WO2018110212A1

WO2018110212A1 - Vehicle air-conditioning apparatus

Info

Publication number: WO2018110212A1
Application number: PCT/JP2017/041581
Authority: WO
Inventors: 雄満山崎; 竜宮腰; 耕平山下
Original assignee: サンデン・オートモーティブクライメイトシステム株式会社
Priority date: 2016-12-14
Filing date: 2017-11-13
Publication date: 2018-06-21
Also published as: JP2018095098A; DE112017006293T5; JP6767856B2; CN110062708B; CN110062708A

Abstract

The present invention eliminates or suppresses temperature distribution (variation in temperature) generated in a heat absorber in a dehumidification cooling mode. The dehumidification cooling mode is executed in which the heat of a refrigerant discharged from a compressor 2 is dissipated at a heat dissipator 4 and an outdoor heat exchanger 7, the pressure of the heat-dissipated refrigerant is reduced by an indoor expansion valve 8, and then the heat is absorbed by a heat absorber 9. A control device controls the performance of the compressor on the basis of the temperature of the heat absorber, and controls the valve opening degree of an outdoor expansion valve on the basis of the temperature or pressure of the heat dissipator. The minimum opening degree of the outdoor expansion valve is changed so that no temperature distribution is generated in the heat absorber or the temperature distribution becomes small.

Description

Air conditioner for vehicles

The present invention relates to a heat pump type air conditioner that air-conditions the interior of a vehicle.

Hybrid vehicles and electric vehicles have come into widespread use due to the emergence of environmental problems in recent years. As an air conditioner that can be applied to such a vehicle, 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 heat from the passenger compartment, dissipate the refrigerant discharged from the compressor in the radiator, and dissipate the refrigerant dissipated in the radiator Heating mode in which heat is absorbed in the outdoor heat exchanger, and dehumidification in which the refrigerant discharged from the compressor is dissipated in the radiator and the refrigerant dissipated in the radiator is absorbed only in the heat absorber or in the heat absorber and the outdoor heat exchanger. Heating mode, dehumidifying cooling mode in which the refrigerant discharged from the compressor dissipates heat in the radiator and the outdoor heat exchanger, and absorbs heat in the heat absorber, and refrigerant discharged from the compressor Is radiated in the outdoor heat exchanger, which executes switching between the cooling mode to heat absorption have been developed in the heat sink (e.g., see Patent Document 1).
In the dehumidifying and cooling mode, the cooling (dehumidifying) capacity of the heat absorber is controlled by controlling the rotation speed of the compressor based on the temperature of the heat absorber. Moreover, the heating capacity of the radiator has been controlled by controlling the valve opening degree of the outdoor expansion valve that depressurizes the refrigerant flowing into the outdoor heat exchanger based on the temperature of the radiator.

JP 2014-205563 A

That is, in the dehumidifying and cooling mode, the temperature of the radiator can be increased by reducing the valve opening degree of the outdoor expansion valve. However, if the valve opening of the outdoor expansion valve is reduced, the amount of refrigerant circulating in the heat absorber decreases, so the temperature distribution of the heat absorber (the temperature varies depending on the heat absorber) increases and the dehumidification performance decreases. In addition, there is a problem that it is difficult to establish the target blowing temperature.
The present invention has been made to solve the conventional technical problem, and eliminates or suppresses the temperature distribution (temperature variation) generated in the heat absorber in the dehumidifying and cooling mode, thereby improving the air conditioning performance in the vehicle interior. An object of the present invention is to provide an air conditioning apparatus for a vehicle with improved performance.

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 heat sink for absorbing heat from the refrigerant and cooling the air supplied from the air flow passage to the vehicle interior, an outdoor heat exchanger for dissipating the refrigerant provided outside the vehicle compartment, An outdoor expansion valve for depressurizing the refrigerant flowing into the heat exchanger, an indoor expansion valve for depressurizing the refrigerant flowing into the heat absorber, and a control device are provided, and at least discharged from the compressor by the control device. The controller performs a dehumidifying and cooling mode in which the refrigerant is radiated by the radiator and the outdoor heat exchanger, and the radiated refrigerant is decompressed by the indoor expansion valve and then absorbed by the heat absorber. In cooling mode Controls the capacity of the compressor based on the temperature of the heat absorber, controls the valve opening of the outdoor expansion valve based on the temperature or pressure of the radiator, and prevents the temperature distribution from occurring in the heat absorber, The minimum valve opening degree of the outdoor expansion valve is changed so that the distribution becomes small.
According to a second aspect of the present invention, there is provided a vehicular air conditioner according to the first aspect of the present invention, wherein the control device is configured such that the temperature distribution of the heat absorber satisfies a predetermined threshold that is allowed for the temperature distribution of the heat absorber. The valve opening is changed.
According to a third aspect of the present invention, there is provided an air conditioner for a vehicle including an indoor blower that circulates air in the air flow passage in each of the above-described inventions, and the control device is configured based on the amount of air flow to the heat absorber by the indoor blower. The minimum valve opening degree of the outdoor expansion valve is changed in the direction of increasing as the amount increases.
According to a fourth aspect of the present invention, there is provided a vehicle air conditioner according to the above invention, wherein the controller is configured to open the minimum of the outdoor expansion valve in such a direction that the smaller the valve opening is, the smaller the valve opening is. It is characterized by changing the degree.
According to a fifth aspect of the present invention, in the air conditioning apparatus for a vehicle according to each of the above aspects, in the dehumidifying and cooling mode, the control device controls the capacity of the compressor based on the temperature of the heat absorber and the target temperature of the heat absorber, The minimum valve opening degree of the outdoor expansion valve is changed in a direction of decreasing as the target temperature of the vessel is lower.
A vehicle air conditioner according to a sixth aspect of the present invention is characterized in that, in each of the above inventions, the control device has a predetermined hysteresis when the minimum valve opening degree of the outdoor expansion valve is changed.

According to the present invention, 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 heat absorber that cools the air supplied to the vehicle interior through the air flow path by absorbing the refrigerant, an outdoor heat exchanger that is provided outside the vehicle cabin and dissipates the refrigerant, and the outdoor heat exchanger. An outdoor expansion valve for depressurizing the refrigerant flowing in, an indoor expansion valve for depressurizing the refrigerant flowing into the heat absorber, and a control device are provided, and at least the refrigerant discharged from the compressor is radiated by the control device. In a vehicle air conditioner that executes a dehumidifying and cooling mode in which heat is radiated by a heat exchanger and an outdoor heat exchanger, and the radiated refrigerant is decompressed by an indoor expansion valve and then absorbed by a heat absorber. smell Controls the capacity of the compressor based on the temperature of the heat absorber, controls the valve opening of the outdoor expansion valve based on the temperature or pressure of the radiator, and prevents the temperature distribution from occurring in the heat absorber, Since the minimum valve opening of the outdoor expansion valve is changed so that the distribution becomes smaller, the valve opening of the outdoor expansion valve becomes smaller, the amount of refrigerant circulation to the heat absorber decreases, and the temperature distribution in the heat absorber The problem that occurs or the temperature distribution of the heat absorber becomes large can be solved.
Thereby, while maintaining the dehumidifying performance of the heat absorber in the dehumidifying and cooling mode, the temperature of the radiator can be expanded, so that it is possible to contribute to energy saving. In addition, since it is easy to establish the target blowing temperature of the air supplied to the passenger compartment, air conditioning performance in the passenger compartment is generally improved, and passenger comfort can be improved.
In this case, the control device changes the minimum valve opening degree of the outdoor expansion valve so that the temperature distribution of the heat absorber satisfies a predetermined threshold that is allowed for the temperature distribution of the heat absorber. By doing so, the temperature distribution of the heat absorber associated with the reduction of the valve opening degree of the outdoor expansion valve can be accurately eliminated or suppressed.
Here, when an indoor blower that circulates air in the air flow passage is provided, and the ventilation blown by the indoor blower to the heat absorber, the larger the amount of ventilation, the more actively the refrigerant evaporates. The temperature distribution also increases. Therefore, the control device according to the invention of claim 3 is configured to change the minimum valve opening degree of the outdoor expansion valve in a direction of increasing the larger the ventilation amount based on the ventilation amount of the indoor fan to the heat absorber. Thus, the temperature distribution of the heat absorber associated with the reduction of the valve opening of the outdoor expansion valve can be effectively eliminated or suppressed.
Further, when the valve opening degree of the indoor expansion valve that depressurizes the refrigerant flowing into the heat absorber is large, the refrigerant circulation amount of the heat absorber increases, so the temperature distribution of the heat absorber becomes small. Therefore, as in the fourth aspect of the present invention, if the control device changes the minimum valve opening of the outdoor expansion valve in the direction of decreasing the valve opening as the valve opening is larger, based on the valve opening of the indoor expansion valve. The temperature of the radiator can be raised without any trouble while eliminating or suppressing the temperature distribution of the heat absorber.
Furthermore, since the controller controls the compressor based on the temperature of the heat absorber and its target temperature in the dehumidifying and cooling mode, the lower the target temperature of the heat absorber, the greater the capacity of the compressor and the amount of refrigerant circulation in the heat absorber. Will also increase. Therefore, if the control device changes the minimum valve opening of the outdoor expansion valve in the direction of decreasing the lower the target temperature of the heat absorber as the target temperature of the heat absorber is reduced, the temperature distribution of the heat absorber is eliminated. Alternatively, the temperature of the radiator can be raised without hindrance while being suppressed.
When the control device changes the minimum valve opening degree of the outdoor expansion valve as in the sixth aspect of the invention, the hunting is performed when the minimum valve opening degree of the outdoor expansion valve is changed by providing a predetermined hysteresis. It becomes possible to avoid the inconvenience that occurs.

It is a block diagram of the air conditioning apparatus for vehicles of one Embodiment to which this invention is applied. It is a block diagram of the control apparatus of the air conditioning apparatus for vehicles of FIG. It is a schematic diagram of the airflow path of the vehicle air conditioner of FIG. It is a control block diagram regarding the compressor control in the heating mode of the heat pump controller of FIG. It is a control block diagram regarding the compressor control in the dehumidification heating mode, the dehumidification cooling mode, the cooling mode, and the MAX cooling mode of the heat pump controller of FIG. It is a control block diagram regarding auxiliary heater (auxiliary heating apparatus) control in the dehumidification heating mode of the heat pump controller of FIG. It is a figure which shows the relationship between the valve opening degree of the outdoor expansion valve in the dehumidification air_conditioning | cooling mode of the vehicle air conditioner of FIG. 1, and the temperature of a radiator. It is a figure which shows the relationship between the valve opening degree of the outdoor expansion valve in the dehumidification air_conditioning | cooling mode of the vehicle air conditioner of FIG. 1, and the temperature distribution of a heat sink. It is a figure which shows the relationship between the valve opening degree of an outdoor expansion valve, and the temperature distribution of a heat absorber when the ventilation volume of a heat absorber changes in the dehumidification cooling mode of the vehicle air conditioner of FIG. It is a figure explaining the hysteresis when changing the minimum valve opening degree of an outdoor expansion valve with the ventilation volume of a heat absorber in the dehumidification cooling mode of the vehicle air conditioner of FIG. It is a figure explaining the control which changes the minimum valve opening degree of an outdoor expansion valve with the valve opening degree of an indoor expansion valve in the dehumidification cooling mode of the vehicle air conditioner of FIG. It is a timing chart explaining the situation when the target temperature of the heat absorber is lowered in the dehumidifying and cooling mode of the vehicle air conditioner of FIG. It is a figure explaining the control which changes the minimum valve opening degree of an outdoor expansion valve with the target temperature of a heat absorber in the dehumidification air_conditioning | cooling mode of the vehicle air conditioner of FIG. It is a block diagram of the air conditioning apparatus for vehicles of the other Example of this invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

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 travels by driving an electric motor for traveling with electric power charged in a battery. Yes (both not shown), the vehicle air conditioner 1 of the present invention is also driven by the power of the battery.
That is, the vehicle air conditioner 1 of the embodiment performs a heating mode by a heat pump operation using a refrigerant circuit in an electric vehicle that cannot be heated by engine waste heat, and further includes a dehumidifying heating mode, a dehumidifying cooling mode, a cooling mode, Each operation mode of the MAX cooling mode (maximum cooling mode) and the auxiliary heater single mode is selectively executed.
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 according to 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 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, dissipates the refrigerant, and supplies it to the vehicle interior. A radiator 4 for heating air, an outdoor expansion valve 6 (pressure reducing device) composed of an electric valve that decompresses and expands the refrigerant during heating, and functions as a radiator during cooling and serves as a radiator during heating, and an evaporator during heating An outdoor heat exchanger 7 that exchanges heat between the refrigerant and the outside air, an indoor expansion valve 8 (decompression device) that is an electric valve that decompresses and expands the refrigerant, and an air flow passage 3. Absorbs refrigerant during cooling and dehumidification A heat sink 9 for cooling caused by the air supplied to the vehicle interior is sucked from the cabin outside the accumulator 12 and the like are sequentially connected by a refrigerant pipe 13, the refrigerant circuit R is formed.
The refrigerant circuit R is filled with a predetermined amount of refrigerant and lubricating oil. 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). It is comprised so that external air may be ventilated by the heat exchanger 7. FIG.
The outdoor heat exchanger 7 has a receiver dryer section 14 and a supercooling section 16 sequentially on the downstream side of the refrigerant, and the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is received via an electromagnetic valve 17 opened during cooling. The refrigerant pipe 13 B connected to the dryer unit 14 and on the outlet side of the supercooling unit 16 is connected to the inlet side of the heat absorber 9 via the indoor expansion valve 8. In addition, the receiver dryer part 14 and the supercooling part 16 structurally constitute a part of the outdoor heat exchanger 7.
The refrigerant pipe 13B between the subcooling section 16 and the indoor expansion valve 8 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. Thus, 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.
Further, 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 downstream of the internal heat exchanger 19 via an electromagnetic valve 21 opened during heating. The refrigerant pipe 13C is connected in communication. The refrigerant pipe 13 C is connected to the accumulator 12, and the accumulator 12 is connected to the refrigerant suction side of the compressor 2. Further, the refrigerant pipe 13E on the outlet side of the radiator 4 is connected to the inlet side of the outdoor heat exchanger 7 via the outdoor expansion valve 6.
A refrigerant pipe 13G between the discharge side of the compressor 2 and the inlet side of the radiator 4 is provided with a solenoid valve 30 (which constitutes a flow path switching device) that is closed during dehumidification heating and MAX cooling described later. Yes. In this case, the refrigerant pipe 13G is branched into a bypass pipe 35 on the upstream side of the electromagnetic valve 30, and the bypass pipe 35 is opened by the electromagnetic valve 40 (which also constitutes a flow path switching device) during dehumidifying heating and MAX cooling. ) Through the refrigerant pipe 13E on the downstream side of the outdoor expansion valve 6. Bypass pipe 45, solenoid valve 30 and solenoid valve 40 constitute bypass device 45.
Since the bypass device 45 is configured by the bypass pipe 35, the electromagnetic valve 30, and the electromagnetic valve 40, the dehumidifying heating mode or the MAX for allowing the refrigerant discharged from the compressor 2 to directly flow into the outdoor heat exchanger 7 as will be described later. Switching between the cooling mode and the heating mode in which the refrigerant discharged from the compressor 2 flows into the radiator 4, the dehumidifying cooling mode, and the cooling mode can be performed smoothly.
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). 25 is provided with a suction switching damper 26 for switching the air introduced into the air flow passage 3 between the inside air (inside air circulation mode) which is air inside the passenger compartment and the outside air (outside air introduction mode) which is outside the passenger compartment. Yes. Further, an indoor blower (blower fan) 27 for supplying the introduced inside air or outside air to the air flow passage 3 and ventilating the heat absorber 9 is provided on the air downstream side of the suction switching damper 26.
Moreover, in FIG. 1, 23 is an auxiliary heater as an auxiliary heating device provided in the vehicle air conditioner 1 of the embodiment. The auxiliary heater 23 of the embodiment is composed of a PTC heater which is an electric heater, and is in the air flow passage 3 which is on the windward side (air upstream side) of the radiator 4 with respect to the air flow in the air flow passage 3. Is provided. When the auxiliary heater 23 is energized and generates heat, the air in the air flow passage 3 flowing into the radiator 4 through the heat absorber 9 is heated. In other words, the auxiliary heater 23 serves as a so-called heater core, which heats or complements the passenger compartment.
Here, the air flow passage 3 on the leeward side (air downstream side) from the heat absorber 9 of the HVAC unit 10 is partitioned by a partition wall 10A, and a heating heat exchange passage 3A and a bypass passage 3B that bypasses it are formed. The radiator 4 and the auxiliary heater 23 described above are disposed in the heating heat exchange passage 3A.
Further, 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 supplemented into the air flow passage 3 on the windward side of the auxiliary heater 23. An air mix damper 28 is provided for adjusting the rate of ventilation through the heating heat exchange passage 3A in which the heater 23 and the radiator 4 are disposed.
Further, the HVAC unit 10 on the leeward side of the radiator 4 includes a FOOT (foot) outlet 29A (first outlet) and a VENT (vent) outlet 29B (FOOT outlet 29A). For the outlet and the DEF outlet 29C, first outlets) and DEF (def) outlets 29C (second outlets) are formed. The FOOT air outlet 29A is an air outlet for blowing air under the feet in the passenger compartment, and is at the lowest position. Further, the VENT outlet 29B is an outlet for blowing out air near the driver's chest and face in the passenger compartment, and is located above the FOOT outlet 29A. The DEF air outlet 29C is an air outlet for blowing air to the inner surface of the windshield of the vehicle, and is located at the highest position above the

other air outlets

29A and 29B.
The FOOT air outlet 29A, the VENT air outlet 29B, and the DEF air outlet 29C are respectively provided with a FOOT air outlet damper 31A, a VENT air outlet damper 31B, and a DEF air outlet damper 31C that control the amount of air blown out. It has been.
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 20 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 20, 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. Has been.
The air conditioning controller 20 is a host controller that controls the air conditioning of the vehicle interior of the vehicle. The input of the air conditioning controller 20 includes an outside air temperature sensor 33 that detects the outside air temperature Tam of the vehicle and an outside air humidity that detects the outside air humidity. The sensor 34, the HVAC suction temperature sensor 36 that detects the temperature of the air (suction air temperature Tas) that is sucked into the air flow passage 3 from the suction port 25 and flows into the heat sink 9, and the temperature of the air (inside air) in the passenger compartment An indoor air temperature sensor 37 that detects (indoor temperature Tin), an indoor air humidity sensor 38 that detects the humidity of the air in the vehicle interior, an indoor CO ₂ concentration sensor 39 that detects the carbon dioxide concentration in the vehicle interior, and a blowout into the vehicle interior The temperature sensor 41 that detects the temperature of the air to be discharged, the discharge pressure sensor 42 that detects the refrigerant pressure Pd discharged from the compressor 2, and the amount of solar radiation into the passenger compartment are detected. For example, a photosensor-type solar radiation sensor 51, a vehicle speed sensor 52 for detecting the moving speed (vehicle speed) of the vehicle, and an air conditioner (air conditioner) operation for setting a set temperature and switching operation modes. The unit 53 is connected.
The output of the air conditioning controller 20 is connected to an outdoor blower 15, an indoor blower (blower fan) 27, a suction switching damper 26, an air mix damper 28, and air outlet dampers 31A to 31C. It is controlled by the controller 20.
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 for detecting the pressure Ps, a suction temperature sensor 55 for detecting the suction refrigerant temperature Ts of the compressor 2, a radiator temperature sensor 46 for detecting the refrigerant temperature of the radiator 4 (radiator temperature TCI), A radiator pressure sensor 47 that detects the refrigerant pressure of the radiator 4 (radiator pressure PCI), a heat absorber temperature sensor 48 that detects the refrigerant temperature of the heat absorber 9 (heat absorber temperature Te), and the refrigerant pressure of the heat absorber 9 A heat absorber pressure sensor 49 that detects the temperature of the auxiliary heater 23, an auxiliary heater temperature sensor 50 that detects the temperature of the auxiliary heater 23 (auxiliary heater temperature Tptc), and the outlet of the outdoor heat exchanger 7 An outdoor heat exchanger temperature sensor 54 that detects the refrigerant temperature (outdoor heat exchanger temperature TXO), and an outdoor heat exchanger pressure sensor 56 that detects the refrigerant pressure (outdoor heat exchanger pressure PXO) at the outlet of the outdoor heat exchanger 7. Each output is connected.
The output of the heat pump controller 32 includes an outdoor expansion valve 6, an indoor expansion valve 8, an electromagnetic valve 30 (for reheating), an electromagnetic valve 17 (for cooling), an electromagnetic valve 21 (for heating), and an electromagnetic valve 40 (bypass). Are connected to each other and are controlled by the heat pump controller 32. 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 20 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. In the embodiment in this case, the outside air temperature sensor 33, the discharge pressure sensor 42, the vehicle speed sensor 52, the volumetric air volume Ga of air flowing into the air flow passage 3 (calculated by the air conditioning controller 20), and the air volume ratio SW ( The output from the air conditioning controller 53 is transmitted from the air conditioning controller 20 to the heat pump controller 32 via the vehicle communication bus 65, and is used for control by the heat pump controller 32.
Next, the operation of the vehicle air conditioner 1 having the above-described configuration will be described. In this embodiment, the control device 11 (the air conditioning controller 20 and the heat pump controller 32) has each operation mode of heating mode, dehumidifying heating mode, dehumidifying cooling mode, cooling mode, MAX cooling mode (maximum cooling mode), and auxiliary heater single mode. Switch and execute. First, an outline of refrigerant flow and control in each operation mode will be described.
(1) Heating mode When the heating mode is selected by the heat pump controller 32 (auto mode) or by manual operation (manual mode) to the air conditioning operation unit 53, the heat pump controller 32 opens the electromagnetic valve 21 (for heating), The electromagnetic valve 17 (for cooling) is closed. Further, the electromagnetic valve 30 (for reheating) is opened, and the electromagnetic valve 40 (for bypass) is closed. Then, the compressor 2 is operated. The air conditioning controller 20 operates each of the

blowers

15 and 27, and the air mix damper 28 basically heats all the air in the air flow passage 3 that is blown out from the indoor blower 27 and passes through the heat absorber 9 to the heat exchange passage 3A for heating. The auxiliary heater 23 and the radiator 4 are ventilated, but the air volume may be adjusted.
As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 from the refrigerant pipe 13G via the electromagnetic valve 30. Since the air in the airflow passage 3 is passed through the radiator 4, the air in the airflow passage 3 is converted into the high-temperature refrigerant in the radiator 4 (when the auxiliary heater 23 operates, the auxiliary heater 23 and the radiator 4. On the other hand, the refrigerant in the radiator 4 is cooled by being deprived of heat by the air, and is condensed and liquefied.
The refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 through the refrigerant pipe 13E. 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. That is, the refrigerant circuit R becomes a heat pump. Then, the low-temperature refrigerant exiting the outdoor heat exchanger 7 enters the accumulator 12 from the refrigerant pipe 13C through the refrigerant pipe 13A, the electromagnetic valve 21 and the refrigerant pipe 13D, and is separated into gas and liquid there. Repeated circulation inhaled. The air heated by the radiator 4 (when the auxiliary heater 23 is operated, the auxiliary heater 23 and the radiator 4) is blown out from the outlets 29A to 29C, so that the vehicle interior is heated. become.
The heat pump controller 32 calculates the target radiator pressure PCO (target value of the radiator pressure PCI) from the target heater temperature TCO (target value of the radiator temperature TCI) calculated by the air conditioning controller 20 from the target outlet temperature TAO, and this target. The number of revolutions NC of the compressor 2 is controlled based on the radiator pressure PCO and the refrigerant pressure of the radiator 4 detected by the radiator pressure sensor 47 (radiator pressure PCI. High pressure of the refrigerant circuit R). Control the heating by. Further, the heat pump controller 32 opens the outdoor expansion valve 6 based on the refrigerant temperature (radiator temperature TCI) of the radiator 4 detected by the radiator temperature sensor 46 and the radiator pressure PCI detected by the radiator pressure sensor 47. The degree of supercooling of the refrigerant at the outlet of the radiator 4 is controlled.
Further, in this heating mode, when the heating capability by the radiator 4 is insufficient with respect to the heating capability required for the cabin air conditioning, the heat pump controller 32 supplements the shortage with the heat generated by the auxiliary heater 23. The energization of the auxiliary heater 23 is controlled. Thereby, comfortable vehicle interior heating is realized and frost formation of the outdoor heat exchanger 7 is also suppressed. At this time, since the auxiliary heater 23 is disposed on the air upstream side of the radiator 4, the air flowing through the air flow passage 3 is vented to the auxiliary heater 23 before the radiator 4.
Here, when the auxiliary heater 23 is disposed on the air downstream side of the radiator 4, when the auxiliary heater 23 is configured by a PTC heater as in the embodiment, the temperature of the air flowing into the auxiliary heater 23 is determined by the radiator. 4, the resistance value of the PTC heater increases, the current value also decreases, and the heat generation amount decreases. However, by arranging the auxiliary heater 23 on the air upstream side of the radiator 4, Thus, the capacity of the auxiliary heater 23 composed of the PTC heater can be sufficiently exhibited.
(2) Dehumidifying heating mode Next, in the dehumidifying heating mode, the heat pump controller 32 opens the electromagnetic valve 17 and closes the electromagnetic valve 21. Further, the electromagnetic valve 30 is closed, the electromagnetic valve 40 is opened, and the valve opening degree of the outdoor expansion valve 6 is fully closed. Then, the compressor 2 is operated. The air conditioning controller 20 operates each of the

blowers

15 and 27, and the air mix damper 28 basically heats all the air in the air flow passage 3 that is blown out from the indoor blower 27 and passes through the heat absorber 9 to the heat exchange passage 3A for heating. The auxiliary heater 23 and the radiator 4 are ventilated, but the air volume is also adjusted.
Accordingly, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 to the refrigerant pipe 13G flows into the bypass pipe 35 without going to the radiator 4, passes through the electromagnetic valve 40, and is connected to the refrigerant pipe on the downstream side of the outdoor expansion valve 6. 13E. At this time, since the outdoor expansion valve 6 is fully closed, the refrigerant flows into the outdoor heat exchanger 7. 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 that has exited the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13 A through the electromagnetic valve 17 into the receiver dryer unit 14 and the supercooling unit 16. Here, the refrigerant is supercooled.
The refrigerant that has exited the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13 B, reaches the indoor expansion valve 8 through the internal heat exchanger 19. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. The air blown out from the indoor blower 27 by the heat absorption action at this time is cooled, and moisture in the air condenses and adheres to the heat absorber 9, so that the air in the air flow passage 3 is cooled, and Dehumidified. The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C through the internal heat exchanger 19, and repeats circulation that is sucked into the compressor 2 there through.
At this time, since the valve opening degree of the outdoor expansion valve 6 is fully closed, it is possible to suppress or prevent inconvenience that the refrigerant discharged from the compressor 2 flows backward from the outdoor expansion valve 6 into the radiator 4. It becomes. Thereby, the fall of a refrigerant | coolant circulation amount can be suppressed or eliminated and air-conditioning capability can be ensured now. Further, in this dehumidifying and heating mode, the heat pump controller 32 energizes the auxiliary heater 23 to generate heat. As a result, the air cooled and dehumidified by the heat absorber 9 is further heated in the process of passing through the auxiliary heater 23 and the temperature rises, so that the dehumidifying heating in the passenger compartment is performed.
The heat pump controller 32 is a target heat absorption which is the target value (target temperature of the heat absorber 9) of the heat absorber temperature Te calculated by the air conditioning controller 20 and the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48 (heat absorber temperature Te). The rotational speed NC of the compressor 2 is controlled based on the compressor temperature TEO, and the auxiliary heater temperature Tptc detected by the auxiliary heater temperature sensor 50 and the above-described target heater temperature TCO (in this case, the target value of the auxiliary heater temperature Tptc is obtained). ) To control the energization (heating by heat generation) of the auxiliary heater 23 to appropriately cool the air in the heat absorber 9 and dehumidify the air from the air outlets 29A to 29C by heating with the auxiliary heater 23. The fall of the temperature of the air blown into the room is accurately prevented. As a result, it is possible to control the temperature to an appropriate heating temperature while dehumidifying the air blown into the vehicle interior, and it is possible to realize comfortable and efficient dehumidification heating in the vehicle interior.
In addition, since the auxiliary heater 23 is disposed on the air upstream side of the radiator 4, the air heated by the auxiliary heater 23 passes through the radiator 4. In this dehumidifying heating mode, the refrigerant is supplied to the radiator 4. Therefore, the disadvantage that the radiator 4 absorbs heat from the air heated by the auxiliary heater 23 is also eliminated. That is, the temperature of the air blown out into the vehicle compartment by the radiator 4 is suppressed, and the COP is improved.
(3) Dehumidifying and Cooling Mode Next, in the dehumidifying and cooling mode, the heat pump controller 32 opens the electromagnetic valve 17 and closes the electromagnetic valve 21. Further, the electromagnetic valve 30 is opened and the electromagnetic valve 40 is closed. Then, the compressor 2 is operated. The air conditioning controller 20 operates each of the

blowers

15 and 27, and the air mix damper 28 basically heats all the air in the air flow passage 3 that is blown out from the indoor blower 27 and passes through the heat absorber 9 to the heat exchange passage 3A for heating. The auxiliary heater 23 and the radiator 4 are ventilated, but the air volume is also adjusted.
As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 from the refrigerant pipe 13G via the electromagnetic valve 30. 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 that has exited the radiator 4 reaches the outdoor expansion valve 6 through the refrigerant pipe 13E, and flows into the outdoor heat exchanger 7 through the outdoor expansion valve 6 that is controlled to open. 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 that has exited the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13 A through the electromagnetic valve 17 into the receiver dryer unit 14 and the supercooling unit 16. Here, the refrigerant is supercooled.
The refrigerant that has exited the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13 B, reaches the indoor expansion valve 8 through the internal heat exchanger 19. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.
The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C through the internal heat exchanger 19, and repeats circulation that is sucked into the compressor 2 there through. In this dehumidifying and cooling mode, the heat pump controller 32 does not energize the auxiliary heater 23, so that the air that has been cooled and dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4 (the heat dissipation capability is lower than that during heating). Is done. As a result, dehumidifying and cooling in the passenger compartment is performed.
The heat pump controller 32 transmits the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and a target heat absorber temperature TEO (a target temperature of the heat absorber 9), which is a target value (target temperature of the heat absorber 9). ) To control the rotational speed NC (capacity of the compressor 2) of the compressor 2. That is, when the heat absorber temperature Te is higher than the target heat absorber temperature TEO, the rotational speed NC of the compressor 2 is increased, and when the heat absorber temperature Te is lower than the target heat absorber temperature TEO, the rotational speed NC is decreased. The heat pump controller 32 calculates the target radiator pressure PCO from the target heater temperature TCO described above, and the target radiator pressure PCO and the refrigerant pressure (radiator pressure PCI) of the radiator 4 detected by the radiator pressure sensor 47. Based on the high pressure of the refrigerant circuit R), the valve opening degree of the outdoor expansion valve 6 is controlled, and heating by the radiator 4 is controlled.
Here, in the embodiment, the heat pump controller 32 determines the valve opening degree of the outdoor expansion valve 6 based on the target radiator pressure PCO and the radiator pressure PCI calculated from the target heater temperature TCO that is the target value of the radiator temperature TCI. However, the valve opening degree of the outdoor expansion valve 6 may be controlled based on the radiator temperature TCI and the target heater temperature TCO. In any case, the heat pump controller 32 decreases the valve opening degree of the outdoor expansion valve 6 when the pressure (or temperature) of the radiator 4 is lower than the target value. When the valve opening degree of the outdoor expansion valve 6 decreases, the refrigerant subcooling degree SC in the radiator 4 increases, so the temperature of the radiator 4 rises and the heating capacity increases. On the other hand, when it is higher than the target value, the valve opening degree of the outdoor expansion valve 6 is increased, the temperature of the radiator 4 is lowered, and the heating capacity is reduced.
(4) Cooling mode Next, in the cooling mode, the heat pump controller 32 fully opens the valve opening degree of the outdoor expansion valve 6 in the dehumidifying and cooling mode. Then, the compressor 2 is operated and the auxiliary heater 23 is not energized. The air-conditioning controller 20 operates each of the

blowers

15 and 27, and the air mix damper 28 is blown from the indoor blower 27 and the air in the air flow passage 3 that has passed through the heat absorber 9 is used as the auxiliary heater 23 in the heating heat exchange passage 3A. And it is set as the state which adjusts the ratio ventilated by the heat radiator 4. FIG.
As a result, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 from the refrigerant pipe 13G via the electromagnetic valve 30, and the refrigerant exiting the radiator 4 passes through the refrigerant pipe 13E and the outdoor expansion valve 6. To. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant passes through it and flows into the outdoor heat exchanger 7 as it is, where it is cooled by air or by outside air that is ventilated by the outdoor blower 15 and condensed. Liquefaction. The refrigerant that has exited the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13 A through the electromagnetic valve 17 into the receiver dryer unit 14 and the supercooling unit 16. Here, the refrigerant is supercooled.
The refrigerant that has exited the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13 B, reaches the indoor expansion valve 8 through the internal heat exchanger 19. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. The air blown out from the indoor blower 27 by the heat absorption action at this time is cooled. Further, moisture in the air condenses and adheres to the heat absorber 9.
The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C through the internal heat exchanger 19, and repeats circulation that is sucked into the compressor 2 there through. Air that has been cooled and dehumidified by the heat absorber 9 is blown into the vehicle interior from each of the air outlets 29A to 29C (partly passes through the radiator 4 to exchange heat), thereby cooling the vehicle interior. Will be done. Further, in this cooling mode, the heat pump controller 32 uses the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the above-described target heat absorber temperature TEO which is the target value of the compressor 2. The number of revolutions NC is controlled.
(5) MAX cooling mode (maximum cooling mode)
Next, in the MAX cooling mode as the maximum cooling mode, the heat pump controller 32 opens the electromagnetic valve 17 and closes the electromagnetic valve 21. Further, the electromagnetic valve 30 is closed, the electromagnetic valve 40 is opened, and the valve opening degree of the outdoor expansion valve 6 is fully closed. Then, the compressor 2 is operated and the auxiliary heater 23 is not energized. The air conditioning controller 20 operates each of the

blowers

15 and 27, and the air mix damper 28 is blown from the indoor blower 27 and the air in the air flow passage 3 passing through the heat absorber 9 is used as an auxiliary heater for the heating heat exchange passage 3 A. 23 and the rate of ventilation through the radiator 4 are adjusted.
Accordingly, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 to the refrigerant pipe 13G flows into the bypass pipe 35 without going to the radiator 4, passes through the electromagnetic valve 40, and is connected to the refrigerant pipe on the downstream side of the outdoor expansion valve 6. 13E. At this time, since the outdoor expansion valve 6 is fully closed, the refrigerant flows into the outdoor heat exchanger 7. 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 that has exited the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13 A through the electromagnetic valve 17 into the receiver dryer unit 14 and the supercooling unit 16. Here, the refrigerant is supercooled.
The refrigerant that has exited the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13 B, reaches the indoor expansion valve 8 through the internal heat exchanger 19. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. The air blown out from the indoor blower 27 by the heat absorption action at this time is cooled. In addition, since moisture in the air condenses and adheres to the heat absorber 9, the air in the air flow passage 3 is dehumidified. The refrigerant evaporated in the heat absorber 9 reaches the accumulator 12 through the refrigerant pipe 13C through the internal heat exchanger 19, and repeats circulation that is sucked into the compressor 2 there through. At this time, since the outdoor expansion valve 6 is fully closed, similarly, it is possible to suppress or prevent the disadvantage that the refrigerant discharged from the compressor 2 flows backward from the outdoor expansion valve 6 into the radiator 4. . Thereby, the fall of a refrigerant | coolant circulation amount can be suppressed or eliminated and air-conditioning capability can be ensured now.
Here, since the high-temperature refrigerant flows through the radiator 4 in the cooling mode described above, direct heat conduction from the radiator 4 to the HVAC unit 10 occurs not a little, but in this MAX cooling mode, the refrigerant flows into the radiator 4. Therefore, the air in the air flow passage 3 from the heat absorber 9 is not heated by the heat transmitted from the radiator 4 to the HVAC unit 10. Therefore, powerful cooling of the passenger compartment is performed, and particularly in an environment where the outside air temperature Tam is high, the passenger compartment can be quickly cooled to realize comfortable air conditioning in the passenger compartment. Also in this MAX cooling mode, the heat pump controller 32 is also connected to the compressor based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO, which is the target value. 2 is controlled.
(6) Auxiliary heater single mode In addition, the control apparatus 11 of an Example stops the compressor 2 and the outdoor air blower 15 of the refrigerant circuit R, when the overheating frost arises in the outdoor heat exchanger 7, etc., and the auxiliary heater 23 And an auxiliary heater single mode in which the vehicle interior is heated only by the auxiliary heater 23. Also in this case, the heat pump controller 32 controls energization (heat generation) of the auxiliary heater 23 based on the auxiliary heater temperature Tptc detected by the auxiliary heater temperature sensor 50 and the target heater temperature TCO described above.
The air conditioning controller 20 operates the indoor blower 27, and the air mix damper 28 passes the air in the air flow passage 3 blown out from the indoor blower 27 to the auxiliary heater 23 of the heat exchange passage 3A for heating, and the air volume is reduced. The state to be adjusted. Since the air heated by the auxiliary heater 23 is blown into the vehicle interior from each of the air outlets 29A to 29C, the vehicle interior is thereby heated.
(7) Switching of operation mode The air-conditioning controller 20 calculates the target blowing temperature TAO mentioned above from following formula (I). This target blowing temperature TAO is a target value of the temperature of the air blown into the passenger compartment.
TAO = (Tset−Tin) × K + Tbal (f (Tset, SUN, Tam))
.. (I)
Here, Tset is the set temperature in the passenger compartment set by the air conditioning operation unit 53, Tin is the indoor temperature detected by the inside air temperature sensor 37, K is a coefficient, Tbal is the set temperature Tset, and the non-radiated light detected by the solar radiation sensor 51. The amount SUN is a balance value calculated from the outside air temperature Tam detected by the outside air temperature sensor 33. And generally this target blowing temperature TAO is so high that the outside temperature Tam is low, and it falls as the outside temperature Tam rises.
When the heat pump controller 32 is activated, the heat pump controller 32 determines which one of the above operation modes based on the outside air temperature Tam (detected by the outside air temperature sensor 33) transmitted from the air conditioning controller 20 via the vehicle communication bus 65 and the target outlet temperature TAO. The operation mode is selected and each operation mode is transmitted to the air conditioning controller 20 via the vehicle communication bus 65. In addition, after startup, the outside air temperature Tam, the humidity in the passenger compartment, the target blowing temperature TAO, the heating temperature TH (the temperature of the air on the leeward side of the radiator 4, estimated value), the target heater temperature TCO, the heat sink temperature Te, By switching each operation mode based on parameters such as the target heat absorber temperature TEO and whether or not there is a dehumidification request in the passenger compartment, the heating mode, dehumidification heating mode, and dehumidification are accurately performed according to the environmental conditions and necessity of dehumidification. The cooling mode, the cooling mode, the MAX cooling mode, and the auxiliary heater single mode are switched to control the temperature of the air blown into the vehicle interior to the target blowing temperature TAO, thereby realizing comfortable and efficient vehicle interior air conditioning.
(8) Control of compressor 2 in heating mode by heat pump controller 32 Next, control of the compressor 2 in heating mode mentioned above using FIG. 4 is explained in full detail. FIG. 4 is a control block diagram of the heat pump controller 32 that determines the target rotational speed (compressor target rotational speed) TGNCh of the compressor 2 for heating mode. The F / F (feed forward) manipulated variable calculation unit 58 of the heat pump controller 32 has an outside air temperature Tam obtained from the outside air temperature sensor 33, a blower voltage BLV of the indoor blower 27, and SW = (TAO−Te) / (TH−Te). ) Obtained by the air mix damper 28, the target supercooling degree TGSC that is the target value of the supercooling degree SC at the outlet of the radiator 4, and the target heater that is the target value of the temperature of the radiator 4 described above. Based on the temperature TCO (transmitted from the air conditioning controller 20) and the target radiator pressure PCO that is the target value of the pressure of the radiator 4, the F / F manipulated variable TGNChff of the compressor target rotational speed is calculated.
Here, the above-mentioned TH for calculating the air volume ratio SW is the temperature of the leeward air of the radiator 4 (hereinafter referred to as the heating temperature), and the heat pump controller 32 calculates the first-order lag calculation formula (II) shown below. presume.
TH = (INTL × TH0 + Tau × THz) / (Tau + INTL) (II)
Here, INTL is the calculation cycle (constant), Tau is the time constant of the primary delay, TH0 is the steady value of the heating temperature TH in the steady state before the primary delay calculation, and THz is the previous value of the heating temperature TH. By estimating the heating temperature TH in this way, there is no need to provide a special temperature sensor.
The heat pump controller 32 changes the time constant Tau and the steady value TH0 according to the operation mode described above, thereby making the above-described estimation formula (II) different depending on the operation mode, and estimates the heating temperature TH. The heating temperature TH is transmitted to the air conditioning controller 20 via the vehicle communication bus 65.
The target radiator pressure PCO is calculated by the target value calculator 59 based on the target subcooling degree TGSC and the target heater temperature TCO. Further, the F / B (feedback) manipulated variable calculator 60 calculates the F / B manipulated variable TGNChfb of the compressor target rotational speed based on the target radiator pressure PCO and the radiator pressure PCI that is the refrigerant pressure of the radiator 4. To do. The F / F manipulated variable TGNCnff computed by the F / F manipulated variable computing unit 58 and the TGNChfb computed by the F / B manipulated variable computing unit 60 are added by the adder 61, and the control upper limit value and the control are controlled by the limit setting unit 62. After the lower limit is set, it is determined as the compressor target rotational speed TGNCh. In the heating mode, the heat pump controller 32 controls the rotational speed NC of the compressor 2 based on the compressor target rotational speed TGNCh.
(9) Control of Compressor 2 in Dehumidification Heating Mode, Dehumidification Cooling Mode, Cooling Mode, and MAX Cooling Mode by Heat Pump Controller 32 On the other hand, FIG. 5 is for the dehumidifying heating mode, dehumidifying cooling mode, cooling mode, and MAX cooling mode. FIG. 3 is a control block diagram of a heat pump controller 32 that determines a target rotational speed (compressor target rotational speed) TGNCc of the compressor 2. The F / F manipulated variable calculation unit 63 of the heat pump controller 32 is a target heat release that is a target value of the outside air temperature Tam, the volumetric air volume Ga of the air flowing into the air flow passage 3, and the pressure of the radiator 4 (radiator pressure PCI). Based on the compressor pressure PCO and the target heat absorber temperature TEO which is the target value of the temperature of the heat absorber 9 (heat absorber temperature Te), the F / F manipulated variable TGNCcff of the compressor target rotational speed is calculated.
Further, the F / B operation amount calculation unit 64 calculates the F / B operation amount TGNCcfb of the compressor target rotational speed based on the target heat absorber temperature TEO (transmitted from the air conditioning controller 20) and the heat absorber temperature Te. Then, the F / F manipulated variable TGNCcff computed by the F / F manipulated variable computing unit 63 and the F / B manipulated variable TGNCcfb computed by the F / B manipulated variable computing unit 64 are added by the adder 66, and the limit setting unit 67 After the control upper limit value and the control lower limit value are set, the compressor target rotational speed TGNCc is determined. In the dehumidifying and heating mode, the heat pump controller 32 controls the rotational speed NC of the compressor 2 based on the compressor target rotational speed TGNCc.
(10) Control of the auxiliary heater 23 in the dehumidifying and heating mode by the heat pump controller 32 Next, FIG. 6 is a control block diagram of the heat pump controller 32 that determines the auxiliary heater required capacity TGQPTC of the auxiliary heater 23 in the dehumidifying and heating mode. The subtractor 73 of the heat pump controller 32 receives the target heater temperature TCO and the auxiliary heater temperature Tptc, and calculates a deviation (TCO−Tptc) between the target heater temperature TCO and the auxiliary heater temperature Tptc. This deviation (TCO-Tptc) is input to the F / B control unit 74. The F / B control unit 74 eliminates the deviation (TCO-Tptc) so that the auxiliary heater temperature Tptc becomes the target heater temperature TCO. The required capacity F / B manipulated variable is calculated.
The auxiliary heater required capability F / B manipulated variable calculated by the F / B control unit 74 is determined as the auxiliary heater required capability TGQPTC after the limit setting unit 76 limits the control upper limit value and the control lower limit value. . In the dehumidifying heating mode, the controller 32 controls energization of the auxiliary heater 23 based on the auxiliary heater required capacity TGQPTC, thereby generating heat (heating) of the auxiliary heater 23 so that the auxiliary heater temperature Tptc becomes the target heater temperature TCO. To control.
Thus, in the dehumidifying heating mode, the heat pump controller 32 controls the operation of the compressor based on the heat absorber temperature Te and the target heat absorber temperature TEO, and controls the heat generation of the auxiliary heater 23 based on the target heater temperature TCO. Thus, cooling and dehumidification by the heat absorber 9 and heating by the auxiliary heater 23 in the dehumidifying heating mode are accurately controlled. As a result, it is possible to control the temperature to a more accurate heating temperature while more appropriately dehumidifying the air blown into the passenger compartment, thereby realizing more comfortable and efficient dehumidifying heating in the passenger compartment. Will be able to.
(11) Control of Air Mix Damper 28 Next, control of the air mix damper 28 by the air conditioning controller 20 will be described with reference to FIG. In FIG. 3, Ga is the volumetric volume of the air flowing into the air flow passage 3 described above, Te is the heat absorber temperature, and TH is the heating temperature described above (the temperature of the air on the leeward side of the radiator 4).
The air conditioning controller 20 is based on the air volume ratio SW that is passed through the radiator 4 and the auxiliary heater 23 in the heating heat exchange passage 3A calculated by the above-described expression (the following expression (III)) so that the air volume of the ratio is obtained. Further, by controlling the air mix damper 28, the amount of ventilation to the radiator 4 (and the auxiliary heater 23) is adjusted.
SW = (TAO-Te) / (TH-Te) (III)
That is, the air flow rate ratio SW passing through the radiator 4 and the auxiliary heater 23 in the heat exchange passage 3A for heating changes in a range of 0 ≦ SW ≦ 1, and when “0”, the air is not passed through the heat exchange passage 3A for heating. The air mix fully closed state in which all the air in the air flow passage 3 is passed through the bypass passage 3B, and the air mix fully open state in which all the air in the air flow passage 3 is passed through the heating heat exchange passage 3A with "1" It becomes. That is, the air volume to the radiator 4 is Ga × SW.
(12) Change control of the minimum valve opening degree of the outdoor expansion valve 6 in the dehumidifying and cooling mode by the heat pump controller 32 (part 1)
Next, an example of change control of the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 in the dehumidifying and cooling mode by the heat pump controller 32 will be described with reference to FIGS. As described above, the heat pump controller 32 controls the valve opening ECCVpc of the outdoor expansion valve 6 based on the target radiator pressure PCO and the radiator pressure PCI in the embodiment in the dehumidifying and cooling mode. 32 controls the valve opening ECCVpc of the outdoor expansion valve 6 between a predetermined maximum valve opening ECCVpcmax and a minimum valve opening ECCVpcmin.
If the valve opening ECCVpc of the outdoor expansion valve 6 is reduced (the outdoor expansion valve 6 is throttled), the temperature of the radiator 4 (heat radiator temperature TCI) is increased as shown in FIG. 7, and the heating capacity is also increased. . However, when the valve opening degree ECCVpc of the outdoor expansion valve 6 is reduced, the refrigerant circulation amount of the heat absorber 9 is reduced by that amount, so that the refrigerant is completely evaporated at an early stage when it flows into the heat absorber 9. For this reason, the heat absorber 9 has low and high temperatures, resulting in temperature distribution (temperature variation). As the valve opening ECCVpc of the outdoor expansion valve 6 decreases as shown in FIG. Distribution increases.
When the temperature distribution is generated in the heat absorber 9 and becomes larger, the dehumidifying performance is lowered, and depending on the part, it becomes difficult to cool the ventilated air, and it becomes difficult to establish the target blowing temperature TAO, and the air conditioning performance in the vehicle interior Will get worse.
On the other hand, there is a correlation between the air flow rate through the indoor fan 27 to the heat absorber 9 and the temperature distribution, and the greater the air flow rate, the easier the temperature distribution occurs (note that all the air blown out from the indoor fan 27 is the heat absorber. 9), the volume air volume Ga described above becomes the air flow volume to the heat absorber 9). This is shown in FIG. In the embodiment, for example, the flow rate to the heat absorber 9 is divided into three stages, L1 in FIG. 9 is the temperature distribution of the heat sink 9 when the flow rate is high, L2 is the temperature distribution when the medium flow rate, L3 indicates the temperature distribution when the air volume is low. For example, assuming that the valve opening ECCVpc of the outdoor expansion valve 6 is B (FIG. 9), the greater the amount of ventilation to the heat absorber 9, the more actively the refrigerant in the heat absorber 9 evaporates. The temperature distribution of the heat absorber 9 also increases, and the difference between the temperature distribution L1 when the air volume is high and the temperature distribution L2 when the air volume is medium is X1 (FIG. 9).
Therefore, in the embodiment, a predetermined threshold value X2 that is allowed for the temperature distribution of the heat absorber 9 is set. In the embodiment, the threshold value X2 is a temperature distribution when the difference between the temperature of the air blown to the driver's seat side in the passenger compartment and the temperature of the air blown to the passenger seat side is a predetermined value (for example, 5 degrees). This is obtained in advance by experiments. However, the present invention is not limited thereto, and for example, the temperature at a plurality of locations of the heat absorber 9 may be measured in advance, and the threshold value X2 may be set directly from the difference therebetween.
As shown in FIG. 9, when the air flow rate of the heat absorber 9 is high, the valve opening degree of the outdoor expansion valve 6 at which the temperature distribution L1 of the heat absorber 9 increases to the threshold value X2 is A, and the air flow rate of the heat absorber 9 is medium. The temperature of the outdoor expansion valve 6 at which the temperature distribution L2 of the heat absorber 9 increases to the threshold value X2 when the air volume is B is B, and the temperature distribution L3 of the heat absorber 9 is the threshold value X2 when the air flow rate of the heat absorber 9 is low. If the valve opening degree of the outdoor expansion valve 6 that increases to C is C, the heat pump controller 32 allows the temperature distribution L1 of the heat absorber 9 to be the threshold value X2 of the outdoor expansion valve 6 when the air flow rate of the heat absorber 9 is high. When the valve opening degree A (FIG. 9) is the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 and the air flow rate of the heat absorber 9 is medium, the outdoor expansion valve 6 in which the temperature distribution L2 of the heat absorber 9 becomes the threshold value X2. Is the minimum valve opening ECC of the outdoor expansion valve 6. pcmin, and when the air flow rate of the heat absorber 9 is low, the valve opening C (FIG. 9) of the outdoor expansion valve 6 at which the temperature distribution L3 of the heat absorber 9 becomes the threshold value X2 is the minimum valve opening of the outdoor expansion valve 6. The minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is changed so as to set the degree of ECCVpcmin. As is apparent from FIG. 9, the relationship between the valve openings (minimum valve opening ECCVpcmin) is A>B> C. Moreover, although the air flow rate is determined in three steps in the embodiment, it may be determined in two steps, and conversely, it may be determined in more steps (four steps or more).
As a result, the valve opening degree of the outdoor expansion valve 6 is not reduced to a value at which the temperature distribution of the heat absorber 9 becomes larger than the threshold value X2 at any ventilation rate. That is, the heat pump controller 32 determines the minimum of the outdoor expansion valve 6 so that the temperature distribution of the heat absorber 9 satisfies the threshold value X2 (the temperature distribution is equal to or less than the threshold value X2) based on the air flow rate (volumetric air volume Ga) of the heat absorber 9. The valve opening degree ECCVpcmin is changed. However, when the heat pump controller 32 changes the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 according to the air flow rate of the heat absorber 9, the heat pump controller 32 gives a predetermined hysteresis to the air flow rate as shown in FIG. In FIG. 10, the arrow line indicating the change direction is shown obliquely, but actually changes in the vertical direction.
Thus, the heat pump controller 32 increases the minimum valve opening of the outdoor expansion valve 6 in such a direction that the larger the amount of air flow (high air amount) and the smaller the amount (low air amount), the smaller the amount of air flow. Since ECCVpcmin is changed, no temperature distribution is generated in the heat absorber 9 or the temperature distribution is reduced. As a result, the valve opening degree ECCVpc of the outdoor expansion valve 6 is decreased, the refrigerant circulation amount to the heat absorber 9 is decreased, the temperature distribution is generated in the heat absorber 9, or the temperature distribution of the heat absorber 9 is increased. Can be resolved. And while maintaining the dehumidifying performance of the heat sink 9 in the dehumidifying and cooling mode, the temperature of the radiator 4 (heat radiator temperature TCI) can also be expanded, so that it can contribute to energy saving. It becomes possible. In addition, since the target blowing temperature TAO of the air supplied to the passenger compartment can be easily established, the air conditioning performance in the passenger compartment can be improved as a whole, and passenger comfort can also be improved.
In this case, in the embodiment, the heat pump controller 32 changes the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 so that the temperature distribution of the heat absorber 9 satisfies a predetermined threshold value X2 that is allowed for the temperature distribution of the heat absorber 9. As a result, the temperature distribution of the heat absorber 9 accompanying the reduction of the valve opening ECCVpc of the outdoor expansion valve 6 can be eliminated or suppressed accurately.
Further, in this embodiment, the heat pump controller 32 changes the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 in a direction of increasing the larger the ventilation amount based on the ventilation amount of the indoor blower 6 to the heat absorber 9. Therefore, the temperature distribution of the heat absorber 9 accompanying the reduction of the valve opening ECCVpc of the outdoor expansion valve 6 can be effectively eliminated or suppressed.
Furthermore, in the embodiment, when changing the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6, the heat pump controller 32 changes the minimum valve opening degree ECCVpc of the outdoor expansion valve 6 because it has a predetermined hysteresis. In this case, the inconvenience of hunting can be avoided in advance.
(13) Change control of the minimum valve opening degree of the outdoor expansion valve 6 in the dehumidifying and cooling mode by the heat pump controller 32 (part 2)
Further, when the valve opening degree TXV of the indoor expansion valve 8 for reducing the pressure of the refrigerant flowing into the heat absorber 9 is large, the refrigerant circulation amount of the heat absorber 9 is increased, so that the temperature distribution of the heat absorber 9 is reduced. Therefore, the heat pump controller 32 changes the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 based on the valve opening degree TXV of the indoor expansion valve 8 instead of or in addition to the above embodiment (part 1).
FIG. 11 is a diagram for explaining an example of control for changing the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 by the valve opening degree TXV of the indoor expansion valve 8 in addition to the above-described embodiment (No. 1). In this embodiment, the ventilation to the heat absorber 9 described above depends on whether the valve opening TXV of the indoor expansion valve 8 is on the open side (the valve opening is large), the reference, or the closing side (the valve opening is small). The valve openings A, B, and C that are the minimum valve opening ECCVpcmin based on the amount (high air volume, medium air volume, low air volume) are further changed.
That is, when the valve opening degree TXV of the indoor expansion valve 8 is on the open side (the valve opening degree is large) and the air flow rate to the heat absorber 9 is high, the minimum valve of the outdoor expansion valve 6 is used. The opening degree ECCVpcmin is set to A-α smaller than the above-described valve opening degree A, and is set to B-β smaller than the above-described valve opening degree B when the medium air volume is obtained. C−γ is smaller than the opening degree C (where α, β, and γ are positive numbers).
When the valve opening degree TXV of the indoor expansion valve 8 is a reference value, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is set to the valve opening degree A set based on the air flow rate to the heat absorber 9 described above. , B, C.
On the other hand, when the valve opening degree TXV of the indoor expansion valve 8 is on the closed side (the valve opening degree is small) and the air flow rate to the heat absorber 9 is high, the minimum valve of the outdoor expansion valve 6 is used. The opening degree ECCVpcmin is set to A + δ larger than the above-described valve opening degree A, B + ε larger than the above-described valve opening degree B when the medium air volume is obtained, and from the above-described valve opening degree C when the air volume is low. Is larger C + ζ (where δ, ε, and ζ are positive numbers).
In this way, by changing the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 in a direction to be smaller as the valve opening degree TXV is larger based on the valve opening degree TXV of the indoor expansion valve 8 by the heat pump controller 32, While eliminating or suppressing the temperature distribution of the heat sink 9, the temperature of the radiator 4 can be raised without any trouble.
It should be noted that the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is changed based on only the valve opening degree TXV of the indoor expansion valve 8 without making any change based on the air flow rate to the heat absorber 9 regardless of this embodiment. You may make it do. In this case, for example, based on only the valve opening B described above, when the valve opening TXV of the indoor expansion valve 8 is on the open side, the minimum valve opening ECCVpcmin of the outdoor expansion valve 6 is set to B-β, and the valve opening For example, B is set when TXV is a reference, and B + ε is set when the valve opening TXV is closed.
(14) Change control of the minimum valve opening degree of the outdoor expansion valve 6 in the dehumidifying and cooling mode by the heat pump controller 32 (part 3)
Furthermore, as described above, in the dehumidifying and cooling mode, the heat pump controller 32 controls the rotational speed NC of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) and the target heat absorber temperature TEO that is the target temperature. As shown in FIG. 12, when the target heat absorber temperature TEO (target temperature of the heat absorber 9) is lowered, the rotational speed NC of the compressor 2 is increased, the capacity thereof is increased, and the refrigerant circulation amount of the heat absorber 9 is also increased. Become more. Thereby, the temperature distribution of the heat absorber 9 becomes smaller (portion indicated by X3 in FIG. 12), and the temperature of the radiator 4 (heat radiator temperature TCI) also rises.
Therefore, even if the minimum valve opening ECCVpcmin of the outdoor expansion valve 6 is lowered (the portion indicated by X4 in FIG. 12, the radiator temperature TCI also rises), the temperature distribution of the heat absorber 9 is the same as that before the target heat absorber temperature TEO is lowered. It becomes larger only up to the state (portion indicated by X5 in FIG. 12).
Therefore, the heat pump controller 32 changes the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 based on the target heat absorber temperature TEO instead of or in addition to the first embodiment (part 1) and the second embodiment (part 2). .
FIG. 13 is a diagram for explaining an example of control for changing the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 by the target heat absorber temperature TEO in addition to the first embodiment (part 1). In this embodiment, the minimum valve opening ECCVpcmin based on the air flow rate (high air volume, medium air volume, low air volume) to the heat absorber 9 described above depending on whether the target heat absorber temperature TEO is low, medium or high. Further, the valve openings A, B, and C are changed. Although FIG. 13 shows only the valve opening A when the air volume is high, the valve opening B when the air volume is medium and the valve opening C when the air volume is low are similarly changed.
That is, when the target heat absorber temperature TEO is low and the air flow rate to the heat absorber 9 is high, the minimum valve opening ECCVpcmin of the outdoor expansion valve 6 is set to A−η smaller than the valve opening A described above. And When the target heat absorber temperature TEO is medium, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is set to the valve opening degree A set from the high air flow rate to the heat absorber 9 described above. Further, when the target heat absorber temperature TEO is high and the air flow rate to the heat absorber 9 is high, the minimum valve opening ECCVpcmin of the outdoor expansion valve 6 is set to A + θ larger than the valve opening A described above. (However, η and θ are positive numbers).
Thus, since the heat pump controller 32 changes the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 in a direction to decrease as the target temperature of the heat absorber 9 (target heat absorber temperature TEO) is lower, the temperature of the heat absorber 9 While eliminating or suppressing the distribution, the temperature of the radiator 4 (the radiator temperature TCI) can be raised without any trouble (FIG. 12).
In the case of this embodiment as well, the minimum valve opening degree ECCVpcmin of the outdoor expansion valve 6 is set based on only the target heat absorber temperature TEO, without changing based on the air flow rate to the heat absorber 9 regardless of the above. You may make it change. In that case, for example, as shown in FIG. 13, only when the target heat absorber temperature TEO is low, the minimum valve opening ECCVpcmin of the outdoor expansion valve 6 is set to A−η when the target heat absorber temperature TEO is low. Is A, and when it is high, A + θ.

Next, FIG. 14 shows a configuration diagram of a vehicle air conditioner 1 of another embodiment to which the present invention is applied. In this figure, the same reference numerals as those in FIG. 1 indicate the same or similar functions. In the case of this embodiment, the outlet of the supercooling section 16 is connected to the check valve 18, and the outlet of the check valve 18 is connected to the refrigerant pipe 13B. The check valve 18 has a forward direction on the refrigerant pipe 13B (indoor expansion valve 8) side.
The refrigerant pipe 13E on the outlet side of the radiator 4 is branched before the outdoor expansion valve 6, and the branched refrigerant pipe (hereinafter referred to as second bypass pipe) 13F is an electromagnetic valve 22 (for dehumidification). Is connected to the refrigerant pipe 13B downstream of the check valve 18. Further, an evaporating pressure adjusting valve 70 is connected to the refrigerant pipe 13C on the outlet side of the heat absorber 9 on the refrigerant downstream side of the internal heat exchanger 19 and upstream of the refrigerant with respect to the refrigerant pipe 13D. .
The electromagnetic valve 22 and the evaporation pressure adjusting valve 70 are also connected to the output of the heat pump controller 32. Note that the bypass device 45 including the bypass pipe 35, the electromagnetic valve 30, and the electromagnetic valve 40 in FIG. 1 of the above-described embodiment is not provided. Others are the same as in FIG.
With the above configuration, the operation of the vehicle air conditioner 1 of this embodiment will be described. In this embodiment, the heat pump controller 32 switches between the heating mode, the dehumidifying heating mode, the internal cycle mode, the dehumidifying cooling mode, the cooling mode, and the auxiliary heater single mode (the MAX cooling mode is present in this embodiment). do not do). The operation when the heating mode, the dehumidifying and cooling mode, and the cooling mode are selected, the refrigerant flow, and the auxiliary heater single mode are the same as those in the above-described embodiment (embodiment 1), and thus the description thereof is omitted. However, in this embodiment (Example 2), the solenoid valve 22 is closed in the heating mode, the dehumidifying cooling mode, and the cooling mode.
(15) Dehumidifying heating mode of vehicle air conditioner 1 of FIG. 14 On the other hand, when the dehumidifying heating mode is selected, in this embodiment, heat pump controller 32 opens electromagnetic valve 21 (for heating) and electromagnetic valve 17 ( Close for cooling. Further, the electromagnetic valve 22 (for dehumidification) is opened. Then, the compressor 2 is operated. The air conditioning controller 20 operates each of the

blowers

15 and 27, and the air mix damper 28 basically heats all the air in the air flow passage 3 that is blown out from the indoor blower 27 and passes through the heat absorber 9 to the heat exchange passage 3A for heating. The auxiliary heater 23 and the radiator 4 are ventilated, but the air volume is also adjusted.
Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 from the refrigerant pipe 13G. Since the air in the air flow path 3 that has flowed into the heat exchange path 3A for heating is passed through the heat radiator 4, the air in the air flow path 3 is heated by the high-temperature refrigerant in the heat radiator 4, while the heat radiator The refrigerant in 4 is deprived of heat by the air and cooled to condense.
The refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 through the refrigerant pipe 13E. 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. That is, 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 solenoid valve 21 and the refrigerant pipe 13D, and is gas-liquid separated there. Repeated circulation inhaled.
Further, a part of the condensed refrigerant flowing through the refrigerant pipe 13E through the radiator 4 is diverted, passes through the electromagnetic valve 22, and reaches the indoor expansion valve 8 through the internal heat exchanger 19 from the second bypass pipe 13F and the refrigerant pipe 13B. It becomes like this. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.
The refrigerant evaporated in the heat absorber 9 sequentially passes through the internal heat exchanger 19 and the evaporation pressure adjusting valve 70 and then merges with the refrigerant from the refrigerant pipe 13D in the refrigerant pipe 13C. Then, the refrigerant is sucked into the compressor 2 through the accumulator 12. repeat. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed.
The air conditioning controller 20 transmits the target heater temperature TCO (target value of the radiator outlet temperature TCI) calculated from the target blowing temperature TAO to the heat pump controller 32. The heat pump controller 32 calculates a target radiator pressure PCO (target value of the radiator pressure PCI) from the target heater temperature TCO, and the refrigerant of the radiator 4 detected by the target radiator pressure PCO and the radiator pressure sensor 47. The number of revolutions NC of the compressor 2 is controlled based on the pressure (radiator pressure PCI, high pressure of the refrigerant circuit R), and heating by the radiator 4 is controlled. The heat pump controller 32 controls the valve opening degree of the outdoor expansion valve 6 based on the temperature Te of the heat absorber 9 detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO transmitted from the air conditioning controller 20. In addition, the heat pump controller 32 opens (enlarges the flow path) / closes (flows a small amount of refrigerant) the heat absorber 9 based on the temperature Te of the heat absorber 9 detected by the heat absorber temperature sensor 48. The inconvenience of freezing due to too low temperature is prevented.
(16) Internal cycle mode of the vehicle air conditioner 1 of FIG. 14 In the internal cycle mode, the heat pump controller 32 fully closes the outdoor expansion valve 6 in the dehumidifying and heating mode state (fully closed position), The solenoid valve 21 is closed. Since the outdoor expansion valve 6 and the electromagnetic valve 21 are closed, the inflow of refrigerant to the outdoor heat exchanger 7 and the outflow of refrigerant from the outdoor heat exchanger 7 are blocked. The condensed refrigerant flowing through the refrigerant pipe 13E through the refrigerant flows through the electromagnetic valve 22 to the second bypass pipe 13F. The refrigerant flowing through the second bypass pipe 13F reaches the indoor expansion valve 8 via the internal heat exchanger 19 from the refrigerant pipe 13B. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.
The refrigerant evaporated in the heat absorber 9 sequentially flows through the refrigerant pipe 13C through the internal heat exchanger 19 and the evaporation pressure adjustment valve 70, and repeats circulation that is sucked into the compressor 2 through the accumulator 12. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed. Since the refrigerant is circulated between the radiator 4 (radiation) and the heat absorber 9 (heat absorption) in the passage 3, heat from the outside air is not pumped up, and heating for the consumed power of the compressor 2 is performed. Ability is demonstrated. Since the entire amount of the refrigerant flows through the heat absorber 9 that exhibits the dehumidifying action, the dehumidifying capacity is higher than that in the dehumidifying and heating mode, but the heating capacity is lowered.
The air conditioning controller 20 transmits the target heater temperature TCO (target value of the radiator outlet temperature TCI) calculated from the target outlet temperature TAO to the heat pump controller 32. The heat pump controller 32 calculates the target radiator pressure PCO (target value of the radiator pressure PCI) from the transmitted target heater temperature TCO, and the target radiator pressure PCO and the radiator 4 detected by the radiator pressure sensor 47. The rotational speed NC of the compressor 2 is controlled based on the refrigerant pressure (radiator pressure PCI, high pressure of the refrigerant circuit R), and heating by the radiator 4 is controlled.
Since the flow and control of the refrigerant in the dehumidifying and cooling mode of the vehicle air conditioner 1 according to the second embodiment are the same as those in the first embodiment described above, the heat pump controller 32 also operates in the dehumidifying and cooling mode in this embodiment. By performing the change control (No. 1) to (No. 3) of the minimum valve opening degree of the outdoor expansion valve 6 of (12) to (14) described above, the temperature distribution is not generated in the heat absorber 9 as described above, or The temperature distribution becomes smaller. Accordingly, the valve opening ECCVpc of the outdoor expansion valve 6 is similarly reduced, the refrigerant circulation amount to the heat absorber 9 is reduced, and the temperature distribution is generated in the heat absorber 9 or the temperature distribution of the heat absorber 9 is increased. Inconvenience can be eliminated.
Similarly, in this case as well, the temperature of the radiator 4 (heat radiator temperature TCI) can be expanded while maintaining the dehumidifying performance of the heat absorber 9 in the dehumidifying and cooling mode. It is possible to contribute to energy saving. In addition, since the target blowing temperature TAO of the air supplied to the passenger compartment can be easily established, the air conditioning performance in the passenger compartment can be improved as a whole, and passenger comfort can also be improved.
It should be noted that the numerical values shown in the embodiments are not limited thereto, and should be appropriately set according to the apparatus to be applied. Further, 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. You may utilize the heater core etc. which circulate through the heated radiator water.

DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner 2 Compressor 3 Air flow path 4 Radiator 6 Outdoor expansion valve 7 Outdoor heat exchanger 8 Indoor expansion valve 9 Heat absorber 10 HVAC unit 11 Controller 20 Air-conditioning controller 27 Indoor blower (blower fan)
28 Air Mix Damper 32 Heat Pump Controller 41 Blowout Temperature Sensor 65 Vehicle Communication Bus R Refrigerant Circuit

Claims

A compressor for compressing the refrigerant;
An air flow passage through which air to be supplied into the passenger compartment flows;
A radiator for radiating the refrigerant to heat the air supplied from the air flow passage to the vehicle interior;
A heat absorber for absorbing the refrigerant and cooling the air supplied from the air flow passage to the vehicle interior;
An outdoor heat exchanger provided outside the passenger compartment to dissipate the refrigerant,
An outdoor expansion valve for depressurizing the refrigerant flowing into the outdoor heat exchanger;
An indoor expansion valve for depressurizing the refrigerant flowing into the heat absorber;
A control device,
Dehumidification by which at least the refrigerant discharged from the compressor is radiated by the controller and the outdoor heat exchanger, and the radiated refrigerant is decompressed by the indoor expansion valve and then absorbed by the heat absorber. In a vehicle air conditioner that executes a cooling mode,
In the dehumidifying and cooling mode, the control device controls the capacity of the compressor based on the temperature of the heat absorber, and controls the opening degree of the outdoor expansion valve based on the temperature or pressure of the radiator. ,
An air conditioner for a vehicle, wherein a minimum valve opening degree of the outdoor expansion valve is changed so that a temperature distribution does not occur in the heat absorber or the temperature distribution becomes small.
The said control apparatus changes the minimum valve opening degree of the said outdoor expansion valve so that the temperature distribution of the said heat absorber may satisfy | fill the predetermined threshold value permitted regarding the temperature distribution of the said heat absorber. The vehicle air conditioner according to claim 1.
An indoor blower for circulating air in the air flow passage;
The said control apparatus changes the minimum valve-opening degree of the said outdoor expansion valve in the direction which makes it large, so that the said ventilation amount is large based on the ventilation amount to the said heat absorber by the said indoor air blower. Or the air conditioning apparatus for vehicles of Claim 2.
2. The control device according to claim 1, wherein the control device changes the minimum valve opening of the outdoor expansion valve in a direction of decreasing the larger the valve opening, based on the valve opening of the indoor expansion valve. Item 4. The vehicle air conditioner according to any one of Items 3 to 4.
The control device, in the dehumidifying and cooling mode, controls the capacity of the compressor based on the temperature of the heat absorber and the target temperature of the heat absorber,
5. The vehicle air conditioner according to claim 1, wherein the minimum valve opening degree of the outdoor expansion valve is changed in a direction of decreasing as the target temperature of the heat absorber becomes lower. apparatus.
6. The vehicle air conditioner according to claim 1, wherein the control device gives a predetermined hysteresis when changing the minimum valve opening of the outdoor expansion valve. .