JP6871745B2 - Vehicle air conditioner - Google Patents

Description

In the present invention, an air conditioner for a vehicle that air-conditions the interior of a vehicle, particularly a heating device such as an electric heater, is used as an auxiliary for heating by a refrigerant circuit, or the heating device is mainly used to heat the air supplied to the interior of the vehicle. It relates to an air conditioner for vehicles.

Due to the emergence of environmental problems in recent years, hybrid vehicles and electric vehicles have become widespread. Then, as an air conditioner that can be applied to such a vehicle, a compressor that compresses and discharges the refrigerant, a radiator provided in the air flow passage of the HVAC unit to dissipate the refrigerant, and an air flow passage. It is equipped with a refrigerant circuit consisting of a heat absorber provided to absorb the refrigerant and an outdoor heat exchanger provided outside the vehicle interior to dissipate or absorb the refrigerant, and dissipate the refrigerant discharged from the compressor in the radiator. , A device that heats the air supplied from the indoor blower to heat the vehicle interior has been developed (see, for example, Patent Document 1).

Further, in Patent Document 1, an auxiliary heater (heating device) composed of an electric heater is provided in the air flow passage so that the heating capacity can be exhibited by the auxiliary heater in addition to the heating by the radiator of the refrigerant circuit. Further, in some cases, the refrigerant circuit is not heated by the radiator (for example, the refrigerant circuit is only for cooling), and the heating is performed only by the auxiliary heater (heating device) supplied from the battery.

Here, the HVAC unit having the air flow passage inside is usually molded of a hard resin. Therefore, when the auxiliary heater (heating device) is energized to generate heat, if the temperature of the auxiliary heater rises excessively, the heat of the auxiliary heater may cause the HVAC unit (air flow passage) to be deformed or melted. ..

Therefore, conventionally, in this type of vehicle air conditioner, output limit control is performed to limit the target auxiliary heater output value TGQhtr that controls the heat generation of the auxiliary heater (heating device). In this output limit control, for example, the detection value of the auxiliary heater temperature sensor that detects the highest temperature among the plurality of auxiliary heater temperature sensors that detect the temperature of the auxiliary heater (heating device) rises, and a predetermined limit is set. The target auxiliary heater output value TGQhr, which is started when the threshold value is reached and the controller controls the heat generation of the auxiliary heater, is lowered by a predetermined value.

After that, while the detection value of the auxiliary heater temperature sensor that detects the highest temperature is equal to or higher than the limit threshold value, the output value is lowered by a predetermined value, so that the temperature of at least a part of the auxiliary heater rises abnormally. As a result, the HVAC unit was prevented from being deformed.

FIG. 10 shows a control block diagram of a conventional controller relating to the control of the auxiliary heater, and FIG. 11 shows a flowchart illustrating output limitation control of the auxiliary heater by the conventional controller. In the required capacity calculation unit 101 of FIG. 10, the target blowing temperature TAO, which is the target value of the temperature of the air blown into the vehicle interior, the volume air volume Ga of the air flowing into the air flow passage of the HVAC unit, and the heat absorber temperature Te. Calculate the required heating capacity of the auxiliary heater from. The required heating capacity calculated by the required capacity calculation unit 101 is input to the target temperature calculation unit 102, and the target temperature calculation unit 102 calculates the target auxiliary heater temperature THO of the auxiliary heater.

The target auxiliary heater temperature THO calculated by the target temperature calculation unit 102 is then input to the target output value calculation unit 103. In the target output value calculation unit 103, the target is calculated by the calculation formula based on the heat absorber temperature Te, the volume air volume Ga, the target auxiliary heater temperature THO, and the auxiliary heater temperature Thr: TGQtr = f (Te, Ga, THO, Thr). The auxiliary heater temperature THO is converted into the target power (output) and output as the target auxiliary heater output value TGQtr (before the output limit). The auxiliary heater temperature Thr is the average value of the detection values of the plurality of auxiliary heater temperature sensors described above for detecting the temperature of the auxiliary heater, and in the calculation by the above formula executed by the controller, the target auxiliary heater temperature THO and the auxiliary heater are used. The feedback calculation based on the difference from the temperature Thr is calculated by adding the influence of the heat absorber temperature Te and the volume air volume Ga.

Next, the target auxiliary heater output value TGQhtr is input to the output limit control unit 104, and the output limit control described above is performed here. In the conventional output limit control, the detection value (maximum auxiliary heater temperature ThrMAX) of the auxiliary heater temperature sensor that detects the highest temperature among the plurality of auxiliary heater temperature sensors described in step S51 of FIG. 11 is a predetermined limit threshold value. It is determined whether or not it is (for example, + 70 ° C.) or higher, and if it is equal to or higher than the limit threshold value, the process proceeds to step S55, and the target auxiliary heater output value TGQhtr at the time of limitation is the control output lower limit value (control is not possible below that). It is determined whether or not it is the lower limit value), and if it is the lower limit value of the output, the process proceeds to step S57 and the target auxiliary heater output value TGQhr is set as the lower limit value of the output.

If the target auxiliary heater output value TGQhr at the time of limitation is not the control output lower limit value in step S55, the process proceeds to step S56 and the target auxiliary heater output value TGQhr at the time of limitation is set to the previous value − predetermined value. The target auxiliary heater output value TGQtr at the time of this limitation is output as the target auxiliary heater output value TGQtr (after the output limitation) in FIG. After that, this is repeated, and when the maximum auxiliary heater temperature ThrMAX is equal to or higher than the limit threshold value in step S51, the target auxiliary heater output value TGQhr is lowered by a predetermined value until it reaches the output lower limit value (during output limitation).

When the maximum auxiliary heater temperature ThrMAX becomes lower than the limit threshold value in the output limit control of the auxiliary heater, the process proceeds from step S51 to step S52. In this step S52, it is determined whether or not the target auxiliary heater output value TGQtr at the time of limitation is equal to or higher than the target auxiliary heater output value TGQtr (before output limitation) output from the target output value calculation unit 103, and the target auxiliary heater output value at the time of limitation is determined. If the TGQtr is smaller than the target auxiliary heater output value TGQtr (before the output limitation), the process proceeds to step S53 and the target auxiliary heater output value TGQtr at the time of limitation is set to the previous value + the predetermined value. After that, this is repeated, and the target auxiliary heater output value TGQtr at the time of limitation is increased by a predetermined value until the target auxiliary heater output value TGQtr at the time of limitation becomes equal to or higher than the target auxiliary heater output value TGQtr (before the output limitation) in step S52. ..

Then, when the target auxiliary heater output value TGQtr at the time of limitation becomes equal to or higher than the target auxiliary heater output value TGQtr (before the output limitation) in step S52, the process proceeds to step S54 and the target auxiliary heater output value TGQhr at the time of limitation is set to the target auxiliary heater. The output value is TGQhtr (before output limitation) (normal control). By such output limiting control, the inconvenience that the HVAC unit (member constituting the air flow passage) constituting the air flow passage is deformed due to an abnormal temperature rise of the auxiliary heater is prevented.

Japanese Unexamined Patent Publication No. 2014-213765

However, since the auxiliary heater temperature sensor that detects the temperature of the auxiliary heater has a response delay, when the maximum auxiliary heater temperature ThrMAX becomes lower than the limit threshold value and the output limit control ends, the target auxiliary heater output at the time of limit is output. The value TGQthr is lowered too much. This situation will be described with reference to FIG. In FIG. 12, L1 is the auxiliary heater temperature Thr (the average value of the detected values of the plurality of auxiliary heater temperature sensors), and L2 is the maximum auxiliary heater temperature ThrMAX (the auxiliary that detects the highest temperature among the plurality of auxiliary heater temperature sensors). The detection value of the heater temperature sensor) and L3 indicate the transition of the target auxiliary heater output value TGQhtr, respectively.

Although the limit threshold value (+ 70 ° C.) is shown in FIG. 12, when the maximum auxiliary heater temperature ThrMAX rises to the protection threshold value shown at + 90 ° C. above it, the power supply of the auxiliary heater is cut off. become.

As shown in FIG. 12, when the maximum auxiliary heater temperature ThrMAX exceeds the limit threshold value, the target auxiliary heater output value TGQtr (after the output limit) of the auxiliary heater (heating device) is gradually lowered by a predetermined value. (During output limitation) After that, when the maximum auxiliary heater temperature ThrMAX becomes lower than the limitation threshold, the target auxiliary heater output value TGQtr (after output limitation) of the auxiliary heater is increased by a predetermined value (normal control), as described above. Since the response of the auxiliary heater temperature sensor that detects the temperature of the auxiliary heater is slow, the maximum auxiliary heater temperature ThrMAX fluctuates greatly, the target auxiliary heater output value TGQtr decreases during output limitation, and the target auxiliary heater output by normal control. There is a problem that the auxiliary heater temperature Thr and the temperature of the air blown into the vehicle interior fluctuate greatly due to repeated increases in the value TGQtr.

The present invention has been made to solve the above-mentioned conventional technical problems, and suppresses fluctuations in the temperature of air blown into a vehicle interior in a vehicle air conditioner that controls output limitation of a heating device. The purpose is to do.

The vehicle air conditioner of the present invention includes an air flow passage through which air supplied to the vehicle interior flows, a heating device provided in the air flow passage for heating the air supplied to the vehicle interior, and the heating device. A temperature sensor that detects the temperature and a control device that controls the heat generation of the heating device based on the output of the temperature sensor are provided to heat the air supplied to the vehicle interior by the heating device. based on the target value THO of the temperature of the heating device, and calculates an output value TGQhtr for controlling the heating of the heating device, when the temperature Thtr heating device for detecting the temperature sensor is equal to or greater than a predetermined limit threshold is calculated It is characterized in that the output limit control for limiting the output value TGQtr is executed, and a predetermined lower limit limit value LimL is set for the output value TGQtr limited by the output limit control with reference to the target value THO.

The vehicle air conditioner according to claim 2 includes a plurality of temperature sensors in the above invention, and the control device is a heating device which is a detection value of the temperature sensor that detects the highest temperature among the plurality of temperature sensors. When the maximum temperature ThrMAX of the above rises and reaches the limit threshold, the output limit control is entered, the output value TGQtr is lowered by a predetermined value, and thereafter, while the maximum temperature ThrMAX of the heating device is equal to or higher than the limit threshold, the output is output by a predetermined value. It is characterized in that the value TGQhr is decreased and the decrease of the output value TGQhr is completed at the lower limit limit value LimL .

In the vehicle air conditioner according to the third aspect of the present invention, in each of the above inventions, the control device has a lower limit limit according to the temperature of the air flowing into the heating device and / or the volume air volume Ga of the air flowing into the air flow passage. It is characterized by changing the value LimL.

In the vehicle air conditioner according to the fourth aspect of the present invention, in the above invention, the control device changes the lower limit value LimL in the lowering direction as the temperature of the air flowing into the heating device is higher or the volume air volume Ga is smaller. It is characterized by doing.

The vehicle air conditioner according to claim 5 includes a compressor that compresses the refrigerant in each of the above inventions, and a radiator that is provided in the air flow passage and dissipates the refrigerant to heat the air supplied to the vehicle interior. A refrigerant circuit provided in the air flow passage and having a heat absorber for absorbing heat of the refrigerant and cooling the air supplied into the vehicle interior is provided, and the heating device is provided in the air flow passage as an auxiliary heating device of the refrigerant circuit. It is characterized by.

According to the present invention, an air flow passage through which air supplied to the vehicle interior flows, a heating device provided in the air flow passage for heating the air supplied to the vehicle interior, and the temperature of the heating device are detected. In a vehicle air conditioner that includes a temperature sensor and a control device that controls the heat generation of the heating device based on the output of the temperature sensor and heats the air supplied to the vehicle interior by the heating device, the control device is a temperature sensor. When the temperature Thr of the heating device detected by is equal to or higher than a predetermined limit threshold value, the output limit control for limiting the output value TGQtr that controls the heat generation of the heating device is executed, and the output value limited by this output limit control is executed. Since the predetermined lower limit value LimL is set for TGQtr, the output value TGQtr that controls the heat generation of the heating device is required even in the situation where the temperature Thr of the heating device exceeds the limit threshold and the output limit control is performed. It becomes possible to eliminate the inconvenience of being lowered above.

As a result, it is possible to prevent the inconvenience that the temperature of the air supplied to the vehicle interior fluctuates greatly due to the response delay of the temperature sensor that detects the temperature of the heating device, and to realize stable vehicle interior air conditioning. become able to.

In particular, the control device calculates the output value TGQtr based on the target value THO of the temperature of the heating device, and the output limit control limits the calculated output value TGQtr, and the lower limit limit value LimL is the target value THO. Is set as a reference, so that the lower limit limit value LimL is set based on the target value THO of the temperature of the heating device before being limited by the output limit control.

As a result, the lower limit limit value LimL is not affected by the output limit control of the heating device. Since the lower limit limit value LimL is set based on the target value THO of the temperature of the heating device, the lower limit limit value LimL is appropriately set according to the temperature of the heating device required for heating, and comfortable vehicle interior air conditioning is realized. You will be able to.

Further, when a plurality of temperature sensors for detecting the temperature of the heating device are provided as in the invention of claim 2, the detection value of the temperature sensor in which the control device detects the highest temperature among the plurality of temperature sensors. When the maximum temperature ThrMAX of the heating device rises and reaches the limit threshold, the output limit control is entered, the output value TGQtr is lowered by a predetermined value, and thereafter, while the maximum temperature ThrMAX of the heating device is equal to or higher than the limit threshold. By lowering the output value TGQtr by a predetermined value and ending the lowering of the output value TGQtr at the lower limit limit value LimL, the members constituting the air flow passage are deformed due to the abnormal temperature rise of the heating device. It becomes possible to realize stable vehicle interior air conditioning by suppressing temperature fluctuations of the air supplied to the vehicle interior while effectively avoiding the inconvenience.

Further, if the lower limit limit value LimL is changed according to the temperature of the air flowing into the heating device and / or the volume air volume Ga of the air flowing into the air flow passage as in the invention of claim 3, for example. As in the invention of claim 4, the higher the temperature of the air flowing into the heating device or the smaller the volume air volume Ga, the more appropriately by changing the lower limit limit value LimL in the lowering direction, depending on the environmental conditions. By setting the lower limit limit value LimL, it becomes possible to accurately realize output limit control and stable vehicle interior air conditioning.

The above invention includes a compressor that compresses the refrigerant as in the invention of claim 5, a radiator that is provided in the air flow passage and dissipates the refrigerant to heat the air supplied to the vehicle interior, and an air flow passage. In a vehicle air conditioner provided with a refrigerant circuit having a heat absorber that absorbs heat from the refrigerant and cools the air supplied to the vehicle interior, a heating device is provided in the air flow passage as an auxiliary heating device for the refrigerant circuit. If this is the case, it will be particularly suitable.

It is a block diagram of the air conditioner for a vehicle of one Embodiment to which this invention is applied. It is a block diagram of the control device of the air conditioner for a vehicle of FIG. It is a schematic diagram of the air flow passage of the air conditioner for a vehicle of FIG. It is a control block diagram concerning the compressor control in the heating mode of the heat pump controller of FIG. It is a control block diagram concerning the compressor control in the dehumidifying heating mode of the heat pump controller of FIG. It is a control block diagram concerning the control of the auxiliary heater (heating device, auxiliary heating device) of the heat pump controller of FIG. It is a flowchart explaining the output limitation control of the auxiliary heater by the heat pump controller of FIG. It is a figure which shows the transition of the auxiliary heater temperature Thr, the maximum auxiliary heater temperature ThrMAX, and the target auxiliary heater output value TGQtr in the output limit control of FIG. 7. It is a block diagram of the air conditioner for a vehicle of another Example of this invention. It is a control block diagram concerning the control of the conventional auxiliary heater. It is a flowchart explaining the output limitation control of the conventional auxiliary heater. It is a figure which shows the transition of the auxiliary heater temperature Thr, the maximum auxiliary heater temperature ThrMAX, and the target auxiliary heater output value TGQtr in the output limit control of FIG.

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

FIG. 1 shows a configuration diagram of an air conditioner 1 for a vehicle according to an embodiment of the present invention. The vehicle of the 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 (neither is shown), and 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 the heating mode by the heat pump operation using the refrigerant circuit in the electric vehicle that cannot be heated by the waste heat of the engine, and further, the dehumidifying heating mode, the dehumidifying cooling mode, the cooling mode, Each operation mode of the MAX cooling mode (maximum cooling mode) and the auxiliary heater independent mode is selectively executed.

It should be noted that the present invention is effective not only for electric vehicles as vehicles but also for so-called hybrid vehicles that use an engine and an electric motor for traveling, and further, it can be applied to ordinary vehicles traveling with an engine. Needless to say.

The vehicle air conditioner 1 of the embodiment air-conditions (heating, cooling, dehumidifying, and ventilating) the interior of the electric vehicle, and includes an electric compressor 2 that compresses the refrigerant and the interior air of the vehicle. Is provided in the air flow passage 3 configured in the HVAC unit 10 through which air is ventilated and circulated, and the high-temperature and high-pressure refrigerant discharged from the compressor 2 flows in through the refrigerant pipe 13G and dissipates the refrigerant to dissipate heat into the vehicle interior. An outdoor expansion valve 6 (decompression device) consisting of a radiator 4 for heating the air supplied to the vehicle and an electric valve that decompresses and expands the refrigerant during heating, and an outdoor expansion valve 6 (decompression device) provided outside the vehicle interior that functions as a radiator during cooling and heating. An outdoor heat exchanger 7 that exchanges heat between the refrigerant and the outside air to sometimes function as an evaporator, an indoor expansion valve 8 (decompression device) consisting of an electric valve that decompresses and expands the refrigerant, and an air flow passage 3 A heat absorber 9 for absorbing heat of the refrigerant during cooling and dehumidification to cool the air supplied to the inside of the vehicle by sucking it from the inside and outside of the vehicle, and an accumulator 12 and the like are sequentially connected by a refrigerant pipe 13 to form a refrigerant circuit. R is configured.

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 forcibly ventilates the outdoor air to the outdoor heat exchanger 7 to exchange heat between the outside air and the refrigerant, whereby the outdoor air is outdoors even when the vehicle is stopped (that is, the vehicle speed is 0 km / h). The heat exchanger 7 is configured to ventilate outside air.

Further, the outdoor heat exchanger 7 has a receiver dryer portion 14 and a supercooling portion 16 in sequence on the downstream side of the refrigerant, and the refrigerant pipe 13A coming out of the outdoor heat exchanger 7 receives the receiver via an electromagnetic valve 17 opened during cooling. The refrigerant pipe 13B on the outlet side of the supercooling unit 16 is connected to the dryer unit 14 and is connected to the inlet side of the heat exchanger 9 via the indoor expansion valve 8. The receiver dryer section 14 and the supercooling section 16 structurally form a part of the outdoor heat exchanger 7.

Further, the refrigerant pipe 13B between the supercooling unit 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 both constitute the internal heat exchanger 19. As a result, the refrigerant flowing into the indoor expansion valve 8 via the refrigerant pipe 13B is configured to be cooled (supercooled) by the low-temperature refrigerant leaving the heat absorber 9.

Further, the refrigerant pipe 13A coming out of the outdoor heat exchanger 7 is branched into the refrigerant pipe 13D, and the branched refrigerant pipe 13D is on the downstream side of the internal heat exchanger 19 via the electromagnetic valve 21 opened at the time of heating. Is connected to the refrigerant pipe 13C in the above. The refrigerant pipe 13C 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.

Further, the 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) which is closed at the time of dehumidifying heating and MAX cooling, which will be described later. There is. In this case, the refrigerant pipe 13G branches to the bypass pipe 35 on the upstream side of the solenoid valve 30, and the bypass pipe 35 also constitutes the solenoid valve 40 (which also constitutes the flow path switching device) that is opened during dehumidifying heating and MAX cooling. ) Is communicated with the refrigerant pipe 13E on the downstream side of the outdoor expansion valve 6. The bypass device 45 is composed of the bypass pipe 35, the solenoid valve 30, and the solenoid valve 40.

By configuring the bypass device 45 with such a bypass pipe 35, a solenoid valve 30, and a solenoid valve 40, a dehumidifying heating mode or MAX in which the refrigerant discharged from the compressor 2 directly flows into the outdoor heat exchanger 7 as described later. It becomes possible to smoothly switch between the cooling mode and the heating mode, the dehumidifying cooling mode, and the cooling mode in which the refrigerant discharged from the compressor 2 flows into the radiator 4.

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

Further, in FIG. 1, 23 is an auxiliary heater constituting the auxiliary heating device provided in the vehicle air conditioner 1 as an embodiment of the heating device. The auxiliary heater 23 of the embodiment is composed of a PTC heater (electric heater), and is inside the air flow passage 3 which is on the windward side (air upstream side) of the radiator 4 with respect to the air flow of the air flow passage 3. It is provided in. Then, when the auxiliary heater 23 is energized to generate heat, the air in the air flow passage 3 flowing into the radiator 4 via the endothermic absorber 9 is heated. That is, the auxiliary heater 23 serves as a so-called heater core, which heats or complements the interior of the vehicle.

Here, the air flow passage 3 on the leeward side (downstream side of the air) of the heat absorber 9 of the HVAC unit 10 is partitioned by the partition wall 10A, and the heat exchange passage 3A for heating and the bypass passage 3B bypassing the heat exchange passage 3A are formed. The above-mentioned radiator 4 and auxiliary heater 23 are arranged in the heating heat exchange passage 3A.

Further, in the air flow passage 3 on the wind side of the auxiliary heater 23, the air (inside air or outside air) in the air flow passage 3 that has flowed into the air flow passage 3 and passed through the heat absorber 9 is assisted. An air mix damper 28 for adjusting the ratio of ventilation to the heating heat exchange passage 3A in which the heater 23 and the radiator 4 are arranged is provided.

Further, the HVAC unit 10 on the leeward side of the radiator 4 has a FOOT (foot) outlet 29A (first outlet) and a VENT outlet 29B (a second outlet for the FOOT outlet 29A). Each outlet is formed with respect to the outlet and the DEF outlet 29C (first outlet) and the DEF (def) outlet 29C (second outlet). The FOOT outlet 29A is an outlet for blowing air under the feet in the vehicle interior, and is located at the lowest position. The VENT outlet 29B is an outlet for blowing air near the driver's chest and face in the vehicle interior, and is above the FOOT outlet 29A. The DEF outlet 29C is an outlet for blowing air onto the inner surface of the windshield of the vehicle, and is located at the highest position above the other outlets 29A and 29B.

The FOOT outlet 29A, the VENT outlet 29B, and the DEF outlet 29C are provided with the FOOT outlet damper 31A, the VENT outlet damper 31B, and the DEF outlet damper 31C, respectively, which control the amount of air blown out. Has been done.

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 is composed of an air conditioning controller 20 and a heat pump controller 32, each of which is composed of a microcomputer which is an example of a computer equipped with a processor, and these are CAN (Controller Area Network) and LIN (Local Interconnect Network). It is connected to the vehicle communication bus 65 constituting the above. Further, 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 done.

The air conditioner controller 20 is a higher-level controller that controls the interior air conditioning of the vehicle, and the input of the air conditioner 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 that is sucked into the air flow passage 3 from the suction port 25 and flows into the heat absorber 9 (suction air temperature Tas), and the temperature of the air (inside air) in the vehicle interior. An inside air temperature sensor 37 that detects (indoor temperature Tin), an inside air humidity sensor 38 that detects the humidity of the air inside the vehicle, an indoor CO ₂ concentration sensor 39 that detects the carbon dioxide concentration inside the vehicle, and a blowout into the vehicle interior. A blowout temperature sensor 41 that detects the temperature of the air to be generated, a discharge pressure sensor 42 that detects the discharge refrigerant pressure Pd of the compressor 2, and a photosensor type solar radiation sensor 51 for detecting the amount of solar radiation into the vehicle interior. Each output of the vehicle speed sensor 52 for detecting the moving speed (vehicle speed) of the vehicle is connected to the air conditioner (air conditioner) operation unit 53 for setting the set temperature and the switching of the operation mode.

Further, an outdoor blower 15, an indoor blower (blower fan) 27, a suction switching damper 26, an air mix damper 28, and outlet dampers 31A to 31C are connected to the output of the air conditioning controller 20, and they are air-conditioned. It is controlled by the controller 20.

The heat pump controller 32 is a controller that mainly controls the refrigerant circuit R, and the input of the heat pump controller 32 includes a discharge temperature sensor 43 that detects the discharge refrigerant temperature Td of the compressor 2 and a suction refrigerant of the compressor 2. A suction pressure sensor 44 that detects the pressure Ps, a suction temperature sensor 55 that detects the suction refrigerant temperature Ts of the compressor 2, a radiator temperature sensor 46 that detects the refrigerant temperature (radiator temperature TCI) of the radiator 4, and the radiator temperature sensor 46. The radiator pressure sensor 47 that detects the refrigerant pressure (radiator pressure PCI) of the radiator 4, the heat absorber temperature sensor 48 that detects the refrigerant temperature (heat absorber temperature Te) of the heat absorber 9, and the refrigerant pressure of the heat absorber 9. The heat absorber pressure sensor 49 that detects the above, a plurality of (four in the example) auxiliary heater temperature sensors 50D, 50A, 68D, 68A that detect the temperature of the auxiliary heater 23, and the refrigerant temperature at the outlet of the outdoor heat exchanger 7. Each of the outdoor heat exchanger temperature sensor 54 that detects (outdoor heat exchanger temperature TXO) and the 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. The output is connected.

In the embodiment, the auxiliary heater temperature sensor 50D is attached to a position near the center of the portion where the air blown to the driver's seat side of the auxiliary heater 23 flows, and the auxiliary heater temperature sensor 68D is also attached to the driver's seat side of the auxiliary heater 23. It is installed near the periphery of the part where the air blown out to the air flows. On the other hand, the auxiliary heater temperature sensor 50A is attached to a position near the center of the portion where the air blown to the passenger seat side of the auxiliary heater 23 flows, and the auxiliary heater temperature sensor 68A is also blown to the passenger seat side of the auxiliary heater 23. Auxiliary heater temperature sensors 50D, 68D, 50A, 68A are attached to positions near the periphery of the part where the air is circulated, and each of the auxiliary heater temperature sensors 50D, 68D, 50A, 68A detects the temperature of the auxiliary heater 23 in the attached portion and causes the heat pump controller 32 Output.

Further, the outputs of the heat pump controller 32 include an outdoor expansion valve 6, an indoor expansion valve 8, a solenoid valve 30 (for reheating), a solenoid valve 17 (for cooling), a solenoid valve 21 (for heating), and a solenoid valve 40 (bypass). Each solenoid valve is connected and they 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 transmit and receive data to and from the heat pump controller 32 via the vehicle communication bus 65, and the heat pump controller 32 transmits and receives data. Be controlled.

The heat pump controller 32 and the air conditioning controller 20 send and receive data to and from each other via the vehicle communication bus 65, and control each device based on the output of each sensor and the settings 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 volume air volume Ga of the air flowing into the air flow passage 3 (calculated by the air conditioning controller 20), and the air volume ratio SW by the air mix damper 28 ( (Calculated by the air conditioning controller 20), the output of the air conditioning operation unit 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.

With the above configuration, the operation of the vehicle air conditioner 1 of the embodiment will be described next. In this embodiment, the control device 11 (air conditioning controller 20, heat pump controller 32) sets each operation mode of heating mode, dehumidifying heating mode, dehumidifying cooling mode, cooling mode, MAX cooling mode (maximum cooling mode), and auxiliary heater independent mode. Switch and execute. First, the outline of the flow and control of the refrigerant 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 to the air conditioning operation unit 53 (manual mode), the heat pump controller 32 opens the solenoid valve 21 (for heating). Close the solenoid valve 17 (for cooling). Further, the solenoid valve 30 (for reheating) is opened, and the solenoid valve 40 (for bypass) is closed. Then, the compressor 2 is operated. The air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 basically blows out all the air in the air flow passage 3 that has been blown out from the indoor blower 27 and passed through the heat absorber 9 to heat the heat exchange passage 3A for heating. Although the state is such that the auxiliary heater 23 and the radiator 4 of the above are ventilated, 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 solenoid valve 30. Since the air in the air flow passage 3 is ventilated through the radiator 4, the air in the air flow passage 3 is the high temperature refrigerant in the radiator 4 (when the auxiliary heater 23 operates, the auxiliary heater 23 and the radiator 4 are used. ), On the other hand, the refrigerant in the radiator 4 is deprived of heat by the air and cooled to be condensed.

The refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 via the refrigerant pipe 13E. The refrigerant that has flowed into the outdoor expansion valve 6 is decompressed there, and then flows into the outdoor heat exchanger 7. The refrigerant that has flowed into the outdoor heat exchanger 7 evaporates and draws heat by running or from the outside air that is ventilated by the outdoor blower 15. That is, the refrigerant circuit R serves as a heat pump. Then, the low-temperature refrigerant that has exited the outdoor heat exchanger 7 enters the accumulator 12 from the refrigerant pipe 13C via the refrigerant pipe 13A, the solenoid valve 21, and the refrigerant pipe 13D, and after gas-liquid separation there, the gas refrigerant is used in the compressor 2. Repeat the circulation sucked into. Since the air heated by the radiator 4 (when the auxiliary heater 23 operates, the auxiliary heater 23 and the radiator 4) is blown out from the outlets 29A to 29C, the interior of the vehicle is heated by this. become.

In the heat pump controller 32, the target heater temperature TCO (target value of radiator temperature TCI. Basically TAO = TCO) calculated by the air conditioning controller 20 from the target outlet temperature TAO to the target radiator pressure PCO (target value of radiator pressure PCI). ) Is calculated, and the rotation speed NC of the compressor 2 is calculated based on the target radiator pressure PCO and the refrigerant pressure of the radiator 4 (radiator pressure PCI. High pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47. And control the heating by the radiator 4. 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 is controlled, and the degree of supercooling SC of the refrigerant at the outlet of the radiator 4 is controlled.

Further, in this heating mode, when the heating capacity of the radiator 4 is insufficient for the heating capacity required for the air conditioning in the vehicle interior, the heat pump controller 32 compensates for the shortage with the heat generated by the auxiliary heater 23. Controls the energization of the auxiliary heater 23. In this case, the heat pump controller 32 sets the average value of the temperatures (detected values) detected by the auxiliary heater temperature sensors 50D, 68D, 50A, and 68A as the auxiliary heater temperature Thr, and the auxiliary heat pump temperature Thr and the target auxiliary heater temperature THO ( The energization of the auxiliary heater 23 is controlled based on the auxiliary heater temperature Thtr (target value) calculated from the shortage of the heating capacity. The calculation of the target auxiliary heater temperature THO will be described in detail later.

By such coordinated control of the radiator 4 and the auxiliary heater 23, 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 arranged on the upstream side of the air of the radiator 4, the air flowing through the air flow passage 3 is ventilated to the auxiliary heater 23 in front of the radiator 4.

Here, if the auxiliary heater 23 is arranged on the downstream side of the air of the radiator 4, when the auxiliary heater 23 is configured by the PTC heater as in the embodiment, the temperature of the air flowing into the auxiliary heater 23 is the radiator. Since the temperature is increased by 4, the resistance value of the PTC heater increases, the current value also decreases, and the calorific value decreases. However, by arranging the auxiliary heater 23 on the air upstream side of the radiator 4, the example of the embodiment As described above, the ability of the auxiliary heater 23 composed of the PTC heater can be fully exhibited.

(2) Dehumidifying and heating mode Next, in the dehumidifying and heating mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valve 21. Further, the solenoid valve 30 is closed, the solenoid 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 the blowers 15 and 27, and the air mix damper 28 basically blows out all the air in the air flow passage 3 that has been blown out from the indoor blower 27 and passed through the heat absorber 9 to heat the heat exchange passage 3A for heating. The auxiliary heater 23 and the radiator 4 of the above 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 to the refrigerant pipe 13G flows into the bypass pipe 35 without going to the radiator 4, passes through the solenoid valve 40, and flows into the refrigerant pipe on the downstream side of the outdoor expansion valve 6. It will reach 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 air-cooled and condensed by traveling there or by the outside air ventilated by the outdoor blower 15. The refrigerant exiting the outdoor heat exchanger 7 flows sequentially from the refrigerant pipe 13A through the solenoid valve 17 to the receiver dryer section 14 and the supercooling section 16. Here the refrigerant is supercooled.

The refrigerant exiting the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8. 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 is cooled by the endothermic action at this time, and the 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 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12.

At this time, since the valve opening degree of the outdoor expansion valve 6 is fully closed, it is possible to suppress or prevent the inconvenience that the refrigerant discharged from the compressor 2 flows back from the outdoor expansion valve 6 into the radiator 4. It becomes. As a result, it becomes possible to suppress or eliminate the decrease in the amount of refrigerant circulation and secure the air conditioning capacity. Further, in this dehumidifying / 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 and heating of the vehicle interior is performed.

The heat pump controller 32 is a 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 a target value of the heat absorber temperature Te calculated by the air conditioner controller 20. From the auxiliary heater temperature Thr, which is the average value of the temperatures detected by the auxiliary heater temperature sensors 50D, 68D, 50A, and 68A described above, and the target heater temperature TCO (TCO = TAO) described above, while controlling the rotation speed NC of 2. By controlling the energization (heating by heat generation) of the auxiliary heater 23 based on the calculated target auxiliary heater temperature THO, the air is appropriately cooled and dehumidified by the heat absorber 9, and each is heated by the auxiliary heater 23. Accurately prevent a decrease in the air temperature blown into the vehicle interior from the outlets 29A to 29C. The calculation of the target auxiliary heater temperature THO will also be described in detail later.

As a result, it becomes possible to control the temperature to an appropriate heating temperature while dehumidifying the air blown into the vehicle interior, and it becomes possible to realize comfortable and efficient dehumidification heating in the vehicle interior.

Since the auxiliary heater 23 is arranged on the upstream side of the air of the radiator 4, the air heated by the auxiliary heater 23 passes through the radiator 4, but in this dehumidifying and heating mode, the radiator 4 has a refrigerant. Is not washed away, so the inconvenience that the radiator 4 absorbs heat from the air heated by the auxiliary heater 23 is also eliminated. That is, it is suppressed that the temperature of the air blown into the vehicle interior is lowered by the radiator 4, and the COP is also improved.

(3) Dehumidifying / cooling mode Next, in the dehumidifying / cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valve 21. Further, the solenoid valve 30 is opened and the solenoid valve 40 is closed. Then, the compressor 2 is operated. The air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 basically blows out all the air in the air flow passage 3 that has been blown out from the indoor blower 27 and passed through the heat absorber 9 to heat the heat exchange passage 3A for heating. The auxiliary heater 23 and the radiator 4 of the above 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 solenoid valve 30. Since the air in the air flow passage 3 is ventilated through the radiator 4, the air in the air flow passage 3 is heated by the high temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. It is deprived, cooled, and condensed.

The refrigerant exiting the radiator 4 reaches the outdoor expansion valve 6 via the refrigerant pipe 13E, and flows into the outdoor heat exchanger 7 via the outdoor expansion valve 6 which is slightly opened and controlled. The refrigerant flowing into the outdoor heat exchanger 7 is air-cooled and condensed by traveling there or by the outside air ventilated by the outdoor blower 15. The refrigerant exiting the outdoor heat exchanger 7 flows sequentially from the refrigerant pipe 13A through the solenoid valve 17 to the receiver dryer section 14 and the supercooling section 16. Here the refrigerant is supercooled.

The refrigerant exiting the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Due to the endothermic action at this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat absorber 9, so that the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. In this dehumidifying / cooling mode, since the heat pump controller 32 does not energize the auxiliary heater 23, it is cooled by the heat absorber 9, and the dehumidified air is reheated in the process of passing through the radiator 4 (the heat dissipation capacity is lower than that during heating). Will be done. As a result, the interior of the vehicle is dehumidified and cooled.

The heat pump controller 32 of the compressor 2 is 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 (transmitted from the air conditioning controller 20) which is the target value thereof. Controls the number of revolutions NC. Further, the heat pump controller 32 calculates the target radiator pressure PCO from the above-mentioned target heater temperature TCO, and the target radiator pressure PCO and the refrigerant pressure (radiator pressure PCI) of the radiator 4 detected by the radiator pressure sensor 47. The valve opening degree of the outdoor expansion valve 6 is controlled based on the high pressure of the refrigerant circuit R), and the heating by the radiator 4 is controlled.

(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 state of the dehumidifying cooling mode. Then, the compressor 2 is operated and the auxiliary heater 23 is not energized. The air conditioning controller 20 operates the blowers 15 and 27, and in the air mix damper 28, the air in the air flow passage 3 blown out from the indoor blower 27 and passed through the heat absorber 9 is the auxiliary heater 23 of the heat exchange passage 3A for heating. And the ratio of ventilation to the radiator 4 is 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 solenoid valve 30, and the refrigerant discharged from 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 air-cooled by running or by the outside air ventilated by the outdoor blower 15 and condensed. Liquefaction. The refrigerant exiting the outdoor heat exchanger 7 flows sequentially from the refrigerant pipe 13A through the solenoid valve 17 to the receiver dryer section 14 and the supercooling section 16. Here the refrigerant is supercooled.

The refrigerant exiting the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8. 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 is cooled by the endothermic action at this time. Further, the moisture in the air condenses and adheres to the heat absorber 9.

The refrigerant evaporated in the heat absorber 9 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. Since the dehumidified air cooled by the heat absorber 9 is blown out into the vehicle interior from the outlets 29A to 29C (a part of the air passes through the radiator 4 to exchange heat), the air inside the vehicle interior is cooled. It will be done. Further, in this cooling mode, the heat pump controller 32 uses the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the above-mentioned target heat absorber temperature TEO which is the target value thereof. Controls the number of rotations NC.

(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 solenoid valve 17 and closes the solenoid valve 21. Further, the solenoid valve 30 is closed, the solenoid 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 the blowers 15 and 27, and in the air mix damper 28, the air in the air flow passage 3 blown out from the indoor blower 27 and passed through the heat absorber 9 is an auxiliary heater of the heat exchange passage 3A for heating. The ratio of ventilation to the 23 and the radiator 4 is adjusted.

As a result, 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 solenoid valve 40, and flows into the refrigerant pipe on the downstream side of the outdoor expansion valve 6. It will reach 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 air-cooled and condensed by traveling there or by the outside air ventilated by the outdoor blower 15. The refrigerant exiting the outdoor heat exchanger 7 flows sequentially from the refrigerant pipe 13A through the solenoid valve 17 to the receiver dryer section 14 and the supercooling section 16. Here the refrigerant is supercooled.

The refrigerant exiting the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8. 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 is cooled by the endothermic action at this time. Further, since the 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 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. At this time, since the outdoor expansion valve 6 is fully closed, it is possible to suppress or prevent the inconvenience that the refrigerant discharged from the compressor 2 flows back from the outdoor expansion valve 6 into the radiator 4. .. As a result, it becomes possible to suppress or eliminate the decrease in the amount of refrigerant circulation and secure the air conditioning capacity.

Here, since the high-temperature refrigerant is flowing through the radiator 4 in the above-mentioned cooling mode, direct heat conduction from the radiator 4 to the HVAC unit 10 is not a little generated, but in this MAX cooling mode, the refrigerant is transferred to the radiator 4. Does not flow, so that the heat transferred from the radiator 4 to the HVAC unit 10 does not heat the air in the air flow passage 3 from the heat absorber 9. Therefore, the interior of the vehicle is strongly cooled, and particularly in an environment where the outside air temperature Tam is high, the interior of the vehicle can be quickly cooled to realize comfortable air conditioning in the vehicle interior. Further, even in this MAX cooling mode, the heat pump controller 32 is a compressor based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the above-mentioned target heat absorber temperature TEO which is the target value thereof. The number of rotations NC of 2 is controlled.

(6) Auxiliary heater independent mode The control device 11 of the embodiment stops the compressor 2 and the outdoor blower 15 of the refrigerant circuit R when over-frost occurs in the outdoor heat exchanger 7, and the auxiliary heater 23 is used. It has an auxiliary heater independent mode in which the vehicle interior is heated only by the auxiliary heater 23 by energizing the vehicle interior. Also in this case, the heat pump controller 32 is calculated from the auxiliary heater temperature Thr, which is the average value of the temperatures detected by the auxiliary heater temperature sensors 50D, 68D, 50A, and 68A, and the target heater temperature TCO (TCO = TAO) described above. The energization (heating by heat generation) of the auxiliary heater 23 is controlled based on the target auxiliary heater temperature THO. The calculation of the target auxiliary heater temperature THO will also be described in detail later.

Further, the air conditioning controller 20 operates the indoor blower 27, and the air mix damper 28 ventilates the air in the air flow passage 3 blown out from the indoor blower 27 to the auxiliary heater 23 of the heating heat exchange passage 3A to increase the air volume. It is in a state to be adjusted. Since the air heated by the auxiliary heater 23 is blown into the vehicle interior from the outlets 29A to 29C, the interior of the vehicle is heated by this.

(7) Switching of operation mode The air conditioning controller 20 calculates the target blowout temperature TAO described above from the following formula (I). This target blowing temperature TAO is a target value of the temperature of the air blown into the vehicle interior.
TAO = (Tset-Tin) x K + Tbal (f (Tset, SUN, Tam))
・ ・ (I)
Here, Tset is the set temperature in the vehicle interior set by the air conditioning operation unit 53, Tin is the indoor temperature detected by the inside air temperature sensor 37, K is a coefficient, Tbal is the set temperature Tset, and the amount of solar radiation detected by the solar radiation sensor 51. It is a balance value calculated from the outside air temperature Tam detected by the SUN and the outside air temperature sensor 33. In general, the target blowing temperature TAO increases as the outside air temperature Tam decreases, and decreases as the outside air temperature Tam increases.

The heat pump controller 32 is any of the above operation modes based on the outside air temperature Tam (detected by the outside air temperature sensor 33) and the target blowout temperature TAO transmitted from the air conditioning controller 20 via the vehicle communication bus 65 at the time of activation. The operation mode is selected, and each operation mode is transmitted to the air conditioning controller 20 via the vehicle communication bus 65. After startup, the outside air temperature Tam, the humidity inside the vehicle, the target blowout 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, and the heater temperature Te, which will be described later, By switching each operation mode based on parameters such as the target heat sink temperature TEO and the presence or absence of dehumidification request in the vehicle interior, the heating mode, dehumidification heating mode, and dehumidification can be performed accurately according to the environmental conditions and the necessity of dehumidification. By switching between the cooling mode, the cooling mode, the MAX cooling mode, and the auxiliary heater independent mode, the temperature of the air blown into the vehicle interior is controlled to the target outlet temperature TAO, and comfortable and efficient vehicle interior air conditioning is realized.

(8) Control of the Compressor 2 in the Heating Mode by the Heat Pump Controller 32 Next, the control of the compressor 2 in the heating mode described above will be described in detail with reference to FIG. FIG. 4 is a control block diagram of the heat pump controller 32 that determines the target rotation speed (compressor target rotation speed) TGNCh of the compressor 2 for the heating mode. The F / F (feed forward) operation amount calculation unit 58 of the heat pump controller 32 has the outside air temperature Tam obtained from the outside air temperature sensor 33, the blower voltage BLV of the indoor blower 27, and SW = (TAO-Te) / (TH-Te). ), The air volume ratio SW by the air mix damper 28, the target supercooling degree TGSC which is the target value of the supercooling degree SC at the outlet of the radiator 4, and the above-mentioned target heater which is the target value of the temperature of the radiator 4 The F / F operation amount TGNChff of the compressor target rotation speed is calculated based on the temperature TCO (transmitted from the air conditioner controller 20) and the target radiator pressure PCO which is the target value of the pressure of the radiator 4.

Here, the TH for calculating the air volume ratio SW is the temperature of the air on the leeward side of the radiator 4 (hereinafter referred to as the heating temperature), and the heat pump controller 32 uses the equation (II) for the first-order lag calculation shown below. presume.
TH = (INTL x TH0 + Tau x THz) / (Tau + INTL) ... (II)
Here, INTL is the calculation period (constant), Tau is the time constant of the first-order delay, TH0 is the steady-state value of the heating temperature TH in the steady state before the first-order delay calculation, and THH is the previous value of the heating temperature TH. By estimating the heating temperature TH in this way, it is not necessary to provide a special temperature sensor.

By changing the time constant Tau and the steady-state value TH0 according to the operation mode described above, the heat pump controller 32 makes the estimation formula (II) described above different depending on the operation mode, and estimates the heating temperature TH. Then, this 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 calculation unit 59 based on the target supercooling degree TGSC and the target heater temperature TCO. Further, the F / B (feedback) operation amount calculation unit 60 calculates the F / B operation amount TGNChfb of the compressor target rotation speed based on the target radiator pressure PCO and the radiator pressure PCI which is the refrigerant pressure of the radiator 4. To do. Then, the F / F operation amount TGNCnff calculated by the F / F operation amount calculation unit 58 and the TGNChfb calculated by the F / B operation amount calculation unit 60 are added by the adder 61, and are controlled by the limit setting unit 62 as the control upper limit value. After the lower limit is set, it is determined as the compressor target rotation speed TGNCh. In the heating mode, the heat pump controller 32 controls the rotation speed NC of the compressor 2 based on the compressor target rotation speed TGNCh.

(9) Control of the Compressor 2 in the Dehumidifying and Heating Mode by the Heat Pump Controller 32 On the other hand, FIG. 5 shows the heat pump controller 32 for determining the target rotation speed (compressor target rotation speed) TGNCc of the compressor 2 for the dehumidifying and heating mode. It is a control block diagram. The F / F operation amount calculation unit 63 of the heat pump controller 32 has an outside air temperature Tam, a volume air volume Ga of the air flowing into the air flow passage 3, and a target heat dissipation which is a target value of the pressure of the radiator 4 (radiator pressure PCI). The F / F operation amount TGNCcff of the compressor target rotation speed is calculated based on the device 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).

Further, the F / B manipulated variable calculation unit 64 calculates the F / B manipulated variable TGNCcfb of the compressor target rotation speed based on the target endothermic temperature TEO (transmitted from the air conditioning controller 20) and the endothermic temperature Te. Then, the F / F operation amount TGNCcff calculated by the F / F operation amount calculation unit 63 and the F / B operation amount TGNCcffb calculated by the F / B operation amount calculation unit 64 are added by the adder 66, and are added by the limit setting unit 67. After the control upper limit value and the control lower limit value are limited, it is determined as the compressor target rotation speed TGNCc. In the dehumidifying / heating mode, the heat pump controller 32 controls the rotation speed NC of the compressor 2 based on the compressor target rotation speed TGNCc.

(10) Control of Air Mix Damper 28 by Air Conditioning Controller 20 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 air volume of the air flowing into the air flow passage 3 described above, Te is the temperature of the endothermic absorber, 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 has an air volume of the ratio based on the air volume ratio SW that ventilates the radiator 4 and the auxiliary heater 23 of the heat exchange passage 3A for heating calculated by the above formula (the following formula (III)). 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 volume ratio SW that ventilates the radiator 4 and the auxiliary heater 23 of the heat exchange passage 3A for heating changes in the range of 0 ≦ SW ≦ 1, and “0” does not allow ventilation to 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 ventilated to the bypass passage 3B, and the air mix fully open state in which all the air in the air flow passage 3 is ventilated to the heating heat exchange passage 3A in "1". It becomes. That is, the air volume to the radiator 4 is Ga × SW.

(11) Control of the auxiliary heater 23 in the heating mode, the dehumidifying heating mode, and the auxiliary heater independent mode by the heat pump controller 32 Next, the above-mentioned heating mode, the dehumidifying heating mode, and the dehumidifying heating mode by the heat pump controller 32 with reference to FIGS. The details of the control of the auxiliary heater 23 in the auxiliary heater independent mode will be described. FIG. 6 shows a control block diagram of the heat pump controller 32 relating to the control of the auxiliary heater 23, and FIG. 7 is a flowchart illustrating output limit control of the auxiliary heater 23 by the heat pump controller 32.

In the required capacity calculation unit 71 of FIG. 6, the target blowout temperature TAO, the volume air volume Ga of the air flowing into the air flow passage of the HVAC unit, and the heat absorber temperature Te (the heat absorber temperature Te is the air flowing into the auxiliary heater 23). The capacity (required heating capacity) required for heating by the auxiliary heater 23 is calculated from the temperature). The required heating capacity calculated by the required capacity calculation unit 71 is input to the target temperature calculation unit 72, and the target temperature calculation unit 72 calculates the target auxiliary heater temperature THO, which is the target value of the temperature of the auxiliary heater 23.

The target auxiliary heater temperature THO calculated by the target temperature calculation unit 72 is then input to the target output value calculation unit 73. In the target output value calculation unit 73, the heat absorber temperature Te, the volume air volume Ga, the target auxiliary heater temperature THO, and the auxiliary heater temperature Thr (the average value of the temperatures detected by the auxiliary heater temperature sensors 50D, 68D, 50A, 68A). ): TGQhr = f (Te, Ga, THO, Thr) converts the target auxiliary heater temperature THO into the target power (output) and outputs it as the target auxiliary heater output value TGQtr (before output limitation). ..

In the calculation by the above calculation formula executed by the heat pump controller 32, the influence of the endothermic temperature Te and the volume air volume Ga is added to the feedback calculation based on the difference between the target auxiliary heater temperature THO and the auxiliary heater temperature Thr. Become. In this case, the target auxiliary heater output value TGQtr increases as the volume air volume Ga increases and the endothermic temperature Te decreases, and the target auxiliary heater temperature THO increases and the auxiliary heater temperature Thr decreases. It becomes smaller. Then, the target auxiliary heater output value TGQtr (before the output limit) calculated by the above formula based on the target auxiliary heater temperature THO by the target output value calculation unit 73 is input to the output limit control unit 74.

On the other hand, the target auxiliary heater temperature THO calculated by the target temperature calculation unit 72 is further input to the subtractor 76. In this subtractor 76, the reduction value RED of the target auxiliary heater temperature THO, which is a fixed value such as 20 deg in this embodiment, is subtracted from the target auxiliary heater temperature THO to set the lower limit value Tliml of the target auxiliary heater temperature THO. It is output. For example, when the target auxiliary heater temperature THO calculated by the target temperature calculation unit 72 is + 60 ° C., the lower limit limit value Tliml of the target auxiliary heater temperature THO is + 40 ° C. reduced by 20 deg, and the target auxiliary heater temperature THO is + 50 ° C. At one time, the lower limit limit value Tliml of the target auxiliary heater temperature THO becomes + 30 ° C.

That is, the lower limit limit value Tliml of the target auxiliary heater temperature THO fluctuates together with the target auxiliary heater temperature THO while maintaining the difference between the target auxiliary heater temperature THO required for heating by the auxiliary heater 23 and the reduction value RED. .. Further, since the target auxiliary heater temperature THO is information (value) before the output limit control is performed in the output limit control unit 74 described later, the lower limit limit value LimL is not affected by the output limit control.

The lower limit value Tliml of the target auxiliary heater temperature THO is input to another target output value calculation unit 77. In the target output value calculation unit 77, the heat absorber temperature Te, the volume air volume Ga, the lower limit limit value Tliml of the target auxiliary heater temperature THO, and the auxiliary heater temperature Thr (each auxiliary heater temperature sensors 50D, 68D, 50A, 68A are detected. Calculation formula based on (average value of temperature): TGQhtr = f (Te, Ga, Tliml, Thr) converts the lower limit limit value Tliml of the target auxiliary heater temperature THO to the target power (output), and the target auxiliary heater output value. It is output as the lower limit value LimL of TGQhr. Therefore, the lower limit limit value LimL is set as a value obtained by converting the value lowered by the reduction value RED from the target auxiliary heater temperature THO as a reference and converting it into the target power.

In this case as well, in the calculation based on the above formula, the influence of the heat absorber temperature Te and the volume air volume Ga is added to the feedback calculation based on the difference between the lower limit value TlimL of the target auxiliary heater temperature THO and the auxiliary heater temperature Thr. It becomes an operation. Also in this case, the lower limit limit value LimL of the target auxiliary heater output value TGQhtr becomes larger as the volume air volume Ga is larger and the endothermic temperature Te is lower, and the lower limit limit value Tliml of the target auxiliary heater temperature THO is higher. The lower the auxiliary heater temperature Thtr, the smaller the temperature. Then, the lower limit limit value LimL of the target auxiliary heater output value TGQhtr calculated by the target output value calculation unit 77 is also input to the output limit control unit 74.

The output limit control unit 74 performs output limit control. In the output limit control of the embodiment, the detection value (maximum auxiliary heater) of the auxiliary heater temperature sensor that detects the highest temperature among the plurality of auxiliary heater temperature sensors 50D, 68D, 50A, 68A described in step S1 of FIG. It is determined whether or not the temperature ThrMAX) is equal to or higher than a predetermined limit threshold value (for example, + 70 ° C.), and if it is equal to or higher than the limit threshold value, the process proceeds to step S5, and the target auxiliary heater output value TGQtr at the time of limit is the control output lower limit value. It is determined whether or not the value is (the lower limit value at which control cannot be performed below that value), and if the output lower limit value is reached, the process proceeds to step S8 and the target auxiliary heater output value TGQhtr is set as the output lower limit value.

If the target auxiliary heater output value TGQhtr at the time of limitation is not the control output lower limit value in step S5, the process proceeds to step S6 to calculate the lower limit limit value LimL of the target auxiliary heater output value TGQhr. This calculation is performed by the target output value calculation unit 77 as described above. Next, the process proceeds to step S7, and the target auxiliary heater output value TGQtr at the time of limitation is subtracted from the previous value of the target auxiliary heater output value TGQtr lower limit value LimL or the target auxiliary heater output value TGQhr at the time of limitation. The larger one (MAX) of (previous value-predetermined value) is used.

Then, the target auxiliary heater output value TGQtr at the time of this limitation is output as the target auxiliary heater output value TGQtr (after MAX) in FIG. This target auxiliary heater output value TGQhtr (after MAX) becomes an output value that controls heat generation of the auxiliary heater 23. That is, this is repeated until the value obtained by subtracting the predetermined value from the previous value of the target auxiliary heater output value TGQhtr at the time of limitation (previous value-predetermined value) becomes smaller than the lower limit limit value LimL of the target auxiliary heater output value TGQtr, and the target auxiliary heater is assisted. The heater output value TGQhtr is limited by decreasing it by a predetermined value (during output limitation).

On the other hand, when the value obtained by subtracting the predetermined value from the previous value of the target auxiliary heater output value TGQhtr at the time of limitation (previous value-predetermined value) becomes smaller than the lower limit limit value LimL of the target auxiliary heater output value TGQhr, the target auxiliary heater is in turn in step S7. Since the lower limit limit value LimL of the heater output value TGQtr is selected and output as the target auxiliary heater output value TGQtr (after MAX) at the time of limitation in FIG. 6, the target auxiliary heater output value TGQtr (after MAX) is output at this point. ) Is finished, and it does not fall below the lower limit limit value LimL.

When the maximum auxiliary heater temperature ThrMAX becomes lower than the limit threshold value by the output limitation control of the auxiliary heater 23, the process proceeds from step S1 to step S2. In this step S2, it is determined whether or not the target auxiliary heater output value TGQtr at the time of limitation is equal to or higher than the target auxiliary heater output value TGQtr (before the output limitation) output from the target output value calculation unit 73, and the target auxiliary heater output value at the time of limitation is determined. If the TGQtr is smaller than the target auxiliary heater output value TGQtr (before the output limit), the process proceeds to step S3, and the target auxiliary heater output value TGQhr at the time of limitation is set to the previous value + a predetermined value. After that, this is repeated, and the target auxiliary heater output value TGQtr at the time of limitation is increased by a predetermined value until the target auxiliary heater output value TGQtr at the time of limitation becomes equal to or higher than the target auxiliary heater output value TGQtr (before the output limitation) in step S2. ..

Then, when the target auxiliary heater output value TGQtr at the time of limitation becomes equal to or higher than the target auxiliary heater output value TGQtr (before the output limitation) in step S2, the process proceeds to step S4 and the target auxiliary heater output value TGQhr at the time of limitation is set to the target auxiliary heater. The output value is TGQhtr (before output limitation) (normal control). Such output limiting control prevents the inconvenience that the HVAC unit 10 (members constituting the air flow passage 3) constituting the air flow passage 3 is deformed due to an abnormal temperature rise of the auxiliary heater 23.

FIG. 8 shows the auxiliary heater temperature Thr (L1) in the output limitation control of the auxiliary heater 23 in the present invention, and the auxiliary heater that detects the highest temperature among the plurality of auxiliary heater temperature sensors 50D, 68D, 50A, and 68A. The transition of the detection value of the temperature sensor (maximum auxiliary heater temperature ThrMAX: L2) and the target auxiliary heater output value TGQhr (L3) is shown.

The limiting threshold value shown in FIG. 8 is + 70 ° C. in the examples, and the protection threshold value is + 90 ° C. above it. When the maximum auxiliary heater temperature ThrMAX rises to this protection threshold value, the heat pump controller 32 cuts off the energization of the auxiliary heater 23.

As shown in FIG. 8, when the maximum auxiliary heater temperature ThrMAX exceeds the limit threshold value from the normal control, the target auxiliary heater output value TGQtr (after MAX) of the auxiliary heater 23 is gradually lowered by a predetermined value. (During output limitation), when the lower limit value is lowered to LimL, the target auxiliary heater output value TGQthr (after MAX) does not decrease any more. As a result, the auxiliary heater temperature Thr and the maximum auxiliary heater temperature ThrtrMAX hardly fluctuate, the auxiliary heater temperature Thrr is substantially stable at a value lower than the limit threshold value, and the maximum auxiliary heater temperature ThrtrMAX is substantially stable at a value lower than the protection threshold value. It becomes.

In the embodiment, since the auxiliary heater 23 is turned off at a certain point, the auxiliary heater temperature Thr and the maximum auxiliary heater temperature ThrtrMAX are also lowered after that. When the heater temperature ThrMAX becomes lower than the limit threshold value, the target auxiliary heater output value TGQtr (after the output limit) of the auxiliary heater is increased by a predetermined value (returns to normal control).

As described above, when the maximum auxiliary heater temperature ThrMAX becomes equal to or higher than the predetermined limit threshold value, the heat pump controller 32 executes the output limit control for limiting the target auxiliary heater output value TGQhr that controls the heat generation of the auxiliary heater 23, and also performs this output limit control. Since the predetermined lower limit limit value LimL is set for the target auxiliary heater output value TGQtr limited by the output limit control, even in the situation where the maximum auxiliary heater temperature ThrMAX exceeds the limit threshold value and the output limit control is performed. It becomes possible to eliminate the inconvenience that the target auxiliary heater output value TGQthr that controls the heat generation of the auxiliary heater 23 is lowered more than necessary.

This prevents the inconvenience that the temperature of the air supplied to the vehicle interior fluctuates greatly due to the response delay of the auxiliary heater temperature sensors 50D, 68D, 50A, 68A that detect the temperature of the auxiliary heater 23. It will be possible to realize stable vehicle interior air conditioning.

Further, in the embodiment, a plurality of auxiliary heater temperature sensors 50D, 68D, 50A, 68A are provided to detect the temperature of the auxiliary heater 23, and the heat pump controller 32 uses the plurality of auxiliary heater temperature sensors 50D, 68D, 50A. , 68A When the maximum auxiliary heater temperature ThrMAX, which is the detection value of the auxiliary heater temperature sensor that detects the highest temperature, rises and reaches the limit threshold, the output limit control is entered and the target auxiliary heater output value TGQhr After that, while the maximum auxiliary heater temperature ThrMAX is equal to or higher than the limit threshold value, the target auxiliary heater output value TGQtr is lowered by a predetermined value, and the target auxiliary heater output value TGQhr is lowered at the lower limit limit value LimL. Is supplied to the vehicle interior while effectively avoiding the inconvenience that the constituent walls of the HVAC unit 10 constituting the air flow passage 3 are deformed due to an abnormal temperature rise of the auxiliary heater 23. It will be possible to realize stable vehicle interior air conditioning by suppressing temperature fluctuations in the air.

In this case, the heat pump controller 32 calculates the target auxiliary heater output value TGQtr based on the target auxiliary heater temperature THO which is the target value of the auxiliary heater temperature Thr, and the output limit control calculates the target auxiliary heater output value TGQtr. Although it is limited, the lower limit limit value LimL is set based on the target auxiliary heater temperature THO, so the lower limit limit value LimL is the target value of the temperature of the auxiliary heater 23 before being limited by the output limit control. It will be set based on the auxiliary heater temperature THO.

As a result, the lower limit limit value LimL is not affected by the output limit control of the auxiliary heater 23. Since the lower limit limit value LimL is set based on the target auxiliary heater temperature THO, the lower limit limit value LimL is appropriately set according to the temperature of the auxiliary heater 23 required for heating to realize comfortable vehicle interior air conditioning. Will be able to.

Then, as in the embodiment, the compressor 2 for compressing the refrigerant, the radiator 4 provided in the air flow passage 3 to dissipate the refrigerant and heating the air supplied to the vehicle interior, and the air flow passage 3 are provided. In the vehicle air conditioner 1 provided with a refrigerant circuit R having a heat absorber 9 that absorbs heat from the refrigerant and cools the air supplied into the vehicle interior, the auxiliary heater 23 serves as an auxiliary heating device for the refrigerant circuit R in the air flow passage. When it is provided in 3, it becomes particularly suitable.

In the above embodiment, the lower limit value LimL of the target auxiliary heater output value TGQhtr is set to a fixed value (20 deg) as the reduction value RED for setting the target auxiliary heater temperature THO as a reference, but the present invention is not limited to this. The reduction value RED is changed according to the endothermic temperature Te (since the endothermic 9 is on the upstream side of the air of the auxiliary heater 23, the endothermic temperature Te is the temperature of the air flowing into the auxiliary heater 23) and the volume air volume Ga. By doing so, the lower limit value LimL of the target auxiliary heater output value TGQhtr may be changed according to the endothermic temperature Te and the volume air volume Ga.

In that case, the heat pump controller 32 increases the reduction value RED of the target auxiliary heater temperature THO as the heater temperature Te increases, and decreases the reduction value RED as the endothermic temperature Te decreases. Further, the smaller the volume air volume Ga, the larger the reduction value RED, and the larger the volume air volume RED, the smaller the reduction value RED. As a result, the higher the endothermic temperature Te, the lower the lower limit LimL of the target auxiliary heater output value TGQhtr, and the lower the endothermic temperature Te, the higher the lower limit LimL. Further, the smaller the volume air volume Ga, the lower the lower limit limit value LimL, and the larger the volume air volume Ga, the higher the lower limit limit value LimL.

As for the temperature of the constituent walls of the HVAC unit 10 constituting the air flow passage 3, the higher the heater temperature Te, which is the temperature of the air flowing into the auxiliary heater 23, and the smaller the volume air volume Ga, the more heat is generated by the auxiliary heater 23. It becomes easy to become high. On the contrary, the lower the heat absorber temperature Te and the larger the volume air volume Ga, the more difficult it is for the temperature of the constituent wall of the HVAC unit 10 to rise.

Therefore, as in this embodiment, the heat pump controller 32 sets the heat absorber temperature Te and the air flow passage 3 with reference to the target auxiliary heater temperature THO, which is the target value of the auxiliary heater temperature Thr output from the target temperature calculation unit 72. If the lower limit limit value LimL is changed according to the volume air volume Ga of the inflowing air, the lower limit value LimL is changed in the direction of lowering as the heat absorber temperature Te is higher or the volume air volume Ga is smaller. Therefore, the lower limit limit value LimL can be appropriately set according to the environmental conditions, and both the protection of the HVAC unit 10 by the output limit control and the stable air conditioning in the vehicle interior can be accurately realized.

In this embodiment, the lower limit value LimL of the target auxiliary heater output value TGQhtr is changed based on both the endothermic temperature Te and the volume air volume Ga, but only the endothermic temperature Te or the volume air volume Ga. It may be changed based on.

Next, FIG. 9 shows a configuration diagram of a vehicle air conditioner 1 of another embodiment to which the present invention is applied. In this figure, those shown by the same reference numerals as those in FIG. 1 have the same or similar functions. In the case of this embodiment, the outlet of the supercooling unit 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 is in the forward direction on the refrigerant pipe 13B (indoor expansion valve 8) side.

Further, the refrigerant pipe 13E on the outlet side of the radiator 4 is branched in front of the outdoor expansion valve 6, and the branched refrigerant pipe (hereinafter referred to as the second bypass pipe) 13F is the solenoid valve 22 (for dehumidification). It is communicated with the refrigerant pipe 13B on the downstream side of the check valve 18 via the check valve 18. Further, an evaporation pressure adjusting valve 70 is connected to the refrigerant pipe 13C on the outlet side of the heat absorber 9 on the downstream side of the refrigerant of the internal heat exchanger 19 and on the upstream side of the refrigerant from the confluence with the refrigerant pipe 13D. .. The solenoid valve 22 and the evaporation pressure adjusting valve 70 are also connected to the output of the heat pump controller 32. The bypass device 45 including the bypass pipe 35, the solenoid valve 30, and the solenoid valve 40 in FIG. 1 of the above-described embodiment is not provided. Others are the same as in FIG. 1, and the description thereof will be omitted.

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 and executes each operation mode of the heating mode, the dehumidifying heating mode, the internal cycle mode, the dehumidifying cooling mode, the cooling mode, and the auxiliary heater independent mode (MAX cooling mode exists in this embodiment). do not). Since the operation and the flow of the refrigerant when the heating mode, the dehumidifying cooling mode, and the cooling mode are selected, and the auxiliary heater independent mode are the same as those in the above-described embodiment (Example 1), the description thereof will be omitted. However, in this embodiment (Example 3), the solenoid valve 22 is closed in the heating mode, the dehumidifying cooling mode, and the cooling mode.

(12) Dehumidifying and heating mode of the vehicle air conditioner 1 of FIG. 9 On the other hand, when the dehumidifying and heating mode is selected, in this embodiment, the heat pump controller 32 opens the solenoid valve 21 (for heating) and the solenoid valve 17 (for heating). Close (for cooling). Also, the solenoid valve 22 (for dehumidification) is opened. Then, the compressor 2 is operated. The air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 basically blows out all the air in the air flow passage 3 that has been blown out from the indoor blower 27 and passed through the heat absorber 9 to heat the heat exchange passage 3A for heating. The auxiliary heater 23 and the radiator 4 of the above 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. Since the air in the air flow passage 3 flowing into the heat exchange passage 3A for heating is ventilated 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 radiator is heated. The heat sink in 4 is deprived of heat by air, cooled, and condensed.

The refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 via the refrigerant pipe 13E. The refrigerant that has flowed into the outdoor expansion valve 6 is decompressed there, and then flows into the outdoor heat exchanger 7. The refrigerant that has flowed into the outdoor heat exchanger 7 evaporates and draws heat by running or from the outside air that is ventilated by the outdoor blower 15. That is, the refrigerant circuit R serves as a heat pump. Then, the low-temperature refrigerant that has exited the outdoor heat exchanger 7 enters the accumulator 12 from the refrigerant pipe 13C via the refrigerant pipe 13A, the solenoid valve 21, and the refrigerant pipe 13D, and after gas-liquid separation there, the gas refrigerant is used in the compressor 2. Repeat the circulation sucked into.

Further, a part of the condensed refrigerant flowing through the refrigerant pipe 13E via the radiator 4 is diverted, and reaches the indoor expansion valve 8 from the second bypass pipe 13F and the refrigerant pipe 13B via the solenoid valve 22 via the internal heat exchanger 19. Will be. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Due to the endothermic action at this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat absorber 9, so that the air is cooled and dehumidified.

The refrigerant evaporated in the heat absorber 9 joins the refrigerant from the refrigerant pipe 13D in the refrigerant pipe 13C through the internal heat exchanger 19 and the evaporation pressure adjusting valve 70 in that order, and then is sucked into the compressor 2 through the accumulator 12. repeat. The air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, so that the dehumidifying and heating of the vehicle interior is performed.

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 target heater temperature TCO, and the target radiator pressure PCO and the refrigerant of the radiator 4 detected by the radiator pressure sensor 47. The rotation speed NC of the compressor 2 is controlled based on the pressure (radiator pressure PCI; high pressure of the refrigerant circuit R), and the heating by the radiator 4 is controlled. Further, 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. Further, the heat pump controller 32 opens / closes the evaporation pressure adjusting valve 70 (expands the flow path) / closes (a small amount of refrigerant flows) based on the temperature Te of the heat absorber 9 detected by the heat absorber temperature sensor 48. Prevents the inconvenience of freezing due to the temperature of the

(13) Internal Cycle Mode of Vehicle Air Conditioning Device 1 of FIG. 9 In the internal cycle mode, the heat pump controller 32 fully closes the outdoor expansion valve 6 (fully closed position) in the dehumidifying and heating mode. The solenoid valve 21 is closed. By closing the outdoor expansion valve 6 and the solenoid valve 21, the inflow of the refrigerant into the outdoor heat exchanger 7 and the outflow of the refrigerant from the outdoor heat exchanger 7 are prevented, so that the radiator 4 All of the condensed refrigerant flowing through the refrigerant pipe 13E flows through the solenoid valve 22 to the second bypass pipe 13F. Then, the refrigerant flowing through the second bypass pipe 13F reaches the indoor expansion valve 8 from the refrigerant pipe 13B via 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. Due to the endothermic action at this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat absorber 9, so that the air is cooled and dehumidified.

The refrigerant evaporated by the heat absorber 9 flows through the refrigerant pipe 13C in sequence through the internal heat exchanger 19 and the evaporation pressure adjusting valve 70, and repeats the circulation of being sucked into the compressor 2 through the accumulator 12. Since the air dehumidified by the endothermic 9 is reheated in the process of passing through the radiator 4, dehumidifying and heating the interior of the vehicle is performed by this, but in this internal cycle mode, the air flow on the indoor side. Since the refrigerant is circulated between the radiator 4 (heat dissipation) and the endothermic 9 (endothermic) in the path 3, the heat from the outside air is not pumped up, and the heating for the power consumed by the compressor 2 is not performed. The ability is demonstrated. Since the entire amount of the refrigerant flows through the endothermic device 9 that exerts a dehumidifying action, the dehumidifying capacity is higher than that of the dehumidifying and heating mode, but the heating capacity is lower.

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 rotation speed NC of the compressor 2 is controlled based on the refrigerant pressure (radiator pressure PCI; high pressure of the refrigerant circuit R), and the heating by the radiator 4 is controlled.

Then, even in the heating mode and the auxiliary heater independent mode (may be performed in the dehumidifying heating mode or the internal cycle mode) in the case of this embodiment, the control of the auxiliary heater 23 described in (11) described above is performed at the highest level. Even in a situation where the auxiliary heater temperature ThrMAX exceeds the limit threshold and the output limit control is performed, the inconvenience that the target auxiliary heater output value TGQhtr that controls the heat generation of the auxiliary heater 23 is lowered more than necessary is solved, and the auxiliary heater is eliminated. Auxiliary heater that detects the temperature of 23 The inconvenience that the temperature of the air supplied to the passenger compartment fluctuates greatly due to the response delay of the temperature sensors 50D, 68D, 50A, 68A is prevented, and the stable passenger compartment It will be possible to realize air conditioning.

The numerical values and the like shown in each embodiment are not limited to those, and should be appropriately set according to the device to be applied. Further, the heating device (auxiliary heating device) is not limited to the auxiliary heater 23 shown in the embodiment, and the heat medium circulation that circulates the heat medium heated by the electric heater to heat the air in the air flow passage 3. A circuit, a heater core that circulates radiator water heated by the engine, or the like may be used.

Further, in each embodiment, the auxiliary heater 23 is provided as the auxiliary heating device of the vehicle air conditioner 1 provided with the refrigerant circuit R, but the inventions other than claim 6 are not limited to this, and the refrigerant circuit R is not provided. The present invention is also effective for the vehicle air conditioner 1 that heats the vehicle interior with only the auxiliary heater 23 (heating device) in the same operation as in the case of the auxiliary heater independent mode described above.

1 Vehicle air conditioner 2 Compressor 3 Air flow passage 4 Heater 6 Outdoor expansion valve 7 Outdoor heat exchanger 8 Indoor expansion valve 9 Heat absorber 10 HVAC unit 11 Control device 20 Air conditioning controller 23 Auxiliary heater (heating device, auxiliary heating) apparatus)
27 Indoor blower (blower fan)
28 Air mix damper 32 Heat pump controller 33 Outside air temperature sensor 50D, 68D, 50A, 68A Auxiliary heater temperature sensor 65 Vehicle communication bus R Refrigerant circuit

Claims (5)

An air flow passage through which the air supplied to the passenger compartment flows, and
A heating device provided in the air flow passage to heat the air supplied to the passenger compartment, and
A temperature sensor that detects the temperature of the heating device and
A control device for controlling heat generation of the heating device based on the output of the temperature sensor is provided.
In a vehicle air conditioner that heats the air supplied into the vehicle interior by the heating device.
The control device calculates an output value TGQtr that controls heat generation of the heating device based on the target value THO of the temperature of the heating device, and the temperature Thr of the heating device detected by the temperature sensor is a predetermined limiting threshold value. In the above case, the output limit control for limiting the calculated output value TGQhr is executed, and the output limit control is executed.
An air conditioner for vehicles, characterized in that a predetermined lower limit value LimL is set in the output value TGQtr limited by the output limit control with reference to the target value THO. Equipped with a plurality of the temperature sensors
The control device outputs the output when the maximum temperature ThrMAX of the heating device, which is a detection value of the temperature sensor that detects the highest temperature among the plurality of temperature sensors, rises and reaches the limit threshold value. The limit control is entered, the output value TGQtr is lowered by a predetermined value, and thereafter, while the maximum temperature ThrMAX of the heating device is equal to or higher than the limit threshold, the output value TGQtr is lowered by a predetermined value.
The vehicle air conditioner according to claim 1, wherein the lower limit value LimL ends the decrease in the output value TGQhtr. Said control device, the temperature of the air flowing into the heating device, and / or, claim 1, characterized in that to change the lower limit value LimL depending on the volume air amount Ga of air flowing into the air flow passage Alternatively, the vehicle air conditioner according to claim 2. The third aspect of the present invention, wherein the control device changes the lower limit value LimL in the lowering direction as the temperature of the air flowing into the heating device is higher or the volume air volume Ga is smaller. Air conditioner for vehicles. A compressor that compresses the refrigerant, a radiator that is provided in the air flow passage to dissipate the refrigerant and heats the air supplied to the passenger compartment, and a radiator that is provided in the air flow passage and absorbs the refrigerant to heat the refrigerant. Equipped with a refrigerant circuit with a heat absorber that cools the air supplied to the passenger compartment,
The vehicle air conditioner according to any one of claims 1 to 4 , wherein the heating device is provided in the air flow passage as an auxiliary heating device for the refrigerant circuit.

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