JPH08282262A - Air conditioner for vehicle - Google Patents

Abstract

PURPOSE: To provide an air conditioner for a vehicle in which dehumidification capacity can be compensated even in the case where temperature of an indoor heat sink rises by effects of a car speed, etc., during dehumidification heating operation. CONSTITUTION: In the case where an evaporation temperature (EVA.S) of an indoor heat sink 3 rises over a target temperature in accordance with temperature rise of an outdoor heat exchanger 2, a flow adjusting valve 20 is throttled in accordance with temperature difference between both to decrease a refrigerant flow into the outdoor heat exchanger 2, so temperature rise of the outdoor heat exchanger 2 is restricted by this to decrease the evaporation temperature of the indoor heat sink 3. Even in the case where temperature of the outdoor heat exchanger 2 rises by effects of a car speed to rise the evaporation temperature of the indoor heat sink 3 accordingly, therefore, the evaporation temperature of the indoor heat sink 3 can be speedily decreased to a correct temperature, and its dehumidification capacity can be compensated, thereby comfortable dehumidification heating can be realized without generating frosting on window glass.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle air conditioner for dehumidifying and heating the interior of a vehicle by a heat pump.

[0002]

2. Description of the Related Art FIG. 7 shows the overall structure of a conventional vehicle air conditioner of this type. In the figure, 1 is a variable capacity electric compressor, 2 is an outdoor heat exchanger, 3 is an indoor heat absorber, 4 is an indoor radiator, 5 and 6 are temperature-sensitive expansion valves, and 7-1.
Reference numeral 0 is an electromagnetic valve, 11 and 12 are check valves, and 13 is a liquid receiver. These devices are connected by a refrigerant pipe line to form a heat pump for both heating and cooling.

Numeral 14 is an outlet temperature EVA · S of the indoor heat absorber 3.
, 15 is a temperature sensor for detecting the outlet temperature MIX · S of the indoor radiator 4, 16 is an air conditioning duct,
17 is a blower fan, 18 is an intake air switching damper, 19
Is an air mix damper, and the indoor heat absorber 3 and the indoor radiator 4 are arranged in an air conditioning duct 16.

This vehicle air conditioner includes solenoid valves 7-1.
Switching between 0 and 0 enables four modes of operation: cooling, dehumidifying cooling, heating, and dehumidifying heating. By the way, the following target outlet temperature TAO is TAO = Ks · Ts−Kr ·
It is calculated based on Tr-Kam * Tam-Krad * Trad + C, where Ks in the equation is a set temperature coefficient,
Ts is a set temperature, Kr is an inside air temperature coefficient, Tr is an inside air temperature, Kam is an outside air temperature coefficient, Tam is an outside air temperature, and Kra.
d is a solar radiation amount coefficient, Trad is a solar radiation amount, and C is a constant.

The operation in the cooling mode is executed by closing the solenoid valves 7 and 8 and opening the solenoid valves 9 and 10. The refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 2 via the electromagnetic valve 9, and flows into the indoor heat absorber 3 via the check valve 11, the liquid receiver 13, the electromagnetic valve 10 and the expansion valve 5 to be compressed. Return to machine 1. At this time, the air mix damper 19 is in the fully closed position (lower position in the figure), and the intake air from the blower fan 17 is cooled by the indoor heat absorber 3 and blown out into the vehicle interior. At this time, the outlet temperature EVA of the indoor heat absorber 3
The rotation speed of the compressor 1 is controlled so that S becomes the target outlet temperature TAO.

The operation in the dehumidifying and cooling mode is executed by closing the solenoid valve 8 and opening the solenoid valves 7, 9, 10. A part of the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 2 via the electromagnetic valve 9, and the other part of the discharged refrigerant flows into the indoor radiator 4 via the electromagnetic valve 7, and the check valves 11 and 11, respectively.
It flows into the liquid receiver 14 via 12 and flows into the indoor heat absorber 3 via the solenoid valve 10 and the expansion valve 5 and returns to the compressor 1. At this time, the opening degree of the air mix damper 19 is controlled between fully closed and fully opened based on the ratio of the outlet temperature MIX · S of the indoor radiator 4 and the target blowout temperature TAO, and the intake air by the blower fan 17 is indoors. It is cooled by the heat absorber 3, heated by the indoor radiator 4, and blown out into the vehicle interior. Further, at this time, the rotation speed of the compressor 1 is controlled so that the outlet temperature EVA · S of the indoor heat absorber 3 becomes a preset target dehumidifying temperature.

The operation in the heating mode is executed by closing the solenoid valves 9 and 10 and opening the solenoid valves 7 and 8.
The refrigerant discharged from the compressor 1 flows into the indoor radiator 4 via the solenoid valve 7, flows into the outdoor heat exchanger 2 via the check valve 12, the liquid receiver 13 and the expansion valve 6 and passes through the solenoid valve 8. Return to compressor 1. At this time, the air mix damper 19 is in the fully open position (upper position in the figure), and the intake air from the blower fan 17 is heated by the indoor radiator 4 and blown out into the vehicle interior. At this time, the outlet temperature MIX of the indoor radiator 4
The rotation speed of the compressor 1 is controlled so that S becomes the target outlet temperature TAO.

The operation in the dehumidifying and heating mode is executed by closing the solenoid valve 9 and opening the solenoid valves 7, 8 and 10. As indicated by the solid line arrow in the figure, the refrigerant discharged from the compressor 1 flows into the indoor radiator 4 via the solenoid valve 7, passes through the check valve 12 and the liquid receiver 13, and is divided into a part of the refrigerant. Flows into the indoor heat absorber 3 via the solenoid valve 10 and the expansion valve 5 and returns to the compressor 1, and the other part of the refrigerant flows into the outdoor heat exchanger 2 via the expansion valve 6 and is compressed via the solenoid valve 8. Return to machine 1. At this time, the air mix damper 19 is in the fully open position (upper position in the figure), and the intake air from the blower fan 17 is cooled by the indoor heat absorber 3 and heated by the indoor radiator 4 and blown out into the vehicle interior. At this time, the rotation speed of the compressor 1 is controlled so that the outlet temperature MIX · S of the indoor radiator 4 becomes the target outlet temperature TAO.

[0009]

By the way, the air passing through the outdoor heat exchanger 2 which functions as an evaporator during the dehumidifying and heating operation is the outside air, and the passing air volume thereof is easily influenced by the vehicle speed.
Especially when the outside air temperature is relatively high even in a heating environment,
As the vehicle speed increases, the amount of air passing through the outdoor heat exchanger 2 also increases, the amount of heat pumped in the outdoor heat exchanger 2 increases, and the temperature (evaporation temperature) rises.

On the other hand, the evaporation temperature of the indoor heat absorber 3 during the dehumidifying and heating operation changes according to the rotation speed of the compressor 1. However, since the outlets of the indoor heat exchanger 3 and the outdoor heat exchanger 2 are in communication with each other, when the temperature of the outdoor heat exchanger 2 rises as described above, the evaporation temperature of the indoor heat exchanger 3 is increased accordingly. It will be higher than the period temperature. The main purpose of the dehumidifying and heating operation is to prevent fogging of the window glass under the heating environment, but as described above, the vehicle speed increases and the indoor heat absorber 3
If the evaporation temperature of is increased, the dehumidifying capacity is reduced accordingly.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a vehicle air that can compensate the dehumidifying capacity even when the temperature of the indoor heat absorber rises due to the vehicle speed or the like during dehumidifying heating operation. To provide a harmony device.

[0012]

In order to achieve the above object, the invention of claim 1 is provided with an outdoor heat exchanger, an indoor heat absorber and an indoor radiator, and the outdoor heat exchanger and the indoor radiator perform a heat radiating action. In a heat pump type vehicle air conditioner that performs dehumidifying and heating in a vehicle interior by exhibiting heat absorbing action in each indoor heat absorber, a temperature detecting means for detecting an evaporation temperature of the indoor heat absorber during dehumidifying and heating operation, and a dehumidifying and heating operation. Refrigerant flow rate adjusting means capable of adjusting the refrigerant flow rate sometimes flowing into the outdoor heat exchanger, and when the evaporation temperature of the indoor heat absorber during dehumidifying heating operation rises above a predetermined temperature, the refrigerant flow rate adjusting means of the outdoor heat exchanger A coolant flow rate control means for reducing the coolant flow rate is provided.

As the refrigerant flow rate adjusting means, the invention of claim 2 uses a flow rate adjusting valve for adjusting the flow rate according to its opening degree, and the invention of claim 3 uses an on-off valve for adjusting the flow rate by opening and closing thereof. The invention of claim 4 uses an electronic expansion valve for adjusting the flow rate according to the opening.

[0014]

According to the present invention, when the evaporation temperature of the indoor heat absorber rises above a predetermined temperature during the dehumidifying and heating operation, the refrigerant flow rate adjusting means decreases the refrigerant flow rate of the outdoor heat exchanger. As a result, the temperature rise of the outdoor heat exchanger is suppressed, the evaporation temperature of the indoor heat absorber drops, and its dehumidifying capacity is compensated.

[0015]

【Example】

[First Embodiment] FIG. 1 shows the overall construction of a vehicle air conditioner according to a first embodiment of the present invention. The difference between the device of the present embodiment and the conventional device shown in FIG. 7 is that a motor-driven flow rate adjusting valve 20 is used in place of the open / close solenoid valve 8, and the indoor heat absorber detected by the temperature sensor 14 is used. 3 is that a controller 21 for controlling the opening of the flow rate adjusting valve 20 based on the outlet temperature EVA · S of No. 3 is provided. Since other configurations are the same as those of the conventional device, the same reference numerals are used and the description thereof is omitted.

This vehicle air conditioner includes a solenoid valve 7,
By opening and closing 9, 10 and the flow control valve 20, it is possible to perform four mode operations of cooling, dehumidifying and cooling, heating, and dehumidifying and heating. Since the refrigerant cycle of each mode operation is the same as that of the conventional device, only the operation of the dehumidifying and heating mode, which is the subject of the present invention, will be described here and the description of the other mode operations will be omitted.

The operation in the dehumidifying and heating mode is executed by closing the solenoid valve 9 and opening the solenoid valves 7 and 10 and the flow rate adjusting valve 20. As indicated by the solid arrow in the figure, the compressor 1
The refrigerant discharged from the inside flows into the indoor radiator 4 through the electromagnetic valve 7, passes through the check valve 12 and the liquid receiver 13, and is diverted.
A part of the refrigerant flows into the indoor heat absorber 3 via the solenoid valve 10 and the expansion valve 5 and returns to the compressor 1, while the other part of the refrigerant flows into the outdoor heat exchanger 2 via the expansion valve 6 and the flow control valve. Return to compressor 1 via 8. At this time, air mix damper 1
Blower fan 1 is at the fully open position (upper position in the figure).
The intake air from 7 is cooled by the indoor heat absorber 3, heated by the indoor radiator 4, and blown into the vehicle interior. At this time, the rotation speed of the compressor 1 is controlled so that the outlet temperature MIX · S of the indoor radiator 4 becomes the target outlet temperature TAO.

FIG. 2 shows a control flow of dehumidification capability compensation executed by the controller 21 during dehumidification heating operation. During the dehumidifying heating operation, the outlet temperature EVA · S of the indoor heat absorber 3 is detected, and the heat absorber outlet temperature EVA · S is detected.
The opening degree M _n of the flow rate adjusting valve 20 is determined based on the value of, and the opening degree of the flow rate adjusting valve 20 is adjusted in accordance with this. The above opening decision, for example, _{M n = M n-1 -K} 1 {(E n -E n-1)
+ K ₂ · E _n } is used. In the equation, M _n is the opening of the flow rate control valve 20, M _n-1 is the previous M _n , E _n is a value obtained by the heat absorber actual temperature−heat absorber target temperature, and E _n-1 is the previous E. _n , K
₁ and K ₂ are coefficients, and the value of EVA · S is used as the actual heat absorber temperature, and the predetermined temperature is used as the heat absorber target temperature.

That is, when the evaporation temperature (EVA.S) of the indoor heat absorber 3 rises above the heat absorber target temperature as the temperature of the outdoor heat exchanger 2 rises, the flow rate is adjusted according to the temperature difference between the two. The flow rate of the refrigerant flowing into the outdoor heat exchanger 2 is reduced by narrowing down the valve 20, thereby suppressing the pumping amount of heat of the outdoor heat exchanger 2 and lowering the evaporation temperature of the indoor heat absorber 3.

Therefore, even if the temperature of the outdoor heat exchanger 2 rises due to the influence of the vehicle speed and the evaporation temperature of the indoor heat absorber 3 rises accordingly, the evaporation temperature of the indoor heat absorber 3 is set to the proper temperature. The temperature can be quickly lowered to compensate for the dehumidifying capacity, and comfortable dehumidifying heating without fogging on the window glass can be realized.

In the present embodiment, the heat absorber outlet temperature EVA · S detected by the temperature sensor 14 is used as the indoor heat absorber 3
Although it is used as the actual evaporation temperature of the above, the temperature may be substituted by the fin temperature of the indoor heat absorber 3 or the inlet refrigerant temperature, and the refrigerant pressure may be used as an alternative value of the temperature.

Further, if the heat absorber target temperature is set to a lower limit temperature (for example, 3 ° C.) at which the heat absorber does not frost, the maximum dehumidifying ability can be obtained, and the dehumidifying ability necessary and sufficient for preventing fogging of the window glass is set. For this purpose, a function of the outside air temperature and the inside air temperature (for example, target temperature = K ₅ · Tam + K ₆ · Tr, K ₅ and K ₆ are coefficients) may be obtained.

[Second Embodiment] FIG. 3 shows the overall construction of a vehicle air conditioner according to a second embodiment of the present invention. The difference between the apparatus of this embodiment and the conventional apparatus shown in FIG. 7 is that a controller 22 for controlling opening / closing of the solenoid valve 8 based on the outlet temperature EVA · S of the indoor heat absorber 3 detected by the temperature sensor 14 is provided. There is a point. Since other configurations are the same as those of the conventional device, the same reference numerals are used and the description thereof is omitted.

This vehicle air conditioner includes solenoid valves 7-1.
Switching between 0 and 0 enables four modes of operation: cooling, dehumidifying cooling, heating, and dehumidifying heating. Since the refrigerant cycle of each mode operation is the same as that of the conventional device, only the operation of the dehumidifying and heating mode, which is the subject of the present invention, will be described here and the description of the other mode operations will be omitted.

The operation in the dehumidifying and heating mode is executed by closing the solenoid valve 9 and opening the solenoid valves 7, 8 and 10. As indicated by the solid line arrow in the figure, the refrigerant discharged from the compressor 1 flows into the indoor radiator 4 via the solenoid valve 7, passes through the check valve 12 and the liquid receiver 13, and is divided into a part of the refrigerant. Flows into the indoor heat absorber 3 via the solenoid valve 10 and the expansion valve 5 and returns to the compressor 1, and the other part of the refrigerant flows into the outdoor heat exchanger 2 via the expansion valve 6 and is compressed via the solenoid valve 8. Return to machine 1. At this time, the air mix damper 19 is in the fully open position (upper position in the figure), and the intake air from the blower fan 17 is cooled by the indoor heat absorber 3 and heated by the indoor radiator 4 and blown out into the vehicle interior. At this time, the rotation speed of the compressor 1 is controlled so that the outlet temperature MIX · S of the indoor radiator 4 becomes the target outlet temperature TAO.

FIG. 4 (a) shows a control flow of dehumidification capability compensation executed by the controller 22 during dehumidification heating operation. Indoor heat absorber 3 during dehumidification heating operation
Outlet temperature EVA · S of the
The opening / closing of the solenoid valve 8 is determined based on the values of A and S, and the opening / closing of the solenoid valve 8 is adjusted accordingly. The above opening / closing decision is as shown in FIG. 4 (b), and the heat absorber outlet temperature EVA · S
From the value higher than the first set temperature Ta to the second set temperature Tb
Until it reaches the end, the heat absorber outlet temperature EVA is selected.
Open is selected from a value of S lower than the second set temperature Tb to the first set temperature Ta. Incidentally, the first set temperature Ta is an upper limit temperature for accurately performing dehumidification, and the second set temperature Tb is a temperature lower than this.

That is, when the evaporation temperature (EVA · S) of the indoor heat absorber 3 rises above the first set temperature Ta as the temperature of the outdoor heat exchanger 2 rises, the solenoid valve 8 is changed from open to closed. By switching the flow rate of the refrigerant flowing into the outdoor heat exchanger 2 to zero, the amount of heat pumped up by the outdoor heat exchanger 2 is suppressed and the evaporation temperature of the indoor heat absorber 3 is lowered.

Therefore, even when the temperature of the outdoor heat exchanger 2 rises due to the influence of the vehicle speed and the evaporation temperature of the indoor heat absorber 3 rises accordingly, the evaporation temperature of the indoor heat absorber 3 is set to the proper temperature. The temperature can be quickly lowered to compensate for the dehumidifying capacity, and comfortable dehumidifying heating without fogging on the window glass can be realized.

In the present embodiment, the heat absorber outlet temperature EVA · S detected by the temperature sensor 14 is used as the indoor heat absorber 3
Although it is used as the actual evaporation temperature of the above, the temperature may be substituted by the fin temperature of the indoor heat absorber 3 or the inlet refrigerant temperature, and the refrigerant pressure may be used as an alternative value of the temperature.

Further, if the first set temperature is set to a lower limit temperature (for example, 3 ° C.) at which the heat absorber does not frost, the maximum dehumidifying ability can be obtained, and the dehumidifying ability necessary and sufficient for preventing fogging of the window glass is set. For this purpose, a function of the outside air temperature and the inside air temperature (for example, target temperature = K ₅ · Tam + K ₆ · Tr, K ₅ and K ₆ are coefficients) may be obtained.

[Third Embodiment] FIG. 5 shows the overall construction of a vehicle air conditioner according to a third embodiment of the present invention. The difference between the device of the present embodiment and the conventional device shown in FIG. 7 is that an electronic expansion valve 23 that can change the throttle opening degree by an external command is used instead of the temperature-sensitive expansion valve 6, and the outdoor heat Temperature sensor 2 for detecting refrigerant temperature T1 on the outlet side of exchanger 2
4 and a point at which a temperature sensor 25 for detecting the inlet side refrigerant temperature T2 is provided, and the outlet side refrigerant temperature T1 and the inlet side refrigerant temperature T2.
The first controller 26 that controls the opening degree of the electronic expansion valve 23 so as to obtain a target superheat degree SH _n described later based on
And the target superheat degree S based on the outlet temperature EVA · S of the indoor heat absorber 3 detected by the temperature sensor 14.
The second controller 27 is provided to determine H _n and send it to the first controller 26. Since other configurations are the same as those of the conventional device, the same reference numerals are used and the description thereof is omitted.

This vehicle air conditioner includes solenoid valves 7-1.
Switching between 0 and 0 enables four modes of operation: cooling, dehumidifying cooling, heating, and dehumidifying heating. Since the refrigerant cycle of each mode operation is the same as that of the conventional device, only the operation of the dehumidifying and heating mode, which is the subject of the present invention, will be described here and the description of the other mode operations will be omitted.

The operation in the dehumidifying and heating mode is executed by closing the solenoid valve 9 and opening the solenoid valves 7, 8 and 10. As indicated by the solid line arrow in the figure, the refrigerant discharged from the compressor 1 flows into the indoor radiator 4 via the solenoid valve 7, passes through the check valve 12 and the liquid receiver 13, and is divided into a part of the refrigerant. Flows into the indoor heat absorber 3 through the solenoid valve 10 and the expansion valve 5 and returns to the compressor 1, and the other part of the refrigerant flows into the outdoor heat exchanger 2 through the electronic expansion valve 23 and through the solenoid valve 8. Return to compressor 1. At this time, the air mix damper 19 is in the fully open position (upper position in the figure), the intake air from the blower fan 17 is cooled by the indoor heat absorber 3, and the indoor radiator 4
It is heated by and is blown out into the passenger compartment. Further, at this time, the outlet temperature MIX · S of the indoor radiator 4 is the target outlet temperature TA.
The number of rotations of the compressor 1 is controlled so that it becomes O.

FIG. 6A shows a control flow of the dehumidifying capacity compensation executed by the second controller 27 during the dehumidifying and heating operation. During the dehumidifying and heating operation, the outlet temperature EVA · S of the indoor heat absorber 3 is detected, and the target superheat degree SH _n is determined based on the value of the heat absorber outlet temperature EVA · S.
This is sent to the first controller 26. For example, SH _n = SH _n-1 + K ₃ {(E _n −E
_n-1 ) + K ₄ · E _n } is used. In the equation, SH _n is the target superheat degree, SH _n-1 is the previous SH _n , E _n is the value obtained by the heat absorber actual temperature-heat absorber target temperature, E _n-1 is the last E _n ,
K ₃ and K ₄ are coefficients, and the actual temperature of the heat absorber is EVA ・ S
, And a predetermined temperature is used as the heat absorber target temperature.

FIG. 6B shows the electronic expansion valve 2 implemented by the first controller 26 during the dehumidifying and heating operation.
3 shows a control flow for adjusting the opening degree of No. 3. Dehumidification heating operation, the outlet side refrigerant temperature T1 and the inlet side refrigerant temperature T2 of the outdoor heat exchanger 2 and each of the detection, the actual superheat SH _r (= T1-
The opening degree of the electronic expansion valve 23 is adjusted so that T2) becomes the target superheat degree SH _n .

That is, when the evaporation temperature (EVA · S) of the indoor heat absorber 3 rises above the target temperature as the temperature of the outdoor heat exchanger 2 rises, the target superheat degree SH is set according to the temperature difference between the two. _While changing _n to a high value, the electronic expansion valve 23 is narrowed down so that the actual superheat degree SH _r becomes the target superheat degree SH _n, and the flow rate of the refrigerant flowing into the outdoor heat exchanger 2 is reduced,
Thereby, the temperature rise of the outdoor heat exchanger 2 is suppressed and the evaporation temperature of the indoor heat absorber 3 is lowered.

Therefore, even when the temperature of the outdoor heat exchanger 2 rises due to the influence of the vehicle speed and the evaporation temperature of the indoor heat absorber 3 rises accordingly, the evaporation temperature of the indoor heat absorber 3 is set to an appropriate temperature. The temperature can be quickly lowered to compensate for the dehumidifying capacity, and comfortable dehumidifying heating without fogging on the window glass can be realized.

In the present embodiment, the heat absorber outlet temperature EVA · S detected by the temperature sensor 14 is used as the indoor heat absorber 3
Although it is used as the actual evaporation temperature of the above, the temperature may be substituted by the fin temperature of the indoor heat absorber 3 or the inlet refrigerant temperature, and the refrigerant pressure may be used as an alternative value of the temperature.

Further, if the heat absorber target temperature is set to the lower limit temperature (for example, 3 ° C.) at which the heat absorber does not frost, the maximum dehumidifying ability is obtained, and the dehumidifying ability necessary and sufficient for preventing fogging of the window glass is set. For this purpose, a function of the outside air temperature and the inside air temperature (for example, target temperature = K ₅ · Tam + K ₆ · Tr, K ₅ and K ₆ are coefficients) may be obtained.

[0040]

As described in detail above, according to the inventions of claims 1 to 4, the temperature of the outdoor heat exchanger rises due to the influence of the vehicle speed, and the evaporation temperature of the indoor heat absorber rises accordingly. Even in such a case, the evaporation temperature of the indoor heat absorber can be quickly lowered to an appropriate temperature by reducing the flow rate of the refrigerant flowing to the outdoor heat exchanger, thereby compensating the dehumidifying capacity and providing comfortable dehumidifying heating with no fog on the window glass. Can be done.

[Brief description of drawings]

FIG. 1 is a diagram showing an overall configuration of a vehicle air conditioner according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a control flow of dehumidification capacity compensation according to the first embodiment.

FIG. 3 is a diagram showing an overall configuration of a vehicle air conditioner according to a second embodiment of the present invention.

FIG. 4 is a diagram showing a control flow of dehumidification capability compensation according to the second embodiment and a diagram showing a relationship between EVA / S and opening / closing of a solenoid valve.

FIG. 5 is a diagram showing an overall configuration of a vehicle air conditioner according to a third embodiment of the present invention.

FIG. 6 is a diagram showing a control flow of dehumidification capacity compensation according to a third embodiment and a diagram showing a control flow of expansion valve opening adjustment.

FIG. 7 is a diagram showing an overall configuration of a conventional vehicle air conditioner.

[Explanation of symbols]

1 ... Compressor, 2 ... Outdoor heat exchanger, 3 ... Indoor heat absorber, 4 ...
Indoor radiator, 5, 6 ... Expansion valve, 7-10 ... Solenoid valve, 1
1, 12 ... Check valve, 13 ... Liquid receiver, 14 ... Temperature sensor,
15 ... Temperature sensor, 16 ... Air conditioning duct, 17 ... Blower fan, 18 ... Intake air switching damper, 19 ... Air mix damper, 20 ... Flow control valve, 21 ... Controller, 22
... controller, 23 ... electronic expansion valve, 24 ... temperature sensor, 25 ... temperature sensor, 26 ... controller, 27 ... controller.

Claims (4)

[Claims] 1. Dehumidifying and heating the interior of a vehicle by providing an outdoor heat exchanger, an indoor heat absorber, and an indoor radiator, and making the outdoor heat exchanger and the indoor heat absorber exert heat absorbing action and the indoor heat radiator exerting heat radiating action, respectively. In a heat pump type air conditioner for a vehicle to perform, temperature detection means for detecting the evaporation temperature of the indoor heat absorber during dehumidification heating operation, and refrigerant flow rate adjustment means capable of adjusting the refrigerant flow rate flowing into the outdoor heat exchanger during dehumidification heating operation A refrigerant flow rate control means for reducing the refrigerant flow rate of the outdoor heat exchanger by the refrigerant flow rate adjustment means when the evaporation temperature of the indoor heat absorber rises above a predetermined temperature during the dehumidifying and heating operation. Vehicle air conditioner. 2. The air conditioner for a vehicle according to claim 1, wherein the refrigerant flow rate adjusting means is a flow rate adjusting valve that adjusts the flow rate according to its opening degree. 3. The vehicle air conditioner according to claim 1, wherein the refrigerant flow rate adjusting means is an on-off valve that adjusts the flow rate by opening and closing the refrigerant flow rate adjusting means. 4. The air conditioner for a vehicle according to claim 1, wherein the refrigerant flow rate adjusting means is an electronic expansion valve that adjusts the flow rate according to its opening degree.