in the embodiment, the heat absorber temperature is higher than the target heat absorber temperature TEO + ⁇ (the heat absorber). Temperature Te not established). ⁇ is a predetermined margin.
  • the heat pump controller 32 of the embodiment when the heat absorber temperature Te detected by the heat absorber temperature sensor 48 is higher than the target heat absorber temperature TEO + ⁇ during operation in the dehumidifying heating mode (Te> (TEO + ⁇ )), the dehumidifying cooling is performed. Enter mode.
  • the heat pump controller 32 when operating in this dehumidifying and cooling mode, the heat pump controller 32 causes the auxiliary heater 23 to generate heat when the required heating capacity cannot be realized in a situation where the dehumidifying and heating transition condition described later is not satisfied. Heating assistance (reheating assistance) is performed to achieve the necessary heating capacity and prevent a temperature drop in the passenger compartment.
  • Heating assistance reheating assistance
  • the cooling capacity required for the heat absorber 9 can be realized. More specifically, the target heater temperature TCO, which is the target value of the heater temperature Thp (target temperature of the radiator 4), can be realized by the heat radiation by the radiator 4 in the dehumidifying heating mode, and the heat absorber 9 It is assumed that the target heat absorber temperature TEO can be realized by heat absorption.
  • the target value of the heater temperature Thp (When it is determined that the target heater temperature TCO that is the target temperature of the radiator 4) can be realized and the target heat absorber temperature TEO can be realized by the heat absorption by the heat absorber 9, the dehumidifying heating mode Migrate to
  • the heat pump controller 32 when operating in this dehumidifying and heating mode, performs heating assistance by causing the auxiliary heater 23 to generate heat when the required heating capacity cannot be realized in a situation where dehumidification is required, Achieve the necessary heating capacity to prevent the temperature drop in the passenger compartment.
  • the heating capacity required in the radiator 4 can be realized even in the dehumidifying and heating mode, and the cooling capacity required in the heat absorber 9 can be realized. If not, the dehumidifying and cooling mode cannot be shifted to the dehumidifying and heating mode. Therefore, it has been difficult to shift from the dehumidifying and cooling mode to the dehumidifying and heating mode.
  • the dehumidifying and heating transition conditions are set more severely considering that the refrigerant is excessively squeezed due to variations (individual differences).
  • the heat pump controller 32 in addition to the dehumidifying and heating transition condition, the heat pump controller 32 is provided with a transition condition at the time of fluctuation, and when the transition condition at the time of fluctuation is satisfied during operation in the dehumidifying and cooling mode, the dehumidifying and heating condition is satisfied. The heat pump controller 32 switches the operation mode to the dehumidifying and heating mode regardless of whether or not it is.
  • the transition condition at the time of the change in the present invention is that there is a predetermined change in the operating condition or the driving situation of the vehicle air conditioner 1, and the meaning of the predetermined change is even when the dehumidifying heating mode is entered. These are fluctuations in operating conditions or operating conditions that suggest that the heating capacity required in the radiator 4 can be realized and the cooling capacity required in the heat absorber 9 can be realized.
  • ⁇ Transition conditions during fluctuation (1) in this case, as a specific example of the predetermined variation of the operation condition in the transition condition at the time of the variation, the set temperature Tset in the passenger compartment is raised by the predetermined value T1 or more within the predetermined period t1 during the operation in the dehumidifying and cooling mode. There are cases.
  • the heater temperature Thp can realize the target heater temperature TCO, and the heat absorption This is because there is a high possibility that the heater temperature Te can realize the target heat absorber temperature TEO. Therefore, when the set temperature Tset is rapidly increased during operation in the dehumidifying and cooling mode (for example, within a predetermined period t1 (2 sec: a predetermined short period), the heat pump controller 32 is increased by a predetermined value T1 (3 deg) or more.
  • the dehumidifying and cooling mode is switched to the dehumidifying and heating mode, and the heater temperature Thp is targeted by the heat radiation by the radiator 4.
  • the operation is performed to determine whether the heater temperature TCO can be realized and the heat absorber temperature Te can achieve the target heat absorber temperature TEO by the heat absorption by the heat absorber 9.
  • FIG. 8 shows this state.
  • the change of the set temperature indicates a point in time when the set temperature Tset is increased by a predetermined value T1 or more within the predetermined period t1, and in the embodiment, this is performed twice.
  • the heat absorber temperature Te could not realize the target heat absorber temperature TEO (Te is not established), and thus the dehumidifying and cooling mode is returned.
  • the heat absorber temperature Te can achieve the target heat absorber temperature TEO (Te establishment), and thereafter, the dehumidifying heating mode is continued.
  • the heat pump controller 32 is operating in the dehumidifying and cooling mode and the target blowout temperature TAO has risen by the predetermined value T2 or more within the predetermined period t2, it is determined that the transition condition at the time of variation is satisfied, and the dehumidifying and heating transition condition is satisfied. Even if is not established, the dehumidifying / cooling mode is switched to the dehumidifying / heating mode, the heater temperature Thp can achieve the target heater temperature TCO by the heat radiation by the radiator 4, and the heat absorber temperature Te can be achieved by the heat absorption by the heat absorber 9. It is operated whether the target heat absorber temperature TEO can be realized.
  • the target heater that is the target value of the heater temperature Thp (target temperature of the radiator 4) during operation in the dehumidifying cooling mode
  • the temperature TCO has risen by a predetermined value T3 or more within a predetermined period t3.
  • the predetermined period t3 is also a predetermined short period.
  • the heat absorber temperature TEO can be realized. Therefore, even when the heat pump controller 32 is operating in the dehumidifying and cooling mode and the target heater temperature TCO has risen by the predetermined value T3 or more within the predetermined period t3, it is determined that the transition condition at the time of variation is satisfied, and the dehumidifying and heating transition condition is satisfied. Even if is not established, the dehumidifying / cooling mode is switched to the dehumidifying / heating mode, the heater temperature Thp can achieve the target heater temperature TCO by the heat radiation by the radiator 4, and the heat absorber temperature Te can be achieved by the heat absorption by the heat absorber 9. It is operated whether the target heat absorber temperature TEO can be realized.
  • a predetermined index is used to indicate the air volume Ga of the air flowing through the air flow passage 3 during operation in the dehumidifying and cooling mode.
  • As an index indicating the air volume Ga for example, there is a blower voltage BLV of the indoor blower 27.
  • the heater temperature Thp can achieve the target heater temperature TCO, and the heat sink temperature This is because Te may be able to achieve the target heat absorber temperature TEO.
  • the heat pump controller 32 determines that the variation transition condition is satisfied. Even if the dehumidifying and heating transition condition is not satisfied, the dehumidifying and cooling mode is switched to the dehumidifying and heating mode, the heater temperature Thp can achieve the target heater temperature TCO by the heat radiation by the radiator 4, and the heat absorption by the heat absorber 9 It is tried to operate whether or not the heat absorber temperature Te can achieve the target heat absorber temperature TEO.
  • ⁇ Transition conditions when changing (5) another specific example of the predetermined fluctuation of the operating condition in the transition condition at the time of fluctuation is a target value of the heat absorber temperature Te (target temperature of the heat absorber 9) during operation in the dehumidifying and cooling mode.
  • a target value of the heat absorber temperature Te target temperature of the heat absorber 9 during operation in the dehumidifying and cooling mode.
  • TEO target temperature of the heat absorber 9
  • the heat pump controller 32 operates in the dehumidifying and cooling mode and the target heat absorber temperature TEO, which is the target value of the heat absorber temperature Te (the target temperature of the heat absorber 4), has a predetermined fluctuation, Even if the dehumidifying and heating transition condition is not satisfied, it is determined that the dehumidifying and cooling mode is switched to the dehumidifying and heating mode, the heater temperature Thp can realize the target heater temperature TCO by the heat radiation by the radiator 4, and Then, whether or not the heat absorber temperature Te can achieve the target heat absorber temperature TEO by the heat absorption by the heat absorber 9 is tried.
  • the heat pump controller 32 when the heat pump controller 32 is operating in the dehumidifying and heating mode, when the predetermined dehumidifying and cooling transition condition is satisfied, the heat pump controller 32 shifts to the dehumidifying and cooling mode, and when operating in the dehumidifying and cooling mode, the predetermined dehumidifying and heating transition condition is satisfied. If the operating condition or operating condition has a predetermined change during operation in the dehumidifying and cooling mode, and it is determined that the changing condition at the time of change is satisfied.
  • the dehumidifying and dehumidifying modes are operated when there are predetermined fluctuations in the operating conditions and operating conditions during the operation in the dehumidifying and cooling modes. Regardless of the establishment / non-establishment of the heating transition condition, the dehumidifying / heating mode can be entered and the dehumidifying / heating mode can be executed. That is, according to the present invention, the dehumidifying and heating mode is not actually established, but the inconvenience that the dehumidifying and cooling mode cannot be shifted to the dehumidifying and heating mode is eliminated.
  • the possibility that the dehumidifying and heating mode is executed can be further expanded.
  • the possibility that the auxiliary heater 23 generates heat and continues in the dehumidifying and cooling mode as described above is reduced, so that the coefficient of performance (COP) can be improved and the power consumption can be reduced.
  • the target heater temperature TCO is set as the target value of the heater temperature Thp that is the air temperature on the leeward side of the radiator 4, so that the controllability is good.
  • the heat pump controller 32 has a heating mode, a dehumidifying and heating mode, a dehumidifying and cooling mode, and a cooling mode, and the vehicle air conditioning is performed by switching between these operating modes as in the embodiment.
  • This is very suitable for the device 1.
  • the auxiliary heating device is not limited to the auxiliary heater 23 shown in the embodiment, and a heat medium circulation circuit that heats the air in the air flow passage 3 by circulating the heat medium heated by the heater, or an engine In the case of a vehicle provided, a heater core that circulates radiator water heated by an engine may be used.
  • the configuration and numerical values of the refrigerant circuit R described in the above embodiment are not limited thereto, and it goes without saying that the refrigerant circuit R can be changed without departing from the gist of the present invention.
  • the heater temperature Thp is set as the air temperature on the leeward side of the radiator 4 and is estimated
  • the target heater temperature TCO is also set as the target value of the heater temperature Thp. If there is no problem in the control, for example, the temperature of the radiator 4 itself may be the heater temperature Thp, and the target heater temperature TCO may be the target value of the temperature Thp of the radiator 4 itself.

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)
PCT/JP2018/047131 2018-01-31 2018-12-14 車両用空気調和装置 WO2019150832A1 (ja)

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Citations (3)

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Publication number Priority date Publication date Assignee Title
JPH10264646A (ja) * 1997-03-21 1998-10-06 Denso Corp 車両用空気調和装置
WO2017146264A1 (ja) * 2016-02-26 2017-08-31 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
WO2017146269A1 (ja) * 2016-02-26 2017-08-31 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

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Publication number Priority date Publication date Assignee Title
JP6073651B2 (ja) * 2012-11-09 2017-02-01 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
JP5999637B2 (ja) * 2012-11-09 2016-09-28 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
JP6125312B2 (ja) * 2013-04-26 2017-05-10 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
JP6174414B2 (ja) * 2013-08-07 2017-08-02 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
JP6241595B2 (ja) * 2013-08-23 2017-12-06 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
JP6247993B2 (ja) * 2014-04-18 2017-12-13 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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10264646A (ja) * 1997-03-21 1998-10-06 Denso Corp 車両用空気調和装置
WO2017146264A1 (ja) * 2016-02-26 2017-08-31 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
WO2017146269A1 (ja) * 2016-02-26 2017-08-31 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

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