JP7233953B2 - Vehicle air conditioner - Google Patents

Description

TECHNICAL FIELD The present invention relates to a heat pump type air conditioner for air conditioning the interior of a vehicle.

Due to the emergence of environmental problems in recent years, hybrid vehicles and electric vehicles have come into widespread use. Then, as an air conditioner that can be applied to such a vehicle, a compressor that compresses and discharges refrigerant, a radiator that is provided inside the passenger compartment and dissipates heat from the refrigerant, and a radiator that is provided inside the passenger compartment. Equipped with a heat absorber that absorbs heat from the refrigerant and an outdoor heat exchanger that is provided on the exterior side of the vehicle to release or absorb heat from the refrigerant. A heating mode in which heat is absorbed in the outdoor heat exchanger, a dehumidifying heating mode in which the refrigerant discharged from the compressor is radiated in the radiator, and the refrigerant radiated in the radiator is absorbed in the heat absorber and the outdoor heat exchanger, and from the compressor A cooling mode in which the discharged refrigerant releases heat in the outdoor heat exchanger and absorbs heat in the heat absorber, and a dehumidifying cooling mode in which the refrigerant discharged from the compressor releases heat in the radiator and outdoor heat exchanger and absorbs heat in the heat absorber. A device has been developed in which the switching is possible.

In this case, an outdoor expansion valve is provided at the inlet of the outdoor heat exchanger, and the refrigerant flowing into the outdoor heat exchanger is decompressed by the outdoor expansion valve in the heating mode and dehumidifying heating mode described above. In the dehumidification and heating mode, the refrigerant exiting the radiator is split, one of which is decompressed by the indoor expansion valve and flowed into the heat absorber so that the heat absorber absorbs heat, and the other is decompressed by the outdoor expansion valve. The refrigerant is made to absorb heat by flowing into an outdoor heat exchanger (see, for example, Patent Document 1).

JP 2014-94673 A

In the dehumidifying heating mode as described above, when the temperature of the heat absorber drops significantly, conventionally, the rotation speed of the compressor is reduced to prevent the heat absorber from freezing. However, when the rotation speed of the compressor is lowered, the high pressure is lowered, so that the heat radiation in the radiator is lowered and the target blowout temperature cannot be achieved.

On the other hand, if the number of rotations of the compressor is maintained to achieve the target blowout temperature, the heat absorber freezes, resulting in a problem of a decrease in the amount of air blown into the passenger compartment.

SUMMARY OF THE INVENTION The present invention has been made to solve such conventional technical problems. The object is to provide a harmonizing device.

A vehicle air conditioner of the present invention comprises a compressor for compressing a refrigerant, a radiator for radiating heat from the refrigerant to heat the air supplied to the vehicle interior, and a heat absorbing system for the refrigerant to supply the air to the vehicle interior. A heat absorber for cooling, an outdoor heat exchanger provided outside the passenger compartment, an outdoor expansion valve for reducing the pressure of the refrigerant flowing into the outdoor heat exchanger, and a pressure reducing valve for reducing the pressure of the refrigerant flowing into the heat absorber. An indoor expansion valve and a control device are provided, and the control device causes at least the refrigerant discharged from the compressor to radiate heat with a radiator, the heat-dissipated refrigerant is divided, one of the refrigerants is decompressed by the indoor expansion valve, and the heat is absorbed. After the other is decompressed by the outdoor expansion valve, the dehumidifying heating mode is executed in which the heat is absorbed by the outdoor heat exchanger. The valve opening degree of the valve is expanded, and when the outdoor expansion valve reaches the set maximum opening degree and the temperature of the heat absorber becomes lower than a predetermined value, the indoor expansion valve is fully closed.

A vehicle air conditioner according to a second aspect of the invention is characterized in that in the above invention, the control device controls the rotation speed of the compressor based on an index capable of grasping the temperature of the air blown into the passenger compartment. and

In the vehicle air conditioner of the invention of claim 3 , in each of the above inventions , when the outdoor expansion valve reaches a set maximum opening, the control device reduces the valve opening of the indoor expansion valve and increases the temperature of the heat absorber. is lower than a predetermined value, the indoor expansion valve is fully closed.

In the vehicle air conditioner of the invention of claim 4 , in each of the above inventions, the control device sets the temperature of the heat absorber to a predetermined value or a predetermined value higher than the predetermined value after the indoor expansion valve is fully closed. When exceeding, the indoor expansion valve is opened to a predetermined valve opening degree.

In the vehicle air conditioner of the invention of claim 5 , in each of the above inventions, the control device causes the refrigerant discharged from the compressor to radiate heat through the expansion valve and the outdoor heat exchanger, and the heat-dissipated refrigerant is passed through the indoor expansion valve. After reducing the pressure, the dehumidifying cooling mode is executed to absorb heat with a heat absorber, and the maximum value for control of the valve opening of the indoor expansion valve in the dehumidifying heating mode is the control of the valve opening of the indoor expansion valve in the dehumidifying cooling mode. It is characterized by being set smaller than the above maximum value.

According to the present invention, a compressor for compressing the refrigerant, a radiator for releasing heat from the refrigerant to heat the air supplied to the vehicle interior, and a heat sink for absorbing heat from the refrigerant to cool the air to be supplied to the vehicle interior. A heat absorber, an outdoor heat exchanger provided outside the vehicle, an outdoor expansion valve for reducing the pressure of the refrigerant flowing into the outdoor heat exchanger, and an indoor expansion valve for reducing the pressure of the refrigerant flowing into the heat absorber. , a control device that causes at least the refrigerant discharged from the compressor to radiate heat with a radiator, divides the heat-dissipated refrigerant, decompresses one of the refrigerants with an indoor expansion valve, and absorbs heat with a heat absorber. In a vehicle air conditioner that executes a dehumidifying heating mode in which the other is decompressed by an outdoor expansion valve and then heat is absorbed by an outdoor heat exchanger, when the temperature of the heat absorber becomes lower than a predetermined value, Since the indoor expansion valve is fully closed, it is possible to stop the refrigerant from flowing into the heat absorber without lowering the rotation speed of the compressor, thereby avoiding the inconvenience of the heat absorber freezing.

As a result, the inconvenience of a decrease in the amount of air blown into the passenger compartment can be eliminated, and in particular, as in the invention of claim 2, the compressor can be operated based on an index capable of grasping the temperature of the air blown into the passenger compartment. When controlling the number of revolutions, it is possible to smoothly achieve the target blowout temperature.

In particular, the control device expands the valve opening degree of the outdoor expansion valve as the temperature of the heat absorber decreases, the outdoor expansion valve reaches the set maximum opening degree, and the temperature of the heat absorber falls below a predetermined value. In this case, the indoor expansion valve is fully closed, so as long as the flow rate of refrigerant to the heat absorber can be controlled by the control of the outdoor expansion valve, the temperature of the heat absorber can be controlled by the outdoor expansion valve. The indoor expansion valve can stop the flow of refrigerant into the heat absorber when the amount of refrigerant that can be reduced by the valve to the heat absorber reaches its limit.

Further, when the outdoor expansion valve reaches the set maximum opening, the control device reduces the valve opening of the indoor expansion valve, and when the temperature of the heat absorber becomes lower than a predetermined value. If the indoor expansion valve is fully closed, it is not necessary to fully close the indoor expansion valve when the temperature of the heat absorber does not fall below a predetermined value by reducing the opening degree of the indoor expansion valve. disappear. As a result, it becomes possible to maintain the dehumidifying ability in the passenger compartment while preventing the heat absorber from freezing.

Further, when the temperature of the heat absorber exceeds a predetermined value or a predetermined value higher than the predetermined value after the control device fully closes the indoor expansion valve as in the invention of claim 4 , the indoor expansion valve is closed. If the valve is opened at a predetermined opening, after the indoor expansion valve is fully closed, the temperature of the heat absorber rises and the supply of refrigerant to the heat absorber resumes without hindrance, and the dehumidification of the passenger compartment begins. be able to

Here, as in the invention of claim 5 , the control device causes the refrigerant discharged from the compressor to radiate heat with the expansion valve and the outdoor heat exchanger, and after the heat-dissipated refrigerant is decompressed with the indoor expansion valve, the heat absorber When executing the dehumidifying cooling mode in which heat is absorbed by the dehumidifying cooling mode, the maximum controllable value of the valve opening of the indoor expansion valve in the dehumidifying heating mode is set smaller than the controllable maximum valve opening of the indoor expansion valve in the dehumidifying cooling mode. If set, in the dehumidifying and heating mode, a two-stage decompression action by the outdoor expansion valve and the indoor expansion valve will occur while suppressing the temperature drop of the heat absorber in the dehumidifying and heating mode. By controlling the outdoor expansion valve while it is slightly open, dehumidification and cooling of the passenger compartment can be achieved without hindrance.

1 is a configuration diagram of a vehicle air conditioner according to an embodiment to which the present invention is applied; FIG. FIG. 2 is a block diagram of an electric circuit of the control device of the vehicle air conditioner of FIG. 1; FIG. 3 is a configuration diagram of a vehicle air conditioner for explaining a heating mode by a heat pump controller of the control device of FIG. 2; FIG. 3 is a configuration diagram of the vehicle air conditioner for explaining a dehumidifying heating mode by the heat pump controller of the control device in FIG. 2 ; FIG. 3 is a configuration diagram of a vehicle air conditioner for explaining a dehumidifying cooling mode and a cooling mode by a heat pump controller of the control device of FIG. 2; 3 is a configuration diagram of a vehicle air conditioner for explaining an air conditioning (priority)+battery cooling mode and a battery cooling (priority)+air conditioning mode by a heat pump controller of the control device of FIG. 2; FIG. FIG. 3 is a configuration diagram of the vehicle air conditioner for explaining a battery cooling (single) mode by the heat pump controller of the control device in FIG. 2 ; FIG. 3 is a control block diagram relating to compressor control of a heat pump controller of the control device of FIG. 2 ; 3 is a block diagram illustrating control of an outdoor expansion valve in a dehumidifying heating mode by a heat pump controller of the control device of FIG. 2; FIG. 3 is a block diagram illustrating control of indoor expansion valves in a dehumidifying heating mode by a heat pump controller of the control device of FIG. 2; FIG.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described in detail based on the drawings. FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to one 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 supplied to a driving motor (electric motor). , not shown), 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. .

That is, the vehicle air conditioner 1 of the embodiment provides a heating mode, a dehumidifying heating mode, a dehumidifying cooling mode, a cooling mode, and an air conditioning (preferentially )+battery cooling mode, battery cooling (priority)+air conditioning mode, and battery cooling (single) mode are switched and executed to control the air conditioning in the passenger compartment and the temperature of the battery 55.

The vehicle is not limited to an electric vehicle, and the present invention is also effective for a so-called hybrid vehicle that shares an engine and a driving motor. In addition, the vehicle to which the vehicle air conditioner 1 of the embodiment is applied can charge the battery 55 from an external charger (rapid charger or normal charger). Furthermore, although the battery 55, the motor for running, the inverter controlling them, etc. are mounted on the vehicle and subject to temperature control, the battery 55 will be described as an example in the following embodiment.

A vehicle air conditioner 1 of the embodiment performs air conditioning (heating, cooling, dehumidification, and ventilation) in a vehicle interior of an electric vehicle, and includes an electric compressor 2 that compresses a refrigerant and The high-temperature and high-pressure refrigerant discharged from the compressor 2 is provided in the air circulation passage 3 of the HVAC unit 10 through which air is ventilated and circulated. A radiator 4 that releases heat), an outdoor expansion valve 6 that consists of an electric valve (electronic expansion valve) that decompresses and expands the refrigerant during heating, functions as a radiator that releases the refrigerant during cooling, and absorbs heat ( An indoor expansion valve 8 consisting of an outdoor heat exchanger 7 that exchanges heat between the refrigerant and the outside air to function as an evaporator that absorbs heat into the refrigerant, and an electric valve (electronic expansion valve) that decompresses and expands the refrigerant. A heat absorber 9 as an evaporator provided in the air flow passage 3 to absorb heat (evaporate) into the refrigerant from inside and outside the vehicle interior during cooling and dehumidification, and an accumulator 12 and the like are sequentially connected by a refrigerant pipe 13 to form a refrigerant circuit. R is constructed.

The outdoor expansion valve 6 decompresses and expands the refrigerant coming out of the radiator 4 and flowing into the outdoor heat exchanger 7, and can also be fully closed. Also, the indoor expansion valve 8 decompresses and expands the refrigerant flowing into the heat absorber 9, and can also be fully closed.

The outdoor heat exchanger 7 is provided with an outdoor blower 15 . The outdoor blower 15 forcibly blows outside air through the outdoor heat exchanger 7 to exchange heat between the outside air and the refrigerant. The heat exchanger 7 is configured to be ventilated with outside air.

A refrigerant pipe 13A on the refrigerant outlet side of the outdoor heat exchanger 7 is connected to a refrigerant pipe 13B to which a solenoid valve 17 (for cooling) is connected as an on-off valve that is opened when the refrigerant flows to the heat absorber 9. This refrigerant pipe 13B is connected to the refrigerant inlet side of the heat absorber 9 via a check valve 18 and an indoor expansion valve 8 in this order. The direction of the indoor expansion valve 8 is the forward direction of the check valve 18 .

In addition, the refrigerant pipe 13A coming out of 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 an on-off valve that is opened during heating. It is communicated with the refrigerant pipe 13C on the refrigerant outlet side of the heat absorber 9 . The refrigerant pipe 13C is connected to the inlet side of the accumulator 12 via a check valve 35, and the outlet side of the accumulator 12 is connected to the refrigerant pipe 13K on the refrigerant suction side of the compressor 2. The direction of the check valve 35 is the forward direction of the accumulator 12, and the refrigerant pipe 13D is connected to the refrigerant pipe 13C on the upstream side of the check valve 35. As shown in FIG.

Furthermore, 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 pipe 13J and the refrigerant pipe 13F before the outdoor expansion valve 6 (refrigerant upstream side). One branched refrigerant pipe 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 downstream of the check valve 18 and upstream of the indoor expansion valve 8 via an electromagnetic valve 22 (for dehumidification) serving as an on-off valve that is opened during dehumidification. It is communicatively connected to the located refrigerant pipe 13B.

As a result, 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 18 is a bypass circuit.

Further, the air flow passage 3 on the air upstream side of the heat absorber 9 is formed with an outside air suction port and an inside air suction port (represented by a suction port 25 in FIG. 1). 25 is provided with an intake switching damper 26 for switching the air introduced into the air flow passage 3 between inside air (inside air circulation), which is the air inside the vehicle compartment, and outside air (outside air introduction), which is the air outside the vehicle compartment. Furthermore, an indoor air blower (blower fan) 27 for supplying the introduced inside air and outside air to the air flow passage 3 is provided on the air downstream side of the suction switching damper 26 .

Further, in the air flow passage 3 on the leeward side (air downstream side) of the radiator 4, an auxiliary heater 23 is provided as an auxiliary heating device comprising a PTC heater (electric heater) in the embodiment. It is possible to heat the air supplied to the vehicle interior. Furthermore, in the air flow passage 3 on the air upstream side of the radiator 4, the air (inside air or outside air) in the air flow passage 3 after flowing into the air flow passage 3 and passing through the heat absorber 9 is radiated. An air mix damper 28 is provided for adjusting the ratio of ventilation to the vessel 4 and the auxiliary heater 23 .

Furthermore, the air flow passage 3 on the air downstream side of the radiator 4 has outlets for FOOT, VENT, and DEF (representatively indicated by outlet 29 in FIG. 1). The air outlet 29 is provided with an air outlet switching damper 31 for switching and controlling air blowing from each of the air outlets.

Further, the vehicle air conditioner 1 includes a device temperature adjustment device 61 for circulating a heat medium in the battery 55 (a temperature controlled object) to adjust the temperature of the battery 55 . The device temperature adjustment device 61 of the embodiment includes a circulation pump 62 as a circulation device for circulating a heat medium in the battery 55, a refrigerant-heat medium heat exchanger 64 as a heat exchanger for temperature control target, and a heating A heating medium heater 63 is provided as a device, and these and the battery 55 are annularly connected by a heating medium pipe 66 .

In the embodiment, the inlet of the heat medium heater 63 is connected to the discharge side of the circulation pump 62, and the outlet of the heat medium heater 63 is connected to the inlet of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64. It is The outlet of the heat medium flow path 64 A of the refrigerant-heat medium heat exchanger 64 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 .

As the heat medium used in the device temperature adjustment device 61, for example, water, refrigerant such as HFO-1234yf, liquid such as coolant, and gas such as air can be employed. In addition, water is used as a heat medium in the embodiment. The heat medium heater 63 is composed of an electric heater such as a PTC heater. Further, the battery 55 is surrounded by a jacket structure that allows a heat medium to flow in a heat exchange relationship with the battery 55 .

Then, when the circulation pump 62 is operated, the heat medium discharged from the circulation pump 62 reaches the heat medium heater 63, and when the heat medium heater 63 is generating heat, the heat medium is heated there, and then the refrigerant - into the heat medium flow path 64A of the heat medium heat exchanger 64; The heat medium exiting the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 reaches the battery 55 and exchanges heat with the battery 55 there. 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 .

On the other hand, one end of a branch pipe 67 as a branch circuit is connected to the refrigerant downstream side of the electromagnetic valve 22 of the refrigerant pipe 13F of the refrigerant circuit R. This branch pipe 67 is provided with an auxiliary expansion valve 68 which is an electric valve (electronic expansion valve) in this embodiment. 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 can also be fully closed.

The other end of the branch pipe 67 is connected to the refrigerant channel 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 channel 64B. The other end is connected to the refrigerant pipe 13</b>C on the refrigerant downstream side of the check valve 35 and on the refrigerant upstream side of the accumulator 12 . The auxiliary expansion valve 68, the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and the like also constitute a part of the refrigerant circuit R and also a part of the device temperature adjustment device 61 at the same time.

When the auxiliary expansion valve 68 is open, the refrigerant (part or all of the refrigerant) coming out of the outdoor heat exchanger 7 flows into the branch pipe 67, and after being decompressed by the auxiliary expansion valve 68, the refrigerant-heat medium heat It flows into the refrigerant channel 64B of the exchanger 64 and evaporates there. After absorbing heat from the heat medium flowing through the heat medium flow path 64A in the course of flowing through the refrigerant flow path 64B, the refrigerant passes through the refrigerant pipe 71, the refrigerant pipe 13C, the accumulator 12, and is sucked into the compressor 2 from the refrigerant pipe 13K.

Next, 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 having a processor. is connected to a vehicle communication bus 65 that constitutes the In addition, the compressor 2 and the auxiliary heater 23, the circulation pump 62 and the heat medium 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 exchanger are connected to the vehicle communication bus 65. The medium heater 63 is configured to transmit and receive data via the vehicle communication bus 65 .

Further, the vehicle communication bus 65 includes a vehicle controller 72 (ECU) that controls the overall vehicle including running, a battery controller (BMS: Battery Management System) 73 that controls charging and discharging of the battery 55, and a GPS navigation device 74. is connected. The vehicle controller 72, the battery controller 73, and the GPS navigation device 74 are also composed of a microcomputer, which is an example of a computer having a processor. Information (data) is transmitted/received to/from these vehicle controller 72, battery controller 73, and GPS navigation device 74 via.

The air-conditioning controller 45 is a high-order controller that controls air-conditioning in the vehicle interior. A sensor 34, an HVAC intake temperature sensor 36 that detects the temperature of air that is sucked into the air flow passage 3 from the suction port 25 and flows into the heat absorber 9, and an inside air temperature that detects the air temperature (inside air temperature Tin) in the vehicle compartment. A sensor 37, an inside air humidity sensor 38 that detects the humidity of the air in the passenger compartment, an indoor CO ₂ concentration sensor 39 that detects the carbon dioxide concentration in the passenger compartment, and a blowout temperature that detects the temperature of the air blown out into the passenger compartment. A sensor 41, a solar radiation sensor 51 of, for example, a photosensor type for detecting the amount of solar radiation in the vehicle interior, a vehicle speed sensor 52 for detecting the moving speed of the vehicle (vehicle speed VSP), and settings in the vehicle interior. An air-conditioning operation unit 53 is connected for performing air-conditioning setting operations in the passenger compartment such as temperature and operation mode switching, and for displaying information. Incidentally, reference numeral 53A in FIG.

The output of the air conditioning controller 45 is connected to the outdoor fan 15, the indoor fan (blower fan) 27, the suction switching damper 26, the air mix damper 28, and the outlet switching damper 31. controlled by

The heat pump controller 32 is a controller that mainly controls the refrigerant circuit R, and the input of the heat pump controller 32 is a heat dissipation controller that detects the refrigerant inlet temperature Tcxin of the radiator 4 (also the discharge refrigerant temperature of the compressor 2). a radiator outlet temperature sensor 44 for detecting a refrigerant outlet temperature Tci of the radiator 4; a suction temperature sensor 46 for detecting a refrigerant suction temperature Ts of the compressor 2; A radiator pressure sensor 47 that detects the refrigerant pressure (pressure of the radiator 4: radiator pressure Pci) and a heat absorber temperature sensor that detects the temperature of the heat absorber 9 (refrigerant temperature of the heat absorber 9: heat absorber temperature Te) 48, an outdoor heat exchanger temperature sensor 49 that detects the refrigerant temperature at the outlet of the outdoor heat exchanger 7 (refrigerant evaporation temperature of the outdoor heat exchanger 7: outdoor heat exchanger temperature TXO), and the temperature of the auxiliary heater 23 The outputs of auxiliary heater temperature sensors 50A (driver's seat side) and 50B (passenger's seat side) are connected.

The outputs of the heat pump controller 32 include the outdoor expansion valve 6, the solenoid valve 22 (for dehumidification), the solenoid valve 17 (for cooling), the solenoid valve 21 (for heating), the indoor expansion valve 8, and the auxiliary expansion valve 68. 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 heater 63 each incorporate a controller. 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 .

Note that the circulation pump 62 and the heat medium heater 63 that constitute the equipment temperature adjustment device 61 may be controlled by the battery controller 73 . The battery controller 73 also includes a heat medium temperature sensor 76 for detecting the temperature of the heat medium (heat medium temperature Tw) on the inlet side of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 of the device temperature adjustment device 61. and the output of a battery temperature sensor 77 that detects the temperature of the battery 55 (the temperature of the battery 55 itself: battery temperature Tcell) is connected. In the embodiment, the remaining amount (accumulated amount) of the battery 55, information on charging of the battery 55 (information indicating that charging is in progress, charging completion time, remaining charging time, etc.), heat medium temperature Tw, battery temperature Tcell, battery The amount of heat generated by 55 (calculated by the battery controller 73 from the amount of electricity supplied) and the like are 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 on the charge completion time and the remaining charge time when charging the battery 55 is information supplied from an external charger such as a quick charger. Further, the vehicle controller 72 transmits the output Mpower of the running motor to the heat pump controller 32 and the air conditioning controller 45 .

The heat pump controller 32 and the air conditioning controller 45 exchange data with 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. , in this embodiment, the outside air temperature sensor 33, the outside air humidity sensor 34, the HVAC intake temperature sensor 36, the inside air temperature sensor 37, the inside air humidity sensor 38, the indoor CO ₂ concentration sensor 39, the outlet temperature sensor 41, the solar radiation sensor 51, the vehicle speed Sensor 52, air volume Ga of air flowing into the air circulation passage 3 and circulating in the air circulation passage 3 (calculated by the air conditioning controller 45), air volume ratio SW by the air mix damper 28 (calculated by the air conditioning controller 45), indoor blower 27 voltage (BLV), information from the battery controller 73 described above, 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 It is configured to be controlled by the controller 32 .

Data (information) regarding control of the refrigerant circuit R is also transmitted from the heat pump controller 32 to the air conditioning controller 45 via the vehicle communication bus 65 . The air volume ratio SW by the air mix damper 28 described above is calculated by the air conditioning controller 45 within the range of 0≦SW≦1. When SW=1, the air mix damper 28 causes all of the air that has passed through the heat absorber 9 to flow through the radiator 4 and the auxiliary heater 23 .

Next, the operation of the vehicle air conditioner 1 of the embodiment having the above configuration will be described. In this embodiment, the control device 11 (the air conditioning controller 45 and the heat pump controller 32) operates in a heating mode, a dehumidifying heating mode, a dehumidifying cooling mode, a cooling mode, an air conditioning (priority) + battery cooling mode, and a battery cooling mode. Each battery cooling operation of (priority) + air conditioning mode and battery cooling (single) mode is switched and executed.

Of these, the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, the cooling mode, and the air conditioning (priority) + battery cooling mode each air conditioning operation does not charge the battery 55 in the embodiment, and the ignition of the vehicle (IGN) is turned on and the air conditioning switch of the air conditioning operation unit 53 is turned on. However, during remote operation (pre-air conditioning, etc.), it is executed even when the ignition is off. Further, even when the battery 55 is being charged, it is executed when there is no battery cooling request and the air conditioning switch is turned on.

On the other hand, each battery cooling operation of the battery cooling (priority) + air conditioning mode and the battery cooling (single) mode is executed when the battery 55 is being charged by connecting a quick charger (external power supply) plug, for example. It is a thing. However, the battery cooling (single) mode is executed when the air conditioning switch is off and there is a battery cooling request (during running at a high outside temperature, etc.) other than when the battery 55 is being charged.

Further, in the embodiment, the heat pump controller 32 operates the circulation pump 62 of the equipment temperature adjustment 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 the dashed lines in FIGS. Furthermore, the heat pump controller 32 of the embodiment also executes a battery heating mode in which the battery 55 is heated by causing the heat medium heater 63 of the equipment temperature adjustment device 61 to generate heat.

(1) Heating Mode First, the heating mode will be described with reference to FIG. The control of each device is executed by the cooperation of the heat pump controller 32 and the air conditioning controller 45, but in the following description, the heat pump controller 32 is the main control unit, and the description will be simplified. FIG. 3 shows how the refrigerant flows (solid line arrows) in the refrigerant circuit R in the heating mode. When the heating mode is selected by the heat pump controller 32 (auto mode) or by 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 solenoid valve 21 and the solenoid valve 17 , the solenoid valve 22 is closed. Further, the outdoor expansion valve 6 is opened, the indoor expansion valve 8 and the auxiliary expansion valve 68 are fully closed, the compressor 2 and the fans 15 and 27 are operated, and the air mix damper 28 is the indoor fan The ratio of the air blown from 27 to the radiator 4 and the auxiliary heater 23 is adjusted.

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Since the air in the air circulation passage 3 is ventilated to the radiator 4, the air in the air circulation passage 3 exchanges heat with the high-temperature refrigerant in the radiator 4 and is heated. On the other hand, the refrigerant in the radiator 4 is cooled by the heat taken by the air, and is condensed and liquefied.

After leaving the radiator 4, the refrigerant liquefied in the radiator 4 reaches the outdoor expansion valve 6 through the refrigerant pipes 13E and 13J. The refrigerant that has flowed 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 draws up heat from the outside air blown by the outdoor blower 15 while the vehicle is running (heat absorption). That is, the refrigerant circuit R becomes a heat pump. The low-temperature refrigerant leaving the outdoor heat exchanger 7 passes through the refrigerant pipes 13A, 13D, and the electromagnetic valve 21, reaches the refrigerant pipe 13C, further passes through the refrigerant pipe 13C, enters the accumulator 12, and is separated into gas and liquid there. After that, the gas refrigerant is sucked into the compressor 2 from the refrigerant pipe 13K, and the circulation is repeated. Since the air heated by the radiator 4 is blown out from the outlet 29, the vehicle interior is heated.

The heat pump controller 32 determines a target heater temperature TCO (heater temperature The target radiator pressure PCO is calculated from the target value of Thp), and based on this target radiator pressure PCO and the radiator pressure Pci (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47 While controlling the rotational speed NC, the valve opening degree of the outdoor expansion valve 6 is adjusted 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. control and control the degree of subcooling of the refrigerant at the outlet of the radiator 4 .

Although the radiator pressure Pci is an index for grasping the temperature of the air blown into the passenger compartment in the present invention, the temperature of the air blown into the passenger compartment detected by the outlet temperature sensor 41 may also be used as this indicator. good.

Moreover, when the heating capacity (heating capacity) of the radiator 4 is insufficient for the required heating capacity, the heat pump controller 32 compensates for this deficiency with the heat generated by the auxiliary heater 23 . As a result, the vehicle interior can be heated without any problem even when the outside air temperature is low.

(2) Dehumidifying Heating Mode Next, the dehumidifying heating mode will be described with reference to FIG. FIG. 4 shows how the refrigerant flows (solid line arrows) in the refrigerant circuit R in the dehumidifying and heating mode. In the dehumidifying heating mode, the heat pump controller 32 opens the solenoid valves 21 and 22 and closes the solenoid valve 17 . Also, the outdoor expansion valve 6 and the indoor expansion valve 8 are opened, and the auxiliary expansion valve 68 is fully closed. Then, the compressor 2 and the fans 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor fan 27 to the radiator 4 and the auxiliary heater 23 .

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Since the air in the air circulation passage 3 is ventilated to the radiator 4, the air in the air circulation passage 3 exchanges heat with the high-temperature refrigerant in the radiator 4 and is heated. On the other hand, the refrigerant in the radiator 4 is cooled by the heat taken by the air, and is condensed and liquefied.

After the refrigerant liquefied in the radiator 4 exits the radiator 4 , a part of it enters the refrigerant pipe 13 J through the refrigerant pipe 13 E and reaches the outdoor expansion valve 6 . The refrigerant that has flowed 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 draws up heat from the outside air blown by the outdoor blower 15 while the vehicle is running (heat absorption). Then, the low-temperature refrigerant leaving the outdoor heat exchanger 7 reaches the refrigerant pipe 13C through the refrigerant pipe 13A, the refrigerant pipe 13D, and the electromagnetic valve 21, enters the accumulator 12 through the refrigerant pipe 13C, and is separated into gas and liquid there. After that, the gas refrigerant is repeatedly sucked into the compressor 2 through the refrigerant pipe 13K.

On the other hand, the remainder of the condensed refrigerant flowing through the refrigerant pipe 13E through the radiator 4 is branched, and the branched refrigerant flows into the refrigerant pipe 13F, passes through the electromagnetic valve 22, and reaches the refrigerant pipe 13B. Next, the refrigerant reaches the indoor expansion valve 8, and after being decompressed by the indoor expansion valve 8, flows into the heat absorber 9 and evaporates. At this time, moisture in the air blown out from the indoor fan 27 condenses 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 exits the refrigerant pipe 13C, joins the refrigerant from the refrigerant pipe 13D (refrigerant from the outdoor heat exchanger 7), passes through the accumulator 12, and is sucked into the compressor 2 from the refrigerant pipe 13K. repeat the cycle. The air dehumidified by the heat absorber 9 is reheated in the course of passing through the radiator 4 and the auxiliary heater 23 (if it is generating heat), so dehumidifying and heating the vehicle interior is performed.

In the embodiment, the heat pump controller 32 controls the rotation of the compressor 2 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) detected by the radiator pressure sensor 47. Control number NC. Further, the valve opening degrees of the outdoor expansion valve 6 and the indoor expansion valve 8 are controlled based on the heat absorber temperature Te. Control of the outdoor expansion valve 6 and the indoor expansion valve 8 in the dehumidification heating mode will be described in detail later.

Also in this dehumidification heating mode, if the heating capacity (heating capacity) of the radiator 4 is insufficient for the required heating capacity, the heat pump controller 32 compensates for this deficiency with the heat generated by the auxiliary heater 23. . As a result, even when the outside air temperature is low, the interior of the vehicle can be dehumidified and heated without any trouble.

(3) Dehumidifying Cooling Mode Next, the dehumidifying cooling mode will be described with reference to FIG. FIG. 5 shows how the refrigerant flows (solid line arrows) in the refrigerant circuit R in the dehumidifying cooling mode. In the dehumidifying cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 21 and 22 . Also, the outdoor expansion valve 6 and the indoor expansion valve 8 are opened, and the auxiliary expansion valve 68 is fully closed. Then, the compressor 2 and the fans 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor fan 27 to the radiator 4 and the auxiliary heater 23 .

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Since the air in the air circulation passage 3 is ventilated to the radiator 4, the air in the air circulation passage 3 exchanges heat with the high-temperature refrigerant in the radiator 4 and is heated. On the other hand, the refrigerant in the radiator 4 loses heat to the air, is cooled, and is condensed and liquefied.

The refrigerant exiting the radiator 4 passes through the refrigerant pipes 13E and 13J, reaches the outdoor expansion valve 6, and passes through the outdoor expansion valve 6, which is controlled to be slightly more open than in the heating mode or the dehumidifying heating mode (area with a large valve opening). It flows into the outdoor heat exchanger 7 . The refrigerant that has flowed into the outdoor heat exchanger 7 is air-cooled there by traveling or by outside air blown by the outdoor blower 15, and condenses. The refrigerant exiting the outdoor heat exchanger 7 passes through the refrigerant pipe 13A, enters the refrigerant pipe 13B, passes through the solenoid valve 17 and the check valve 18 in order, and reaches the indoor expansion valve 8. After the refrigerant is decompressed by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Moisture in the air blown out from the indoor fan 27 condenses and adheres to the heat absorber 9 due to the heat absorbing action at this time, and the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C, and is sucked into the compressor 2 through the refrigerant pipe 13K. The air cooled by the heat absorber 9 and dehumidified is reheated (heating capacity is lower than during dehumidifying heating) in the process of passing through the radiator 4 and the auxiliary heater 23 (if it is generating heat). Thus, dehumidification and cooling of the passenger compartment is performed.

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 NC of the compressor 2 is controlled so that the device 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 pressure Based on PCO (target value of radiator pressure Pci), the amount of reheat required by radiator 4 (reheat heating amount).

Also in this dehumidification cooling mode, if the heating capacity (reheating capacity) of the radiator 4 is insufficient for the required heating capacity, the heat pump controller 32 compensates for this deficiency with the heat generated by the auxiliary heater 23. do. As a result, dehumidification and cooling is performed without excessively lowering the temperature in the passenger compartment.

(4) Cooling Mode Next, the cooling mode will be described. The way the refrigerant flows in this cooling mode is the same as in FIG. That is, even in this cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 21 and 22 . Also, the outdoor expansion valve 6 is fully opened, the indoor expansion valve 8 is opened, and the auxiliary expansion valve 68 is fully closed. Then, the compressor 2 and the fans 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor fan 27 to the radiator 4 and the auxiliary heater 23 . Incidentally, the auxiliary heater 23 is not energized.

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Although the air in the air flow passage 3 is ventilated to the radiator 4, the ratio is small (because it is only reheated (reheated) during cooling). The discharged refrigerant reaches the refrigerant pipe 13J through the refrigerant pipe 13E. The refrigerant passes through the fully opened outdoor expansion valve 6 as it is and flows into the outdoor heat exchanger 7, where it is air-cooled by traveling or by the outside air blown by the outdoor blower 15, and condensed and liquefied.

The refrigerant exiting the outdoor heat exchanger 7 passes through the refrigerant pipe 13A, enters the refrigerant pipe 13B, passes through the solenoid valve 17 and the check valve 18 in order, and reaches the indoor expansion valve 8. After the refrigerant is decompressed by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Due to the heat absorption action at this time, the air blown out from the indoor fan 27 and exchanging heat with the heat absorber 9 is cooled.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C, and is sucked into the compressor 2 through the refrigerant pipe 13K. The air cooled by the heat absorber 9 is blown into the passenger compartment through the outlet 29, thereby cooling the passenger compartment. In this cooling mode, the heat pump controller 32 controls the rotation speed NC of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 .

(5) Air Conditioning (Priority) + Battery Cooling Mode Next, the air conditioning (priority) + battery cooling mode will be described with reference to FIG. FIG. 6 shows how the refrigerant flows (solid line arrows) in the refrigerant circuit R in the air conditioning (priority) + battery cooling mode. In the air conditioning (priority) + battery cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 21 and 22 . Also, the outdoor expansion valve is fully opened, and the indoor expansion valve 8 and the auxiliary expansion valve 68 are opened.

Then, the compressor 2 and the fans 15 and 27 are operated, and the air mix damper 28 adjusts the ratio of the air blown from the indoor fan 27 to the radiator 4 and the auxiliary heater 23 . Note that the auxiliary heater 23 is not energized in this operation mode. Also, the heating medium heater 63 is not energized.

As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 . Although the air in the air flow passage 3 is ventilated to the radiator 4, the ratio is small (because it is only reheated (reheated) during cooling). The discharged refrigerant reaches the refrigerant pipe 13J through the refrigerant pipe 13E. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant directly flows into the outdoor heat exchanger 7, where it is cooled by running or by the outside air blown by the outdoor blower 15, and condensed and liquefied.

The refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B through the refrigerant pipe 13A, passes through the electromagnetic valve 17 and the check valve 18, and is split. . The refrigerant that has flowed into the indoor expansion valve 8 is decompressed there, and then flows into the heat absorber 9 to evaporate. Due to the endothermic action at this time, the air blown out from the indoor fan 27 and exchanging heat with the heat absorber 9 is cooled.

The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C, and is sucked into the compressor 2 through the refrigerant pipe 13K. The air cooled by the heat absorber 9 is blown into the passenger compartment through the outlet 29, thereby cooling the passenger compartment.

On the other hand, the rest of the refrigerant that has passed through the check valve 18 is split and flows into the branch pipe 67 and reaches the auxiliary expansion valve 68 . After the refrigerant is depressurized here, it flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 and evaporates there. At this time, it exerts an endothermic action. Refrigerant evaporated in the refrigerant flow path 64B repeats circulation by passing through the refrigerant pipe 71, the refrigerant pipe 13C and the accumulator 12 in order and being sucked into the compressor 2 from the refrigerant pipe 13K (indicated by solid arrows in FIG. 6).

On the other hand, since the circulation pump 62 is in operation, the heat medium discharged from the circulation pump 62 passes through the heat medium heater 64 and flows through the heat medium pipe 66 to the heat medium flow of the refrigerant-heat medium heat exchanger 64. It reaches the passage 64A, where it exchanges heat with the refrigerant that evaporates in the refrigerant passage 64B, absorbs heat, and cools the heat medium. The heat medium exiting the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 reaches the battery 55 and exchanges heat therewith. As a result, the battery 55 is cooled, and the heat medium after cooling the battery 55 repeats the circulation of being sucked into the circulation pump 62 (indicated by the dashed arrow in FIG. 6).

In this air conditioning (priority)+battery cooling mode, the heat pump controller 32 keeps the indoor expansion valve 8 open, and based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48, The rotation speed NC of the compressor 2 is controlled. In addition, in the embodiment, the opening and closing of the auxiliary expansion valve 68 is controlled 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). Note that the heat medium temperature Tw is employed as an index indicating the temperature of the battery 55, which is subject to temperature control in the embodiment (same below).

In this case, the heat pump controller 32 sets the upper limit value TUL and the lower limit value TLL with a predetermined temperature difference above and below a predetermined target heat medium temperature TWO as a target value of the heat medium temperature Tw, for example. Then, when the heat medium temperature Tw increases due to heat generation of the battery 55 or the like from the state where the auxiliary expansion valve 68 is closed and rises to the upper limit value TUL (exceeds the upper limit value TUL, or becomes equal to or higher than the upper limit value TUL). (same below), the auxiliary expansion valve 68 is opened. As a result, the refrigerant flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, evaporates, and cools the heat medium flowing through the heat medium flow path 64A. be done.

After that, when the heat medium temperature Tw drops to the lower limit TLL (below the lower limit TLL or below the lower limit TLL; hereinafter the same), the auxiliary expansion valve 68 is opened. Thereafter, such opening and closing of the auxiliary expansion valve 68 is repeated to control the heat medium temperature Tw to the target heat medium temperature TWO and cool the battery 55 while prioritizing the cooling of the passenger compartment.

(6) Switching of Air-Conditioning Operation The heat pump controller 32 calculates the aforementioned target blowout temperature TAO from the following equation (I). This target blowout temperature TAO is a target value for the temperature of the air blown out from the blowout port 29 into the vehicle interior.
TAO=(Tset−Tin)×K+Tbal(f(Tset, SUN, Tam))
... (I)
Here, Tset is the set temperature in the vehicle interior set by the air conditioning operation unit 53, Tin is the temperature of the interior air detected by the inside air temperature sensor 37, K is a coefficient, and Tbal is the set temperature Tset and the solar radiation sensor 51 detects. SUN and the outside air temperature Tam detected by the outside air temperature sensor 33 . In general, the lower the outside air temperature Tam is, the higher the target blowing temperature TAO is, and the higher the outside air temperature Tam is, the lower the target blowing temperature TAO is.

Then, the heat pump controller 32 selects one of the above-described air conditioning operations based on the outside air temperature Tam detected by the outside air temperature sensor 33 and the target air temperature TAO at startup. In addition, after startup, the operating conditions such as the outside air temperature Tam, the target blowout temperature TAO, the heat medium temperature Tw and the battery temperature Tcell, the environmental conditions, changes in the setting conditions, and the battery cooling request (mode shift request) from the battery controller 73 , selects and switches each air conditioning operation.

(7) Battery Cooling (Priority) + Air Conditioning Mode Next, the operation during charging of the battery 55 will be described. For example, when the charging plug of a quick charger (external power supply) 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, 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 the battery cooling (priority) + air conditioning mode. The flow of refrigerant 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.

However, in this battery cooling (priority) + air conditioning mode, in the embodiment, the heat pump controller 32 keeps the auxiliary expansion valve 68 open, and the heat medium temperature sensor 76 (transmitted from the battery controller 73) detects The rotational speed NC of the compressor 2 is controlled based on the heat medium temperature Tw. Further, in the embodiment, the indoor expansion valve 8 is controlled to open/close based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 .

In this case, the heat pump controller 32 sets the upper limit value TeUL and the lower limit value TeLL with a predetermined temperature difference above and below a predetermined target heat absorber temperature TEO as the target value of the heat absorber temperature Te. Then, when the heat absorber temperature Te increases from the state where the indoor expansion valve 8 is fully closed and rises to the upper limit TeUL (when it exceeds the upper limit TeUL, or when it becomes equal to or higher than the upper limit TeUL. Hereinafter, same), the indoor expansion valve 8 is opened. As a result, the refrigerant flows into the heat absorber 9 and evaporates, cooling the air flowing through the air flow passage 3 .

After that, when the heat absorber temperature Te drops to the lower limit TeLL (below the lower limit TeLL or below TeLL; the same applies hereinafter), the indoor expansion valve 8 is fully closed. Thereafter, such opening and closing of the indoor expansion valve 8 is repeated to control the heat absorber temperature Te to the target heat absorber temperature TEO while giving priority to cooling the battery 55, thereby cooling the passenger compartment.

(8) Battery cooling (single) mode Next, regardless of whether the ignition is ON or OFF, the charging plug of the quick charger is connected with the air conditioning switch of the air conditioning operation unit 53 turned off, and the battery 55 is cooled. When being charged, the heat pump controller 32 executes the battery cooling (alone) mode if there is a battery cooling request. However, it is executed when the air conditioning switch is OFF and there is a battery cooling request (during running at high outside temperature, etc.) other than when the battery 55 is being charged. FIG. 7 shows how the refrigerant flows (solid line arrows) in the refrigerant circuit R in this battery cooling (single) mode. In the battery cooling (single) mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 21 and 22 . Also, the auxiliary expansion valve 68 is opened and the indoor expansion valve 8 is fully closed.

Then, the compressor 2 and the outdoor fan 15 are operated. The indoor blower 27 is not operated, and the auxiliary heater 23 is not energized. In this operation mode, the heating medium heater 63 is also not energized.

As a result, 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 only passes through here, and the refrigerant exiting the radiator 4 reaches the refrigerant pipe 13J through the refrigerant pipe 13E. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant directly flows into the outdoor heat exchanger 7, where it is cooled by the outside air blown by the outdoor blower 15 and condensed and liquefied.

The refrigerant exiting the outdoor heat exchanger 7 passes through the refrigerant pipe 13A and enters the refrigerant pipe 13B. After the refrigerant is depressurized here, it flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 and evaporates there. At this time, it exerts an endothermic action. The refrigerant evaporated in the refrigerant flow path 64B repeats the circulation of being 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 (indicated by solid arrows in FIG. 7).

On the other hand, since the circulation pump 62 is in operation, the heat medium discharged from the circulation pump 62 passes through the heat medium heater 63 and flows through the heat medium pipe 66 to the heat medium flow of the refrigerant-heat medium heat exchanger 64. It reaches the path 64A, where heat is absorbed by the refrigerant that evaporates in the refrigerant flow path 64B, and the heat medium becomes cooled. The heat medium exiting the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 reaches the battery 55 and exchanges heat therewith. As a result, the battery 55 is cooled, and the heat medium after cooling the battery 55 repeats the circulation of being sucked into the circulation pump 62 (indicated by the dashed arrow in FIG. 7).

Also in this battery cooling (single) mode, the heat pump controller 32 cools the battery 55 by controlling the rotation speed NC of the compressor 2 based on the heat medium temperature Tw detected by the heat medium temperature sensor 76 .

(9) Battery Heating Mode Further, the heat pump controller 32 executes the battery heating mode when the air conditioning operation is being performed or the battery 55 is being charged. In this battery heating mode, the heat pump controller 32 operates the circulation pump 62 and energizes the heat medium heater 63 . The auxiliary expansion valve 68 is fully closed.

As a result, the heat medium discharged from the circulation pump 62 reaches the heat medium heater 63 through the heat medium pipe 66 . At this time, since the heat medium heater 63 is generating heat, the heat medium is heated by the heat medium heater 63 and the temperature rises, then reaches the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64, It passes through and reaches the battery 55 and exchanges heat with the battery 55 . As a result, the battery 55 is heated, and the heat medium after heating the battery 55 is sucked into the circulation pump 62 to repeat circulation.

In this battery heating mode, the heat pump controller 32 controls the energization of the heat medium heater 63 based on the heat medium temperature Tw detected by the heat medium temperature sensor 76, thereby increasing the heat medium temperature Tw to a predetermined target heat medium temperature. Adjust to TWO and heat the battery 55 .

(10) Control of the compressor 2 in the heating mode and the dehumidifying heating mode In the heating mode and the dehumidifying heating mode, the heat pump controller 32 controls the target rotation speed of the compressor 2 based on the radiator pressure Pci according to the control block diagram of FIG. (Compressor target rotation speed) TGNCh is calculated. FIG. 8 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 F/F (feedforward) manipulated variable calculator 78 of the heat pump controller 32 calculates the outside air temperature Tam obtained from the outside air temperature sensor 33, the blower voltage BLV of the indoor blower 27, and SW=(TAO−Te)/(Thp−Te). ) obtained by the air mix damper 28, the target supercooling degree TGSC which is the target value of the supercooling degree SC of the refrigerant at the outlet of the radiator 4, and the target heater temperature Thp which is the target value of the heater temperature Thp Based on the temperature TCO and the target radiator pressure PCO, which is the target value of the pressure of the radiator 4, the F/F operation amount TGNChff of the compressor target rotation speed is calculated.

The heater temperature Thp is the air temperature (estimated value) on the leeward side of the radiator 4. 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. Further, 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 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. Further, the F/B (feedback) manipulated variable calculation section 81 calculates the F/B manipulated variable TGNChfb of the compressor target rotation speed by PID calculation or PI calculation based on the target radiator pressure PCO and the radiator pressure Pci. Then, the F/F manipulated variable TGNChff calculated by the F/F manipulated variable calculator 78 and the F/B manipulated variable TGNChfb calculated by the F/B manipulated variable calculator 81 are added by the adder 82 to obtain TGNCh00 as the limit setter. 83.

In the limit setting unit 83, the lower limit rotation speed ECNpdLimLo and the upper limit rotation speed ECNpdLimHi for control are limited to TGNCh0, and then through the compressor OFF control unit 84, it is determined as the compressor target rotation speed TGNCh. In the normal mode, the heat pump controller 32 controls the operation (rotational speed NC) of the compressor 2 based on the compressor target rotational speed TGNCh calculated based on the radiator pressure Pci.

In the compressor OFF control unit 84, the compressor target rotation speed TGNCh becomes the above-described lower limit rotation speed ECNpdLimLo, and the radiator pressure Pci is set to be above or below the target radiator pressure PCO. of the upper limit value PUL (state of exceeding the upper limit value PUL, or state of exceeding the upper limit value PUL; hereinafter the same) continues for a predetermined time th1, the compressor 2 is stopped and compression Enter the ON-OFF mode for ON-OFF control of the machine 2.

In the ON-OFF mode of the compressor 2, when the radiator pressure Pci drops to the lower limit PLL (below the lower limit PLL or below the lower limit PLL; hereinafter the same), the compressor 2 is started to operate with the compressor target rotation speed TGNCh set to the lower limit rotation speed ECNpdLimLo, and when the radiator pressure Pci rises to the upper limit value PUL in this state, the compressor 2 is stopped again. That is, the operation (ON) and stop (OFF) of the compressor 2 at the lower limit rotation speed ECNpdLimLo are repeated. Then, after the radiator pressure Pci has decreased to the lower limit value PUL and the compressor 2 has been started, when the state in which the radiator pressure Pci does not exceed the lower limit value PUL continues for a predetermined time th2, the ON-OFF mode of the compressor 2 and return to normal mode.

(11) Control of the outdoor expansion valve 6 and the indoor expansion valve 8 in the dehumidifying and heating mode Next, referring to FIGS. 9 and 10, the heat pump controller 32 controls the outdoor expansion valve 6 and the indoor expansion valve 8 in the dehumidifying and heating mode. An example of is explained. In the dehumidification heating mode, the heat pump controller 32 performs compression 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) detected by the radiator pressure sensor 47 as described above. The rotation speed NC of the machine 2 is controlled ( FIG. 8 ), the opening degree of the outdoor expansion valve 6 is controlled based on the heat absorber temperature Te, and the opening degree of the outdoor expansion valve 6 and the opening degree of the indoor expansion valve 8 are controlled. The valve opening degree is controlled based on the heat absorber temperature Te.

(11-1) Control of Outdoor Expansion Valve 6 in Dehumidifying and Heating Mode First, an example of control of the outdoor expansion valve 6 in the dehumidifying and heating mode by the heat pump controller 32 will be described with reference to FIG. FIG. 9 shows the transition of the valve opening degree of the outdoor expansion valve 6 in the dehumidifying heating mode. The heat pump controller 32 changes the opening degree of the outdoor expansion valve 6 in three steps based on the change in the heat absorber temperature Te detected by the heat absorber temperature sensor 48 in the embodiment. First, when the heat absorber temperature Te becomes lower than the target heat absorber temperature TEO-A from the fully closed state of the outdoor expansion valve 6, the outdoor expansion valve 6 is opened, and the valve opening degree is set to a predetermined valve opening degree 1. . Note that A is a predetermined positive value. Further, the valve opening degree 1 is a predetermined opening degree that is smaller than the set maximum opening degree described later.

Further, when the heat absorber temperature Te further decreases and becomes lower than the target heat absorber temperature TEO-B with the valve opening degree of the outdoor expansion valve 6 set to 1, the valve opening degree of the outdoor expansion valve 6 is the set maximum opening. This set maximum opening is the maximum controllable value of the outdoor expansion valve 6 set in the dehumidifying and heating mode. In addition, the aforementioned B has a relationship of A<B. That is, the heat pump controller 32 increases the opening degree of the outdoor expansion valve 6 as the heat absorber temperature Te decreases below the target heat absorber temperature TEO.

Since the amount of refrigerant diverted to the indoor expansion valve 8 decreases as the opening degree of the outdoor expansion valve 6 increases, the amount of refrigerant flowing into the heat absorber 9 decreases. Then, when the heat absorber temperature Te rises and becomes higher than the target heat absorber temperature TEO+C while the valve opening degree of the outdoor expansion valve 6 is at the set maximum opening degree, the heat pump controller 32 sets the valve opening degree of the outdoor expansion valve 6 to is reduced to the valve opening degree 1 described above. Note that C is also a predetermined positive value.

In addition, when the heat absorber temperature Te further increases and becomes higher than the target heat absorber temperature TEO+D with the valve opening degree of the outdoor expansion valve 6 set to 1, the outdoor expansion valve 6 is fully closed. Incidentally, D is in a relationship of C<D. That is, the heat pump controller 32 reduces the valve opening degree of the outdoor expansion valve 6 as the heat absorber temperature Te rises from the target heat absorber temperature TEO, so the amount of refrigerant diverted to the indoor expansion valve 8 increases. As a result, the amount of refrigerant flowing into the heat absorber 9 also increases.

In this manner, the heat pump controller 32 basically adjusts the valve opening degree of the outdoor expansion valve 6 in the dehumidifying and heating mode to control the heat absorber temperature Te to the vicinity of the target heat absorber temperature TEO. This is called normal control of the outdoor expansion valve 6 .

(11-2) Control of Indoor Expansion Valve 8 in Dehumidifying and Heating Mode Next, an embodiment of control of the indoor expansion valve 8 by the heat pump controller 32 in the dehumidifying and heating mode will be described with reference to FIG. FIG. 10 shows transition of the valve opening degree of the indoor expansion valve 8 in the dehumidifying heating mode. The heat pump controller 32 executes the normal control state when the valve opening degree of the outdoor expansion valve 6 is not the set maximum opening degree described above, and opens and closes when the valve opening degree of the outdoor expansion valve 6 reaches the set maximum opening degree. Move to the control state.

That is, in the normal control state, the heat pump controller 32 sets the valve opening degree of the indoor expansion valve 8 to a predetermined valve opening degree of two. This valve opening degree 2 is the maximum control value of the indoor expansion valve 8 in the dehumidifying and heating mode (set maximum opening degree of the indoor expansion valve 8 in the dehumidifying and heating mode). The maximum control value of the indoor expansion valve 8 in the dehumidifying heating mode is set smaller than the control maximum value of the indoor expansion valve 8 in the dehumidifying cooling mode. The reason for this is that the outdoor expansion valve 6 and the indoor expansion valve 8 produce a two-step decompression action in the dehumidifying cooling mode. By setting the maximum value for the control of the indoor expansion valve 8 as in the embodiment, the temperature drop of the heat absorber 9 is suppressed in the dehumidifying heating mode, and the dehumidifying cooling mode is more open than the dehumidifying heating mode. By controlling the expansion valve 6, dehumidification and cooling of the passenger compartment can be realized without any trouble.

In this normal control state, when the valve opening degree of the outdoor expansion valve 6 reaches the set maximum opening degree, the heat pump controller 32 shifts to the opening/closing control state. When shifting to this open/close control state, the heat pump controller 32 first reduces the valve opening degree of the indoor expansion valve 8 to a predetermined valve opening degree of 3 . This valve opening degree 3 is a predetermined opening degree smaller than the valve opening degree 2 described above. That is, when the heat pump controller 32 can no longer control the heat absorber temperature Te with the valve opening degree of the outdoor expansion valve 6 (because the valve opening degree of the outdoor expansion valve 6 cannot be increased any more), the open/close control state , the valve opening degree of the indoor expansion valve 8 is reduced to valve opening degree 3. In this open/close control state, the heat pump controller 32 fixes the outdoor expansion valve 6 to the set maximum opening.

In this open/close control state, the heat pump controller 32 switches and controls the indoor expansion valve 8 between the valve opening degree 3 and fully closed based on the change in the heat absorber temperature Te detected by the heat absorber temperature sensor 48 . That is, even if the outdoor expansion valve 6 reaches the set maximum opening degree and the valve opening degree of the indoor expansion valve 8 is reduced to the valve opening degree 3, the heat absorber temperature Te further decreases and becomes lower than the predetermined value t1. The controller 32 fully closes the indoor expansion valve 8 . As a result, the refrigerant no longer flows into the heat absorber 9, the heat absorber temperature Te is prevented from decreasing, and the heat absorber 9 is prevented from freezing. The predetermined value t1 described above is a predetermined low value equal to or higher than the freezing point (zero degrees).

When the temperature of the air blown into the passenger compartment (outflow temperature) changes when the indoor expansion valve 8 is fully closed, the heat pump controller 32 adjusts the temperature based on the target radiator pressure PCO and the radiator pressure Pci as described above. By controlling the rotation speed of the compressor 2, the blowout temperature is controlled to a target value in response to the change in the blowout temperature.

Then, after the indoor expansion valve 8 is fully closed, when the heat absorber temperature Te rises and exceeds another predetermined value t2 higher than the predetermined value t1, the heat pump controller 32 opens the indoor expansion valve 8, and the valve The degree of opening is assumed to be the aforementioned degree of valve opening 3 (predetermined degree of valve opening). Alternatively, the indoor expansion valve 8 may be opened when the heat absorber temperature Te exceeds the predetermined value t1. As a result, the refrigerant flows into the heat absorber 9, so that the dehumidification of the passenger compartment is resumed.

After that, when the heat absorber temperature Te drops again and becomes lower than the predetermined value t1, the heat pump controller 32 fully closes the indoor expansion valve 8 again. In such an opening/closing control state, when a predetermined return condition is satisfied, the heat pump controller 32 returns to the above-described normal control state. The return condition is, for example, that the heat absorber temperature Te has risen to a temperature higher than the predetermined value t2, or that a predetermined time has elapsed in addition to that.

As described in detail above, the heat pump controller 32 constituting the control device 11 fully closes the indoor expansion valve 8 when the heat absorber temperature Te becomes lower than the predetermined value t1. It is possible to stop the refrigerant from flowing into the heat absorber 9 without lowering the NC, thereby avoiding the inconvenience of the heat absorber 9 freezing.

As a result, the problem of a decrease in the amount of air blown into the passenger compartment is eliminated, and as in the embodiment, compression is performed on the basis of the radiator pressure Pci (an index for grasping the temperature of the air blown into the passenger compartment). When controlling the rotational speed NC of the machine 2, it becomes possible to smoothly achieve the target blowout temperature.

In this case, in the embodiment, the heat pump controller 32 expands the valve opening degree of the outdoor expansion valve 6 as the heat absorber temperature Te decreases, and the outdoor expansion valve 6 reaches the set maximum opening degree, and the heat absorber temperature Te becomes lower than the predetermined value t1, the indoor expansion valve 8 is fully closed. When the outdoor expansion valve 6 reaches the limit of reducing the flow rate of the refrigerant to the heat absorber 9 in response to the decrease in the heat absorber temperature Te, the indoor expansion valve 8 stops the inflow of the refrigerant to the heat absorber 9. be able to

In particular, in the embodiment, when the outdoor expansion valve 6 reaches the set maximum opening degree, the heat pump controller 32 reduces the valve opening degree of the indoor expansion valve 8 from the valve opening degree 2 to the valve opening degree 3, and reduces the heat absorber temperature. When Te becomes lower than the predetermined value t1, the indoor expansion valve 8 is fully closed. If it is no longer necessary, the indoor expansion valve 8 need not be fully closed. As a result, it becomes possible to maintain the ability to dehumidify the interior of the vehicle while preventing the heat absorber 9 from freezing.

Further, in the embodiment, after the heat pump controller 32 fully closes the indoor expansion valve 8, when the heat absorber temperature Te exceeds a predetermined value t1 or a higher predetermined value t2, the indoor expansion valve 8 is closed to a predetermined value. Since the valve opening is set to 3, after the indoor expansion valve 8 is fully closed, the heat absorber temperature Te rises, so the refrigerant supply to the heat absorber 9 is restarted without any trouble, and the vehicle interior is dehumidified. will be able to start

The configuration and numerical values of the refrigerant circuit R described in the embodiment, and the transition (transition) conditions regarding the control of the outdoor expansion valve 6 and the indoor expansion valve 8 are not limited to them, and are within the scope of the present invention. Needless to say, it can be changed by Further, in the embodiments, the present invention has been described with the vehicle air conditioner 1 having operation modes such as heating mode, dehumidifying heating mode, dehumidifying cooling mode, cooling mode, air conditioning (priority) + battery cooling mode, etc., but is limited to this. In addition, the present invention is also effective for a vehicle air conditioner capable of executing a dehumidifying heating mode and a dehumidifying cooling mode, for example.

1 Vehicle Air Conditioning Device 2 Compressor 3 Air Flow Path 4 Radiator 6 Outdoor Expansion Valve 7 Outdoor Heat Exchanger 8 Indoor Expansion Valve 9 Heat Absorber 11 Control Device 32 Heat Pump Controller 45 Air Conditioning Controller R Refrigerant Circuit

Claims (5)

a compressor that compresses a refrigerant;
a radiator for radiating heat from the refrigerant to heat the air supplied to the vehicle interior;
a heat absorber for absorbing heat from a refrigerant to cool the air supplied to the vehicle interior;
an outdoor heat exchanger provided outside the vehicle;
an outdoor expansion valve for reducing the pressure of the refrigerant flowing into the outdoor heat exchanger;
an indoor expansion valve for decompressing the refrigerant flowing into the heat absorber;
with a control device,
The controller at least:
The refrigerant discharged from the compressor is dissipated by the radiator, the dissipated refrigerant is divided, one is decompressed by the indoor expansion valve, the heat is absorbed by the heat absorber, and the other is absorbed by the outdoor expansion valve. After reducing the pressure by
The control device expands the valve opening degree of the outdoor expansion valve as the temperature of the heat absorber decreases, reaches a set maximum opening degree, and increases the temperature of the heat absorber above a predetermined value. An air conditioner for a vehicle, wherein the indoor expansion valve is fully closed when the air conditioner becomes low. 2. The air conditioner for a vehicle according to claim 1, wherein the control device controls the rotation speed of the compressor based on an index for grasping the temperature of the air blown into the vehicle interior. . The control device reduces the valve opening degree of the indoor expansion valve when the outdoor expansion valve reaches a set maximum opening degree, and reduces the indoor expansion valve when the temperature of the heat absorber becomes lower than the predetermined value. 3. The vehicle air conditioner according to claim 1, wherein the valve is fully closed. After fully closing the indoor expansion valve, the control device opens the indoor expansion valve by a predetermined value when the temperature of the heat absorber exceeds the predetermined value or a predetermined value higher than the predetermined value. 4. The vehicle air conditioner according to any one of claims 1 to 3, wherein the air conditioner opens at a degree. The control device causes the refrigerant discharged from the compressor to radiate heat with the expansion valve and the outdoor heat exchanger, decompresses the radiated refrigerant with the indoor expansion valve, and then absorbs heat with the heat absorber. Along with executing the cooling mode,
A control maximum value of the valve opening degree of the indoor expansion valve in the dehumidification heating mode is set smaller than a control maximum value of the valve opening degree of the indoor expansion valve in the dehumidification cooling mode. The vehicle air conditioner according to any one of claims 1 to 4.

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