JP2022051624A - Air conditioner - Google Patents

Abstract

An air conditioner capable of appropriately returning refrigerating machine oil to a compressor while obtaining the effect of improving operating efficiency by providing a heat exchange section having an adsorption section is provided. SOLUTION: In a dehumidification heating mode of a vehicle air conditioner 1, a refrigerant discharged from a compressor 11 is supplied to an indoor condenser 12, a first expansion valve 14a, an indoor evaporator 15 having a desiccant material 15a, and an outdoor heat exchanger. 16. Switch to the refrigerant circuit of the refrigeration cycle device 10 so as to circulate in order from the suction side of the compressor. In the dehumidifying heating mode, the desiccant material 15a uses the adsorption action to dehumidify the blown air. In the defrosting mode, the refrigerant discharged from the compressor 11 is circulated through the indoor condenser 12, the outdoor heat exchanger 16, the second expansion valve 14b, the indoor evaporator 15, and the suction side of the compressor in this order. Switch to the refrigerant circuit of the cycle device 10 . In the defrost mode, the indoor condenser 12 reheats the blown air. [Selection drawing] Fig. 1

Description

The present invention relates to an air conditioner including a heat exchange unit having an adsorption unit.

Conventionally, Patent Document 1 discloses a vehicle air conditioner applied to an electric vehicle. The vehicle air conditioner of Patent Document 1 has a steam compression type refrigeration cycle device that adjusts the temperature of the blown air blown into the vehicle interior, which is the space to be air-conditioned.

The refrigeration cycle device of Patent Document 1 is provided with a plurality of heat exchangers, and is configured to be able to switch the refrigerant circuit according to the operation mode. For example, in the dehumidifying / heating mode for dehumidifying and heating the interior of the vehicle, the heat exchanger for temperature adjustment functions as a condenser, and the heat exchanger for humidity control and the outdoor heat exchanger are switched to a refrigerant circuit that functions as an evaporator. ..

As a result, in the vehicle air conditioner of Patent Document 1, the blown air cooled and dehumidified by the heat exchanger for humidity adjustment is reheated by the heat exchanger for temperature adjustment and blown out into the vehicle interior. This realizes dehumidifying and heating the interior of the vehicle.

Further, in the vehicle air conditioner of Patent Document 1, as a heat exchanger for adjusting humidity, a heat exchange unit having an adsorption unit for adsorbing moisture contained in blown air (specifically, a desiccant material is applied to the outer surface). The heat exchanger) has been adopted. Then, in the dehumidifying / heating mode, the inside air, which is hotter and more humid than the outside air as the blown air, is guided to the heat exchanger for humidity adjustment, and the moisture contained in the blown air is adsorbed on the adsorption portion.

As a result, in the vehicle air conditioner of Patent Document 1, the energy consumed for dehumidifying the blown air is reduced in the dehumidifying / heating mode, and the operating efficiency is improved.

Further, Patent Document 2 discloses an air conditioning system having a refrigeration cycle device. The refrigeration cycle device of Patent Document 2 includes an indoor heat exchanger and an outdoor heat exchanger, and is configured to be able to switch the refrigerant circuit according to the operation mode. Further, in the air conditioning system of Cited Document 2, a heat exchange unit having an adsorption unit similar to that of Patent Document 1 is adopted as the indoor heat exchanger.

The refrigeration cycle device of Patent Document 2 switches to a refrigerant circuit in which the indoor heat exchanger functions as a condenser and the outdoor heat exchanger functions as an evaporator in the heating mode for heating the room. Further, in the defrosting mode for removing frost on the outdoor heat exchanger, the outdoor heat exchanger is switched to a refrigerant circuit that functions as a condenser, and the indoor heat exchanger is switched to a refrigerant circuit that functions as an evaporator.

Further, in the air conditioning system of Patent Document 2, in the defrosting mode, the heat of adsorption when the adsorption part of the indoor heat exchanger adsorbs the moisture contained in the blown air is removed by melting the frost attached to the outdoor heat exchanger. It is used as a heat source for.

As a result, the air-conditioning system of Patent Document 2 attempts to prevent the temperature of the air-conditioned space from dropping when the heating mode is switched to the defrosting mode.

Japanese Unexamined Patent Publication No. 2018-176936 JP-A-2019-66090

By the way, even in the vehicle air conditioner of Patent Document 1, frost may occur in the outdoor heat exchanger that functions as an evaporator in the dehumidifying / heating mode. Therefore, it is conceivable that the vehicle air conditioner of Patent Document 1 also operates in the same defrosting mode as the air conditioner system of Patent Document 2.

Specifically, in the refrigeration cycle device of Patent Document 1, it is conceivable to switch to a refrigerant circuit in which the outdoor heat exchanger functions as a condenser and the heat exchanger for humidity control functions as an evaporator in the defrosting mode. Be done. Then, in order to suppress the temperature drop of the blown air when switching from the dehumidifying heating mode to the defrosting mode, it is conceivable to defrost the outdoor heat exchanger using the heat adsorbed in the adsorption part of the indoor heat exchanger as a heat source. Be done.

Here, in order to suppress the decrease in temperature of the air-conditioned space after switching from the dehumidifying / heating mode to the defrosting mode, it is necessary to suppress the decrease in the evaporation temperature of the refrigerant in the indoor heat exchanger. For that purpose, it is desirable to reduce the rotation speed of the compressor after switching from the dehumidifying / heating mode to the defrosting mode.

However, the required refrigerant flow rate in which the cycle needs to be circulated in the dehumidification mode is smaller than the required refrigerant flow rate in the dehumidification / heating mode. Therefore, if the number of revolutions of the compressor of the refrigeration cycle device is reduced in the dehumidification mode in order to suppress the temperature drop of the blown air after switching from the dehumidification / heating mode to the defrosting mode, the refrigerant is mixed. It may not be possible to return the freezing machine oil to the compressor.

That is, in the vehicle air conditioner of Patent Document 1, in the dehumidifying / heating mode, it is possible to improve the operating efficiency by the adsorption action of the adsorption portion, but when the operation in the dehumidifying mode is executed, the compressor is appropriately frozen. The machine oil cannot be returned. As a result, the durable life of the compressor may be adversely affected.

In view of the above points, it is an object of the present invention to provide an air conditioner capable of appropriately returning refrigerating machine oil to a compressor while obtaining an effect of improving operating efficiency by providing a heat exchange unit having an adsorption unit. do.

In order to achieve the above object, the air conditioner according to claim 1 includes a compressor (11), a heating unit (12, 12a, 40), a first decompression unit (14a), and a second decompression unit (14b). ), An air cooling heat exchange unit (15), an outdoor heat exchange unit (16), and a refrigerant circuit switching unit (13).

The compressor compresses and discharges the refrigerant mixed with the refrigerating machine oil. The heating unit heats the blown air blown to the air-conditioned space using the refrigerant discharged from the compressor as a heat source. The first decompression section and the second decompression section depressurize the refrigerant. The air cooling heat exchange unit evaporates the refrigerant and cools the blown air before being heated by the heating unit. The outdoor heat exchange unit exchanges heat between the refrigerant and the outside air. The refrigerant circuit switching unit switches the refrigerant circuit that circulates the refrigerant.

The air cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air.

The refrigerant circuit switching unit heats the refrigerant discharged from the compressor in the dehumidifying / heating mode for dehumidifying and heating the air-conditioned space, the heating unit, the first decompression unit, the air cooling heat exchange unit, the outdoor heat exchange unit, and the compressor. Switch to the refrigerant circuit that circulates in the order of the suction side. Further, in the defrosting mode for removing the frost on the outdoor heat exchange unit, the refrigerant discharged from the compressor is used in the heating unit, the outdoor heat exchange unit, the second decompression unit, the air cooling heat exchange unit, and the compressor. Switch to the refrigerant circuit that circulates in the order of the suction side.

According to this, when the refrigerant circuit switching unit (13) switches to the refrigerant circuit in the dehumidifying / heating mode, the heating unit (12, 12a, 40) functions as a condenser, and the air cooling heat exchange unit (15). ) And the outdoor heat exchange unit (16) can be configured as a steam compression type refrigeration cycle that functions as an evaporator.

Then, the blown air cooled and dehumidified by the air cooling heat exchange unit (15) is reheated by the heating unit (12, 12a, 40) and blown out to the air-conditioned space to dehumidify the air-conditioned space. Can be heated.

Further, the air cooling heat exchange unit (15) has an adsorption unit (15a). Therefore, in the dehumidifying / heating mode, it is possible to dehumidify the blown air by utilizing the adsorption action of the adsorption portion (15a). As a result, the power consumption of the compressor (11) can be reduced, and the operating efficiency of the air conditioner as a whole can be improved.

Further, when the refrigerant circuit switching unit (13) is switched to the defrosting mode refrigerant circuit, the heating unit (12, 12a, 40) and the outdoor heat exchange unit (16) are made to function as a condenser to cool the air. The heat exchange unit (15) can function as an evaporator. Therefore, the frost on the outdoor heat exchange unit (16) can be melted and removed.

Further, in the defrosting mode, the high-temperature refrigerant discharged from the compressor (11) is made to flow into the heating unit (12, 12a, 40). Therefore, even if the blown air is cooled by the air cooling heat exchange unit (15) in the defrosting mode, it can be reheated by the heating unit (12, 12a, 40). As a result, the temperature drop in the air-conditioned space can be suppressed even if the rotation speed of the compressor (11) is determined so that the refrigerating machine oil can be appropriately returned to the compressor (11).

That is, according to the air conditioner according to claim 1, the compressor oil is compressed (11) while obtaining the effect of improving the operating efficiency by providing the air cooling heat exchange unit (15) having the adsorption unit (15a). ) Can be properly returned.

The air conditioner according to claim 2 includes a compressor (11), a heating unit (12, 12a, 40), a branch unit (17a), an outdoor decompression unit (14c), and an outdoor heat exchange. Section (16), cooling decompression section (14d, 14e), cooling heat exchange section (15, 19), pressure adjustment section (20), merging section (17g), refrigerant circuit switching section (13a). ... 13d) and.

The compressor compresses and discharges the refrigerant mixed with the refrigerating machine oil. The heating unit heats the blown air blown to the air-conditioned space using the refrigerant discharged from the compressor as a heat source. The branching portion branches the flow of the refrigerant flowing out from the heating portion. The outdoor decompression unit and the cooling decompression unit decompress the refrigerant. The outdoor heat exchange unit exchanges heat between the refrigerant decompressed by the outdoor decompression unit and the outside air. The cooling heat exchange unit evaporates the refrigerant decompressed by the cooling decompression unit in order to cool the object to be cooled. The pressure adjusting unit adjusts at least one of the refrigerant pressure in the cooling heat exchange unit and the refrigerant pressure in the outdoor heat exchange unit. The merging section merges the flow of the refrigerant flowing out from the cooling heat exchange section and the flow of the refrigerant flowing out from the outdoor heat exchange section and flows out to the suction side of the compressor. The refrigerant circuit switching unit switches the refrigerant circuit that circulates the refrigerant.

The cooling heat exchange unit has an air cooling heat exchange unit (15) for cooling the blown air before being heated by the heating unit. The air cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air. The cooling decompression unit has an air cooling decompression unit (14d) that decompresses the refrigerant flowing into the air cooling heat exchange unit.

The refrigerant circuit switching unit compresses the refrigerant discharged from the compressor in the heating unit, branch unit, air cooling decompression unit, air cooling heat exchange unit, confluence unit, and compression unit during the dehumidification / heating mode for dehumidifying and heating the air-conditioned space. Circulate in the order of the suction side of the machine. At the same time, the refrigerant discharged from the compressor is switched to a refrigerant circuit that circulates in the order of the heating part, the branch part, the outdoor decompression part, the outdoor heat exchange part, the merging part, and the suction side of the compressor. Further, in the defrosting mode for removing the frost on the outdoor heat exchange unit, the refrigerant discharged from the compressor is used in the heating unit, the outdoor heat exchange unit, the cooling decompression unit, the cooling heat exchange unit, and the compressor. Switch to the refrigerant circuit that circulates in the order of the suction side.

According to this, when the refrigerant circuit switching unit (13a ... 13d) switches to the refrigerant circuit in the dehumidifying / heating mode, the heating unit (12, 12a, 40) functions as a condenser, and the air cooling heat exchange unit is used. A steam compression type refrigeration cycle can be configured in which the (15) and the outdoor heat exchange unit (16) function as an evaporator.

Then, the blown air cooled and dehumidified by the air cooling heat exchange unit (15) is reheated by the heating unit (12, 12a, 40) and blown out to the air-conditioned space to dehumidify the air-conditioned space. Can be heated.

Further, the air cooling heat exchange unit (15) has an adsorption unit (15a). Therefore, in the dehumidifying / heating mode, it is possible to dehumidify the blown air by utilizing the adsorption action of the adsorption portion (15a). As a result, the power consumption of the compressor (11) can be reduced, and the operating efficiency of the air conditioner as a whole can be improved.

Further, when the refrigerant circuit switching unit (13a ... 13d) is switched to the defrosting mode refrigerant circuit, the heating unit (12, 12a, 40) and the outdoor heat exchange unit (16) are made to function as a condenser. The cooling heat exchange unit (15, 19) can function as an evaporator. Therefore, the frost on the outdoor heat exchange unit (16) can be melted and removed.

Further, in the defrosting mode, the high-temperature refrigerant discharged from the compressor (11) is made to flow into the heating unit (12, 12a, 40). Therefore, even if the blown air is cooled by the air cooling heat exchange unit (15) in the defrosting mode, it can be reheated by the heating unit (12, 12a, 40). As a result, even if the rotation speed of the compressor (11) is determined so that the refrigerating machine oil can be appropriately returned to the compressor (11), the temperature drop in the air-conditioned space can be suppressed.

That is, according to the air conditioner according to claim 2, the compressor oil is compressed (11) while obtaining the effect of improving the operating efficiency by providing the air cooling heat exchange unit (15) having the adsorption unit (15a). ) Can be properly returned.

The air conditioner according to claim 4 includes a compressor (11), a heating unit (12a, 40a), a branch unit (17d), an air cooling pressure reducing unit (14d), and an air cooling heat exchange. Section (15), low temperature side heat medium circuit (50a), heat medium cooling decompression section (14e), heat medium cooling heat exchange section (19), pressure adjustment section (20), and confluence section ( 17 g), a low temperature side outside air heat exchange unit (54), and a heat quantity distribution unit (43).

The compressor compresses and discharges the refrigerant mixed with the refrigerating machine oil. The heating unit heats the blown air blown to the air-conditioned space using the refrigerant discharged from the compressor as a heat source. The branching portion branches the flow of the refrigerant flowing out from the heating portion. The air cooling decompression section decompresses one of the refrigerants branched at the branch section. The air cooling heat exchange unit evaporates the refrigerant decompressed by the air cooling decompression unit and cools the blown air before being heated by the heating unit. The low temperature side heat medium circuit circulates the low temperature side heat medium. The heat medium cooling decompression section decompresses the other refrigerant branched at the branch section. The heat exchange unit for cooling the heat medium exchanges heat between the refrigerant decompressed by the decompression unit for cooling the heat medium and the heat medium on the low temperature side. The pressure adjusting unit adjusts at least one of the refrigerant pressure in the air cooling heat exchange unit and the refrigerant pressure in the heat medium cooling heat exchange unit. The merging section merges the flow of the refrigerant flowing out of the air cooling heat exchange section with the flow of the refrigerant flowing out of the heat medium cooling heat exchange section and causes them to flow out to the suction side of the compressor. The low temperature side outside air heat exchange unit is arranged in the low temperature side heat medium circuit to exchange heat between the low temperature side heat medium and the outside air. The heat amount distribution unit distributes the amount of heat supplied to the heating unit and the amount of heat supplied to the low temperature side outside air heat exchange unit among the heat contained in the refrigerant discharged from the compressor.

The air cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air.

The heat distribution unit supplies the heat of the refrigerant discharged from the compressor to the heating unit in the dehumidifying / heating mode in which the air-conditioned space is dehumidified and heated. Further, in the defrosting mode for removing frost on the low temperature side outside air heat exchange section, the amount of heat supplied to the low temperature side outside air heat exchange section is increased as compared with the dehumidifying heating mode.

According to this, in the dehumidifying and heating mode, the heat quantity distribution unit (43) supplies the heat of the refrigerant discharged from the compressor to the heating unit. Therefore, in the dehumidifying / heating mode, the blast air cooled and dehumidified by the air cooling heat exchange unit (15) is reheated by the heating unit (12a, 40a) and blown out to the air-conditioned space to be air-conditioned. It is possible to dehumidify and heat the space.

Further, the air cooling heat exchange unit (15) has an adsorption unit (15a). Therefore, in the dehumidifying / heating mode, it is possible to dehumidify the blown air by utilizing the adsorption action of the adsorption portion (15a). As a result, the power consumption of the compressor (11) can be reduced, and the operating efficiency of the air conditioner as a whole can be improved.

Further, in the dehumidification mode, the heat amount distribution unit (43) increases the amount of heat supplied to the low temperature side outside air heat exchange unit (54) as compared with the dehumidification / heating mode. Therefore, the frost on the low temperature side outside air heat exchange unit (54) can be melted and removed.

Further, in the defrosting mode, the heat distribution unit (43) can also supply heat to the heating unit (12a, 40a). Therefore, even if the blown air is cooled by the air cooling heat exchange unit (15) in the defrosting mode, it can be reheated by the heating unit (12a, 40a). As a result, even if the rotation speed of the compressor (11) is determined so that the refrigerating machine oil can be appropriately returned to the compressor (11), the temperature drop in the air-conditioned space can be suppressed.

That is, according to the air conditioner according to claim 4, the compressor oil is compressed (11) while obtaining the effect of improving the operating efficiency by providing the air cooling heat exchange unit (15) having the adsorption unit (15a). ) Can be properly returned.

It should be noted that the reference numerals in parentheses of each means described in this column and the scope of claims are examples showing the correspondence with the specific means described in the embodiments described later.

It is an overall block diagram of the vehicle air conditioner of 1st Embodiment. It is a block diagram which shows the electric control part of the air-conditioning apparatus for a vehicle of 1st Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant at the time of the adsorption process of the dehumidifying heating mode in the refrigerating cycle apparatus of 1st Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant at the time of the dehumidifying heating mode dehumidification heating mode in the refrigerating cycle apparatus of 1st Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant in the defrosting mode in the refrigerating cycle apparatus of 1st Embodiment. It is an overall block diagram which shows the flow of the refrigerant, etc. in the cooling mode and the defrosting mode of the vehicle air conditioner of the 2nd Embodiment. It is an overall block diagram which shows the flow of the refrigerant in the dehumidifying heating mode of the vehicle air-conditioning apparatus of 2nd Embodiment. It is a block diagram which shows the electric control part of the air-conditioning apparatus for vehicles of 2nd Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant at the time of the adsorption stroke of the single dehumidification heating mode in the refrigerating cycle apparatus of 2nd Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant at the time of the dehumidifying heating mode dehumidification heating mode in the refrigerating cycle apparatus of 2nd Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant in the single defrosting mode in the refrigerating cycle apparatus of 2nd Embodiment. It is an overall block diagram which shows the flow of the refrigerant, etc. in the cooling mode and the defrosting mode of the vehicle air conditioner of the 3rd Embodiment. It is an overall block diagram which shows the flow of the refrigerant in the dehumidifying heating mode of the vehicle air-conditioning apparatus of 3rd Embodiment. It is an overall block diagram which shows the flow of the refrigerant and the heat medium in the single cooling mode and the single defrosting mode of the vehicle air conditioner of the fourth embodiment. It is an overall block diagram which shows the flow of the refrigerant and the heat medium in the cooling cooling mode and the waste heat defrosting mode of the vehicle air conditioner of 4th Embodiment. It is an overall block diagram which shows the flow of the refrigerant and the heat medium at the time of the adsorption process of the single dehumidifying heating mode of the vehicle air-conditioning apparatus of 4th Embodiment. It is an overall block diagram which shows the flow of the refrigerant and the heat medium at the time of the dehumidification process of the single dehumidifying heating mode of the vehicle air-conditioning apparatus of 4th Embodiment. It is an overall block diagram which shows the flow of the refrigerant and the heat medium at the time of the adsorption process of the cooling dehumidification heating mode of the vehicle air-conditioning apparatus of 4th Embodiment. It is an overall block diagram which shows the flow of the refrigerant and the heat medium at the time of the desorption stroke of the cooling dehumidification heating mode of the vehicle air-conditioning apparatus of 4th Embodiment. It is a block diagram which shows the electric control part of the air-conditioning apparatus for a vehicle of 4th Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant at the time of the adsorption stroke of the single dehumidification heating mode in the refrigerating cycle apparatus of 4th Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant at the time of the dehumidifying heating mode dehumidification heating mode in the refrigerating cycle apparatus of 4th Embodiment. It is a Moriel diagram which shows the change of the state of the refrigerant in the single defrosting mode in the refrigerating cycle apparatus of 4th Embodiment.

Hereinafter, a plurality of embodiments for carrying out the present invention will be described with reference to the drawings. In each embodiment, the same reference numerals may be given to the parts corresponding to the matters described in the preceding embodiments, and duplicate explanations may be omitted. When only a part of the configuration is described in each embodiment, other embodiments described above can be applied to the other parts of the configuration. Not only the combination of the parts that clearly indicate that the combination is possible in each embodiment, but also the partial combination of the embodiments even if the combination is not specified if there is no problem in the combination. Is also possible.

(First Embodiment)
Hereinafter, the first embodiment of the air conditioner according to the present invention will be described with reference to the drawings. In the present embodiment, the air conditioner according to the present invention is applied to the vehicle air conditioner 1 mounted on an electric vehicle. An electric vehicle is a vehicle that obtains driving force for traveling from an electric motor. The vehicle air-conditioning device 1 air-conditions the interior of an electric vehicle, which is a space to be air-conditioned.

The vehicle air conditioner 1 has a refrigerating cycle device 10 and an indoor air conditioner unit 30 as shown in the overall configuration diagram of FIG.

First, the refrigeration cycle apparatus 10 will be described. The refrigeration cycle device 10 adjusts the temperature of the blown air blown into the vehicle interior in the vehicle air conditioner 1. The refrigerating cycle device 10 is configured to be able to switch the refrigerant circuit for circulating the refrigerant according to the operation mode.

In the refrigerating cycle apparatus 10, an HFO-based refrigerant (specifically, R1234yf) is used as the refrigerant. The refrigeration cycle device 10 constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. The refrigerating machine oil is a PAG oil (polyalkylene glycol oil) having compatibility with a liquid phase refrigerant. Some of the refrigerating machine oil circulates in the cycle together with the refrigerant.

The compressor 11 sucks in the refrigerant in the refrigerating cycle device 10, compresses it, and discharges it. The compressor 11 is arranged in the drive unit room on the front side of the vehicle interior. The drive device room is a space outside the vehicle interior in which at least a part of a drive device (for example, an electric motor) for outputting a driving force for traveling is arranged.

The compressor 11 is an electric compressor that rotationally drives a fixed-capacity compression mechanism having a fixed discharge capacity by an electric motor. The number of revolutions (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 60 described later.

The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port of the compressor 11. The indoor condenser 12 is arranged in the casing 31 of the indoor air conditioning unit 30, which will be described later.

The indoor condenser 12 is a heat exchanger that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air. In the indoor condenser 12, the heat of the high-pressure refrigerant is dissipated to the blown air to condense the high-pressure refrigerant and heat the blown air. Therefore, the indoor condenser 12 is a heating unit that heats the blown air using the high-pressure refrigerant discharged from the compressor 11 as a heat source.

One inflow outlet side of the four-way valve 13 is connected to the refrigerant outlet of the indoor condenser 12. The four-way valve 13 is a refrigerant circuit switching unit that switches the refrigerant circuit that circulates the refrigerant in the refrigeration cycle device 10. The four-way valve 13 is an electric switching valve whose operation is controlled by a control voltage output from the control device 60.

Specifically, the four-way valve 13 connects the refrigerant outlet side of the indoor condenser 12 and one of the inflow / outlet sides of the first expansion valve 14a, and at the same time, compresses with one of the refrigerant inlet / outlet sides of the outdoor heat exchanger 16 described later. It is possible to switch to a refrigerant circuit that connects to the suction port side of the machine 11. Further, the four-way valve 13 connects the refrigerant outlet side of the indoor condenser 12 and one refrigerant inlet / outlet side of the outdoor heat exchanger 16 described later, and at the same time, at the same time, connects one inflow outlet side of the first expansion valve 14a and the compressor 11. It is possible to switch to a refrigerant circuit that connects to the suction port side of the.

One inflow port side of the first expansion valve 14a is connected to another inflow port of the four-way valve 13. The first expansion valve 14a is a first pressure reducing unit that reduces the pressure of the refrigerant. The first expansion valve 14a is a first refrigerant flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing out to the downstream side.

The first expansion valve 14a is an electric variable throttle mechanism having a valve body that changes the throttle opening degree and an electric actuator that displaces the valve body. The operation of the first expansion valve 14a is controlled by a control signal (control pulse) output from the control device 60. Further, the first expansion valve 14a has a fully open function that functions as a mere refrigerant passage without exerting a refrigerant depressurizing action and a flow rate adjusting action by fully opening the valve opening.

One refrigerant inlet / outlet side of the indoor evaporator 15 is connected to the other inlet / outlet of the first expansion valve 14a. The indoor evaporator 15 is located in the casing 31 of the indoor air conditioning unit 30 and is located on the upstream side of the blown air flow with respect to the indoor condenser 12.

The indoor evaporator 15 is a heat exchanger that exchanges heat between the low-pressure refrigerant decompressed by the first expansion valve 14a or the second expansion valve 14b and the blown air. The indoor evaporator 15 is a cooling heat exchange unit that cools an object to be cooled by evaporating a low-pressure refrigerant to exert an endothermic action. The indoor evaporator 15 is an air cooling heat exchange unit that cools the blown air before flowing into the indoor condenser 12 as a cooling object.

Further, in the present embodiment, a so-called tank-and-tube type heat exchanger is adopted as the indoor evaporator 15. The tank-and-tube heat exchanger has a plurality of refrigerant tubes and a pair of refrigerant tanks.

The refrigerant tube is a metal tube that allows the refrigerant to flow inside. The plurality of refrigerant tubes are stacked and arranged in a predetermined direction at intervals. An air passage through which the blown air flows is formed between the adjacent tubes. Heat exchange fins that promote heat exchange between the refrigerant and the blown air are arranged in the air passage. The heat exchange fin is a corrugated fin formed by bending a thin metal plate into a corrugated shape.

The refrigerant tank is a metal bottomed tubular member extending in the stacking direction of a plurality of refrigerant tubes. The pair of refrigerant tanks are connected to both ends of the refrigerant tube, respectively. Inside the refrigerant tank, a distribution space for distributing the refrigerant to a plurality of refrigerant tubes and a collecting space for collecting the refrigerants flowing out from the plurality of refrigerant tubes are formed. Therefore, in the tank-and-tube type heat exchanger, a heat exchange core portion for heat exchange between the refrigerant and the blown air is formed mainly by the refrigerant tube and the heat exchange fins.

In the indoor evaporator 15, the desiccant material 15a is applied to the outer surface of the heat exchange core portion. The desiccant material 15a is an adsorption portion that adsorbs moisture contained in the blown air. That is, the indoor evaporator 15 has a suction portion.

One inflow / outlet side of the second expansion valve 14b is connected to the other refrigerant inlet / outlet of the indoor evaporator 15. The second expansion valve 14b is a second pressure reducing unit that reduces the pressure of the refrigerant. The second expansion valve 14b is a second refrigerant flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing out to the downstream side. The basic configuration of the second expansion valve 14b is the same as that of the first expansion valve 14a.

The other refrigerant inlet / outlet side of the outdoor heat exchanger 16 is connected to the other refrigerant inflow outlet of the second expansion valve 14b. The outdoor heat exchanger 16 is an outdoor heat exchange unit that exchanges heat between the refrigerant flowing inside and the outside air blown from an outside air fan (not shown). The outdoor heat exchanger 16 is arranged on the front side in the drive unit room. Therefore, when the vehicle is traveling, the outdoor heat exchanger 16 can be exposed to the traveling wind as the outside air.

As described above, another inflow / outlet side of the four-way valve 13 is connected to one of the refrigerant inlets / outlets of the outdoor heat exchanger 16. The suction port side of the compressor 11 is connected to yet another inflow port of the four-way valve 13.

Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is a unit for blowing out blown air adjusted to an appropriate temperature toward an appropriate portion in the vehicle interior in the vehicle air-conditioning device 1. The indoor air conditioning unit 30 is arranged inside an instrument panel (that is, an instrument panel) arranged at the front of the vehicle interior.

The indoor air conditioning unit 30 has a casing 31 that forms an air passage for blown air inside. An indoor condenser 12, an indoor evaporator 15, and the like are arranged in an air passage formed in the casing 31. The casing 31 is made of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.

An inside / outside air switching device 33 is arranged on the most upstream side of the blast air flow of the casing 31. The inside / outside air switching device 33 adjusts the introduction ratio of the inside air (that is, the vehicle interior air) and the outside air (that is, the vehicle interior / outside air) introduced into the casing 31. Therefore, the inside / outside air switching device 33 is an inside / outside air ratio adjusting unit that adjusts the ratio of the inside air to the outside air in the blown air flowing into the indoor evaporator 15.

The inside / outside air switching device 33 has an inside / outside air door 33a, an electric actuator for the inside / outside air door, and the like. The electric actuator for the inside / outside air door displaces the inside / outside air door 33a. Thereby, the inside / outside air door 33a adjusts the area ratio between the opening area of the inside air introduction port for introducing the inside air into the air passage in the casing 31 and the opening area of the outside air introduction port for introducing the outside air into the air passage. The operation of the electric actuator for the inside / outside air door is controlled by the control signal output from the control device 60.

An indoor blower 32 is arranged on the downstream side of the blower air flow of the inside / outside air switching device 33. The indoor blower 32 blows the air sucked through the inside / outside air switching device 33 toward the vehicle interior. The indoor blower 32 is an electric blower that drives a centrifugal multi-blade fan with an electric motor. The rotation speed (that is, the blowing capacity) of the indoor blower 32 is controlled by the control voltage output from the control device 60.

The downstream side of the blower air flow of the indoor blower 32 is partitioned into a plurality of air passages. Further, in the air passage on the downstream side of the blown air flow of the indoor blower 32, the indoor evaporator 15 and the indoor condenser 12 are arranged in this order with respect to the blown air flow. That is, the indoor evaporator 15 is arranged on the upstream side of the blast air flow with respect to the indoor condenser 12.

More specifically, the air passage on the downstream side of the indoor evaporator 15 is partitioned into a heating passage 35a and a cold air bypass passage 35b. The indoor condenser 12 is arranged in the heating passage 35a. The heating passage 35a is a passage through which the blown air that has passed through the indoor evaporator 15 is further passed through the indoor condenser 12 and flows to the downstream side. The cold air bypass passage 35b is a passage through which the blown air that has passed through the indoor evaporator 15 is bypassed by the indoor condenser 12 and flows to the downstream side.

Further, on the downstream side of the blown air flow of the indoor blower 32, an outside air bypass passage 35c is formed so as to bypass the indoor evaporator 15 and allow the blown air to flow. The most downstream portion of the air flow in the outside air bypass passage 35c is connected to an auxiliary outside air introduction port 31a described later.

An air mix door 34 is arranged in the air passage on the downstream side of the blown air flow of the indoor evaporator 15 and on the upstream side of the blown air flow of the heating passage 35a and the cold air bypass passage 35b. The air mix door 34 adjusts the air volume ratio between the air volume flowing into the heating passage 35a and the air volume flowing into the cold air bypass passage 35b in the air blown air that has passed through the indoor evaporator 15.

Specifically, the air mix door 34 adjusts the air volume ratio by adjusting the area ratio between the opening area of the inlet of the heating passage 35a and the opening area of the inlet of the cold air bypass passage 35b. The operation of the electric actuator 34a for the air mix door that drives the air mix door 34 is controlled by a control signal output from the control device 60.

Here, when the air mix door 34 changes the opening area of the inlet of the heating passage 35a, the amount of blown air passing through the heating passage 35a changes. When the amount of blown air passing through the heating passage 35a changes, the amount of heat exchange between the refrigerant and the blown air in the indoor condenser 12 also changes. Therefore, the air mix door 34 is a heating amount adjusting unit that adjusts the heating amount of the blown air in the indoor condenser 12.

A mixing space 36 is arranged on the downstream side of the blown air flow of the heating passage 35a and the cold air bypass passage 35b. The mixing space 36 mixes the blown air that has passed through the heating passage 35a and heated by the indoor condenser 12 and the blown air that has passed through the cold air bypass passage 35b and has not been heated by the indoor condenser 12. It is a space.

Further, a plurality of opening holes (not shown) are formed in the most downstream portion of the blown air flow of the casing 31 for blowing the blown air (air-conditioned air) mixed in the mixing space 36 into the vehicle interior.

Therefore, the air mix door 34 adjusts the temperature of the blown air mixed in the mixing space 36 by adjusting the air volume ratio between the air volume passing through the heating passage 35a and the air volume passing through the cold air bypass passage 35b. can do. That is, by displacing the air mix door 34, the temperature of the blown air blown from each opening hole into the vehicle interior can be adjusted.

Specifically, as the opening hole, a face opening hole, a foot opening hole, and a defroster opening hole (none of which are shown) are provided. The face opening hole is an opening hole for blowing air-conditioned air toward the upper body of the occupant in the vehicle interior. The foot opening hole is an opening hole for blowing air-conditioned air toward the feet of the occupant. The defroster opening hole is an opening hole for blowing air-conditioned air toward the inner side surface of the front window glass of the vehicle.

An outlet mode switching door (not shown) is arranged on the upstream side of these opening holes. The blowing mode switching door switches the opening hole for blowing out the conditioned air by opening and closing each opening hole. The operation of the electric actuator for driving the blowout mode switching door is controlled by a control signal output from the control device 60.

Further, an auxiliary outside air introduction device 37 is arranged at a portion of the casing 31 that forms the heating passage 35a. The auxiliary outside air introduction device 37 is an auxiliary outside air introduction unit that introduces outside air into the indoor condenser 12 from the downstream side of the air mix door 34 during the desorption stroke described later.

The auxiliary outside air introduction device 37 has an auxiliary outside air door 37a that opens and closes the auxiliary outside air introduction port 31a, and an electric actuator for the auxiliary outside air door. The auxiliary outside air introduction port 31a is provided at a portion of the casing 31 that separates the heating passage 35a and the outside air bypass passage 35c. The operation of the electric actuator for the auxiliary outside air introduction device is controlled by the control signal output from the control device 60.

Then, when the electric actuator for the auxiliary outside air introduction device displaces the auxiliary outside air door 37a so as to open the auxiliary outside air introduction port 31a, the blown air flowing into the outside air bypass passage 35c is condensed indoors through the auxiliary outside air introduction port 31a. It is introduced into the vessel 12.

Further, an exhaust device 38 is arranged on the most downstream side of the cold air bypass passage 35b of the casing 31. The exhaust device 38 is an exhaust unit that exhausts the blown air flowing through the cold air bypass passage 35b to the outside of the vehicle interior during the dehumidification / heating mode desorption stroke described later.

The exhaust device 38 has an exhaust door 38a that opens and closes an exhaust port 31b formed in the casing 31, and an electric actuator for the exhaust door. The operation of the electric actuator for the exhaust door is controlled by the control signal output from the control device 60.

When the electric actuator for the exhaust door displaces the exhaust door 38a so as to fully open the exhaust port 31b, not only the exhaust port 31b opens but also the communication portion between the cold air bypass passage 35b and the mixing space 36 is closed. Will be done. As a result, the entire amount of air blown through the cold air bypass passage 35b is discharged to the outside of the vehicle interior through the exhaust port 31b.

Further, when the electric actuator for the exhaust door displaces the exhaust door 38a so as to fully close the exhaust port 31b, the communication portion between the cold air bypass passage 35b and the mixing space 36 opens. As a result, the blown air of the entire air volume that has passed through the cold air bypass passage 35b flows into the mixing space 36 without being exhausted to the outside.

Next, the outline of the electric control unit of the vehicle air conditioner 1 will be described with reference to FIG. The control device 60 includes a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof. The control device 60 performs various calculations and processes based on the air conditioning control program stored in the ROM, and various controlled target devices 11, 13, 14a, 14b, 32, 33, 34a, 37, connected to the output side. It controls the operation of 38 etc.

As shown in FIG. 2, various control sensors are connected to the input side of the control device 60. The control sensor includes an inside air temperature sensor 61a, an outside air temperature sensor 61b, and an insolation amount sensor 61c. Further, the control sensor includes a high pressure pressure sensor 61d, an air conditioning air temperature sensor 61e, an evaporator temperature sensor 61f, an evaporator pressure sensor 61g, an outdoor unit temperature sensor 61h, and an outdoor unit pressure sensor 61i.

The internal air temperature sensor 61a is an internal air temperature detection unit that detects the internal air temperature Tr, which is the temperature inside the vehicle interior. The outside air temperature sensor 61b is an outside air temperature detection unit that detects the outside air temperature Tam, which is the temperature outside the vehicle interior. The solar radiation amount sensor 61c is a solar radiation amount detection unit that detects the solar radiation amount As irradiated to the vehicle interior. The detected values of these detection units are used when calculating the target blowout temperature TAO, which will be described later.

The high-pressure pressure sensor 61d is a high-pressure pressure detection unit that detects the high-pressure pressure Pd, which is the pressure of the high-pressure refrigerant discharged from the compressor 11. The conditioned air temperature sensor 61e is an conditioned air temperature detecting unit that detects the blown air temperature TAV blown from the mixing space 36 into the vehicle interior.

The evaporator temperature sensor 61f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 15. The evaporator temperature sensor 61f specifically detects the temperature of the heat exchange fins of the indoor evaporator 15.

The evaporator pressure sensor 61g is an evaporator pressure detecting unit that detects the refrigerant evaporation pressure Pe in the indoor evaporator 15. The evaporator pressure sensor 61g of the present embodiment specifically detects the pressure of the refrigerant on one refrigerant inlet / outlet side (the refrigerant inlet / outlet side to which the first expansion valve 14a is connected) of the indoor evaporator 15.

The outdoor unit temperature sensor 61h is an outdoor unit temperature detecting unit that detects the outdoor unit refrigerant temperature (outdoor unit temperature) Tout, which is the temperature of the refrigerant flowing through the outdoor heat exchanger 16. The outdoor unit temperature sensor 61h of the present embodiment specifically detects the temperature of the other refrigerant inlet / outlet side (refrigerant inlet / outlet side to which the second expansion valve 14b is connected) of the outdoor heat exchanger 16.

The outdoor unit pressure sensor 61i is an outdoor unit temperature detecting unit that detects the outdoor unit refrigerant pressure Pout, which is the pressure of the refrigerant flowing through the outdoor heat exchanger 16. The outdoor unit pressure sensor 61i of the present embodiment specifically detects the pressure on the other refrigerant inlet / outlet side (the refrigerant inlet / outlet side to which the second expansion valve 14b is connected) of the outdoor heat exchanger 16.

Further, an operation panel 62 arranged near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device 60, and operation signals from various operation switches provided on the operation panel 62 are input.

Specific examples of the various operation switches provided on the operation panel 62 include an air conditioner switch, an auto switch, an air volume setting switch, a temperature setting switch, and the like.

The air conditioner switch is an operation switch for requesting that the indoor evaporator 15 cools the blown air. The auto switch is an operation switch for setting or canceling the automatic control operation of the refrigeration cycle device 10. The air volume setting switch is an operation switch for manually setting the air volume of the indoor blower 32. The temperature setting switch is an operation switch for setting the target temperature Tset in the vehicle interior.

Further, the control device 60 of the present embodiment is integrally configured with a control unit that controls various controlled devices connected to the output side. That is, in the control device 60, the configuration (that is, hardware and software) that controls the operation of each control target device is a control unit that controls the operation of each control target device.

For example, in the control device 60, the configuration for controlling the operation of the four-way valve 13 which is the refrigerant circuit switching unit is the refrigerant circuit control unit 60a. The configuration that controls the operation of the inside / outside air switching device 33, which is the inside / outside air ratio adjusting unit, is the inside / outside air switching control unit 60b. The configuration that controls the operation of the electric actuator 34a for the air mix door is the heating amount control unit 60c.

Next, the operation of the vehicle air conditioner 1 will be described. In the vehicle air conditioner 1, various operation modes are switched in order to perform air conditioning in the vehicle interior. The operation mode is switched by executing the air conditioning control program stored in the control device 60 in advance. The air conditioning control program is executed when the auto switch of the operation panel 62 is turned on (ON).

In the air conditioning control program, the target blowing temperature TAO of the blown air blown into the vehicle interior is calculated based on the detection signal of the control sensor and the operation signal of the operation panel 62 described above. Further, in the air conditioning control program, the operation mode is switched based on the target blowout temperature TAO, the detection signal of the control sensor, and the operation signal of the operation panel 62. The operation of each operation mode will be described in detail below.

(A) Cooling mode The cooling mode is an operation mode in which the inside of the vehicle is cooled by blowing the cooled blown air into the vehicle interior.

The cooling mode is executed when the outside air temperature Tam detected by the outside air temperature sensor 61b is equal to or higher than the reference non-standard temperature KTam, and the target outlet temperature TAO is equal to or lower than the cooling reference temperature KTao.

The non-standard air temperature KTam is generally set to a value at which it is determined that window fogging is unlikely to occur on the inner surface of the vehicle window glass when the outside air temperature Tam is equal to or higher than the standard air temperature KTam. The cooling reference temperature KTao is generally set to a temperature at which it is determined that cooling in the vehicle interior is necessary when the target blowing temperature TAO is equal to or lower than the cooling reference temperature KTao.

In the cooling mode, the control device 60 sets the first expansion valve 14a in the fully open state and the second expansion valve 14b in the throttle state in which the refrigerant depressurizing action is exerted. Further, the control device 60 connects the refrigerant outlet side of the indoor condenser 12 and the refrigerant inlet / outlet side of one of the outdoor heat exchangers 16, and at the same time, at the same time, sucks in one of the inflow / outlet sides of the first expansion valve 14a and the compressor 11. The operation of the four-way valve 13 is controlled so as to connect to the mouth side.

Therefore, in the refrigerating cycle device 10 in the cooling mode, as shown by the white arrow in FIG. 1, the refrigerant discharged from the compressor 11 is the indoor condenser 12, the four-way valve 13, the outdoor heat exchanger 16, and the second expansion. It is switched to a refrigerant circuit that circulates in the order of the valve 14b, the indoor evaporator 15, the first expansion valve 14a in the fully open state, the four-way valve 13, and the suction port of the compressor 11.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, for the control signal output to the compressor 11, the control device 60 determines that the evaporator temperature Tefin detected by the evaporator temperature sensor 61f approaches the target evaporator temperature TEO.

The target evaporator temperature TEO is determined based on the target blowout temperature TAO with reference to the control map for the cooling mode previously stored in the control device 60. In the control map for the cooling mode, the target evaporator temperature TEO is determined to be a temperature (specifically, 1 ° C. or higher) capable of suppressing frost formation in the indoor evaporator 15.

Further, regarding the control signal output to the inside / outside air switching device 33, the control device 60 determines that the inside air introduction port is fully closed and the outside air introduction port is fully open. If you want to obtain high cooling performance even in the cooling mode, determine the control signal output to the inside / outside air switching device 33 so that the inside air introduction port is fully opened and the outside air introduction port is fully closed. May be good.

Further, the control device 60 determines the control voltage output to the indoor blower 32 based on the target blowout temperature TAO. Further, regarding the control signal output to the electric actuator 34a for the air mix door, the control device 60 determines that the blown air temperature TAV detected by the air conditioning air temperature sensor 61e approaches the target blown temperature TAO.

Further, regarding the control signal output to the auxiliary outside air introduction device 37, the control device 60 determines to close the auxiliary outside air introduction port 31a. Further, regarding the control signal output to the exhaust device 38, the control device 60 determines to close the exhaust port 31b.

Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

In the air conditioning control program, the detection signal and the operation signal are read, the target blowout temperature TAO is calculated, the operation mode is determined, and various types according to the operation mode are read at each predetermined control cycle until the stop of the air conditioning in the vehicle interior is requested. The control routine such as determining the control signal and the like to be output to the controlled device and outputting the determined control signal and the like is repeated. The repetition of such a control routine is similarly performed in other operation modes.

Therefore, in the refrigerating cycle device 10 in the cooling mode, the indoor condenser 12 and the outdoor heat exchanger 16 function as a condenser that dissipates heat and condenses the refrigerant, and the indoor evaporator 15 functions as an evaporator that evaporates the refrigerant. A steam compression type refrigeration cycle is constructed.

In the refrigerating cycle device 10 in the cooling mode, the blown air is heated by the refrigerant radiating heat to the blown air in the indoor condenser 12. In the indoor evaporator 15, the blown air is cooled by evaporating the refrigerant and exerting an endothermic action.

Further, in the indoor air conditioning unit 30 in the cooling mode, the outside air introduced into the casing 31 via the inside / outside air switching device 33 is sucked into the indoor blower 32 as blown air. The blown air blown from the indoor blower 32 is cooled as it passes through the indoor evaporator 15. The blown air cooled by the indoor evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b according to the opening degree of the air mix door 34.

The blown air flowing into the heating passage 35a is heated when passing through the indoor condenser 12. The blown air heated by the indoor condenser 12 flows into the mixing space 36. In the cooling mode, the auxiliary outside air introduction device 37 closes the auxiliary outside air introduction port 31a. Therefore, the outside air does not flow into the heating passage 35a through the auxiliary outside air introduction port 31a.

The blown air that has flowed into the cold air bypass passage 35b flows into the mixing space 36. In the cooling mode, the exhaust device 38 closes the exhaust port 31b. Therefore, the blown air of the entire air volume that has passed through the cold air bypass passage 35b flows into the mixing space 36.

In the mixing space 36, the blown air (warm air) flowing in through the heating passage 35a and the blown air (cold air) flowing in through the cold air bypass passage 35b are mixed, and the blown air (air conditioning air) having an appropriate temperature is mixed. It becomes. The blown air mixed in the mixing space 36 and adjusted in temperature is blown out to an appropriate place in the vehicle interior through the opening hole. As a result, cooling of the passenger compartment is realized.

Here, the indoor evaporator 15 is coated with a desiccant material 15a which is an adsorption portion. Therefore, until the adsorption amount of the desiccant material 15a reaches the saturation amount, when the blown air passes through the indoor evaporator 15, the moisture contained in the blown air is adsorbed on the desiccant material 15a.

However, in the cooling mode, since the outside air temperature Tam is equal to or higher than the standard non-standard air temperature KTam, it is unlikely that the window glass of the vehicle will be fogged. Therefore, in the cooling mode, even if the adsorption amount of the desiccant material 15a reaches the saturation amount, the operation of the desorption process of desorbing water from the desiccant material 15a and regenerating it is not executed. Therefore, in the cooling mode, the interior of the vehicle can be continuously cooled.

(B) Dehumidifying and heating mode The dehumidifying and heating mode is an operation mode in which the dehumidified and heated air inside the vehicle is dehumidified and heated by reheating the cooled and dehumidified blown air and blowing it into the vehicle interior. The dehumidifying / heating mode is executed when the outside air temperature Tam is lower than the reference air temperature KTam, or when the target outlet temperature TAO is higher than the cooling reference temperature KTao.

The vehicle air conditioner 1 dehumidifies the blown air by utilizing the adsorption action of the desiccant material 15a when dehumidifying and heating the interior of the vehicle. Therefore, in the dehumidifying / heating mode, it is necessary to desorb water from the desiccant material 15a and regenerate it before the adsorption amount of the desiccant material 15a reaches the saturation amount.

Therefore, in the dehumidifying / heating mode, an adsorption process for adsorbing water to the desiccant material 15a for dehumidifying the blown air and a desorption process for desorbing water from the desiccant material 15a for regeneration of the desiccant material 15a are predetermined. Switch in the cycle of.

First, in the suction stroke of the dehumidifying / heating mode, the control device 60 sets the first expansion valve 14a in the throttled state and the second expansion valve 14b in the throttled state or fully open. Further, the control device 60 connects the refrigerant outlet side of the indoor condenser 12 and the one inflow / outlet side of the first expansion valve 14a, and at the same time, simultaneously connects the one refrigerant inlet / outlet side of the outdoor heat exchanger 16 and the suction of the compressor 11. The operation of the four-way valve 13 is controlled so as to connect to the mouth side.

Therefore, in the refrigerating cycle device 10 in the adsorption stroke, as shown by the black arrow in FIG. 1, the refrigerant discharged from the compressor 11 is the indoor condenser 12, the four-way valve 13, the first expansion valve 14a, and the indoor evaporator. It is switched to a refrigerant circuit that circulates in the order of 15, the second expansion valve 14b, the outdoor heat exchanger 16, the four-way valve 13, and the suction port of the compressor 11.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control signal output to the compressor 11, the control device 60 determines that the high pressure pressure Pd detected by the high pressure pressure sensor 61d approaches the target high pressure PDO. The target high pressure PDO is determined based on the target blowout temperature TAO with reference to the control map for the dehumidifying / heating mode stored in advance in the control device 60.

Further, regarding the control signal output to the inside / outside air switching device 33, the control device 60 determines that the inside air introduction port is fully opened and the outside air introduction port is fully closed. That is, in the adsorption stroke, the inside / outside air switching device 33 increases the ratio of the inside air in the blown air flowing into the indoor evaporator 15 more than the ratio of the outside air.

The control signals and the like output to other controlled devices are determined in the same manner as in the cooling mode. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10 in the adsorption process, as shown in the Moriel diagram of FIG. 3, the refrigerant discharged from the compressor 11 (point a3 in FIG. 3) flows into the indoor condenser 12. The refrigerant flowing into the indoor condenser 12 exchanges heat with the blown air and condenses (points a3 → b3 in FIG. 3). The refrigerant flowing out of the indoor condenser 12 is depressurized by the first expansion valve 14a (points b3 to c3 in FIG. 3) and flows into the indoor evaporator 15.

The refrigerant flowing into the indoor evaporator 15 exchanges heat with the blown air and evaporates (point c3 → point d3 in FIG. 3). The refrigerant flowing out of the indoor evaporator 15 flows into the outdoor heat exchanger 16 via the fully opened second expansion valve 14b. Note that FIG. 3 shows an example in which the second expansion valve 14b is fully opened. The refrigerant flowing into the outdoor heat exchanger 16 exchanges heat with the outside air and evaporates (point d3 → point e3 in FIG. 3).

The refrigerant flowing out of the outdoor heat exchanger 16 is sucked into the compressor 11 and compressed again (point f3 → point a3 in FIG. 3). The difference in pressure between the points e3 and f3 in FIG. 3 is the suction pressure loss of the compressor 11. The suction pressure loss is also shown in the following Moriel diagram.

That is, in the refrigeration cycle device 10 for the adsorption process, the indoor condenser 12 functions as a condenser, and the indoor evaporator 15 and the outdoor heat exchanger 16 form a steam compression type refrigeration cycle that functions as an evaporator. .. In the refrigerating cycle device 10 for the adsorption process, the blown air is heated by the indoor condenser 12. In the indoor evaporator 15, the blown air is cooled and dehumidified.

Further, in the indoor air conditioning unit 30 in the adsorption process, the inside air introduced into the casing 31 via the inside / outside air switching device 33 is used as blown air in the room as schematically shown by the broken line arrow in the Moriel diagram of FIG. It is sucked into the blower 32. The blown air blown from the indoor blower 32 is cooled and dehumidified as it passes through the indoor evaporator 15. Further, in the adsorption process, the suction action of the desiccant material 15a dehumidifies the blown air passing through the indoor evaporator 15.

The blown air cooled and dehumidified by the indoor evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b according to the opening degree of the air mix door 34. The blown air flowing into the heating passage 35a is heated by the indoor condenser 12. The blown air flowing into the heating passage 35a and the cold air bypass passage 35b is mixed in the mixing space 36 as in the cooling mode. The blown air mixed in the mixing space 36 is blown out to an appropriate place in the vehicle interior through the opening hole. As a result, dehumidifying and heating of the vehicle interior is realized.

Next, in the dehumidification / heating mode desorption stroke, the control device 60 sets the first expansion valve 14a in the fully open state and the second expansion valve 14b in the throttle state. Further, the control device 60 connects the refrigerant outlet side of the indoor condenser 12 and the one inflow / outlet side of the first expansion valve 14a, and at the same time, simultaneously connects the one refrigerant inlet / outlet side of the outdoor heat exchanger 16 and the suction of the compressor 11. The operation of the four-way valve 13 is controlled so as to connect to the mouth side.

Therefore, in the refrigerating cycle device 10 in the desorption stroke, as shown by the black arrow in FIG. 1, the refrigerant circuit is such that the refrigerant circulates in the same order as the adsorption stroke.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, regarding the control signal output to the inside / outside air switching device 33, the control device 60 determines the control signal so that the inside air introduction port is fully closed and the outside air introduction port is fully open. That is, in the desorption stroke, the inside / outside air switching device 33 increases the ratio of the outside air in the blown air flowing into the indoor evaporator 15 more than the ratio of the inside air.

Further, regarding the control signal output to the auxiliary outside air introduction device 37, the control device 60 determines to open the auxiliary outside air introduction port 31a. Further, regarding the control signal output to the exhaust device 38, the control device 60 determines that the exhaust port 31b is fully opened.

The control signals and the like output to other controlled devices are determined in the same manner as in the adsorption process. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigeration cycle device 10 in the desorption stroke, as shown in the Moriel diagram of FIG. 4, the refrigerant discharged from the compressor 11 (point a4 in FIG. 4) flows into the indoor condenser 12. The refrigerant flowing into the indoor condenser 12 exchanges heat with the blown air and condenses (points a4 → b4 in FIG. 4). The refrigerant flowing out of the indoor condenser 12 flows into the indoor evaporator 15 via the first expansion valve 14a which is fully opened.

The refrigerant flowing into the indoor evaporator 15 dissipates heat to the outside air and the desiccant material 15a and condenses (points b4 to c4 in FIG. 4). The refrigerant flowing out of the indoor evaporator 15a is depressurized by the second expansion valve 14b (points c4 to d4 in FIG. 4) and flows into the outdoor heat exchanger 16. The refrigerant flowing into the outdoor heat exchanger 16 exchanges heat with the outside air and evaporates (point d4 → point e4 in FIG. 4). The refrigerant flowing out of the outdoor heat exchanger 16 is sucked into the compressor 11 and compressed again (point f4 → point a4 in FIG. 4).

That is, in the refrigeration cycle device 10 in the desorption stroke, a steam compression type refrigeration cycle is configured in which the indoor condenser 12 and the indoor evaporator 15 function as condensers, and the outdoor heat exchanger 16 functions as an evaporator. To. In the refrigerating cycle device 10 in the desorption stroke, the blown air is heated by the indoor condenser 12.

Further, in the indoor air conditioning unit 30 in the desorption stroke, the outside air introduced into the casing 31 via the inside / outside air switching device 33 is schematically shown by the broken line arrow in the Moriel diagram of FIG. 4, and the outside air is introduced into the indoor blower 32. Inhaled into. The outside air blown from the indoor blower 32 is heated when passing through the indoor evaporator 15 and is humidified by the moisture desorbed from the desiccant material 15a. As a result, the desiccant material 15a is regenerated.

The outside air that has passed through the indoor evaporator 15 flows into the cold air bypass passage 35b because the air mix door 34 completely closes the entrance of the heating passage 35a. The outside air that has flowed into the cold air bypass passage 35b is exhausted to the outside of the vehicle interior through the exhaust port 31b because the exhaust device 38 has the exhaust port 31b fully open.

The outside air flowing into the heating passage 35a from the auxiliary outside air introduction port 31a is heated when passing through the indoor condenser 12 as blown air, as schematically shown by the broken line arrow in the Moriel diagram of FIG. The blown air heated by the indoor condenser 12 flows into the mixing space 36. The blown air flowing into the mixed space 36 is blown out to an appropriate place in the vehicle interior through the opening hole. As a result, the heating inside the vehicle interior can be continued even during the desorption process.

(C) Defrosting mode The defrosting mode is an operation mode for removing frost on the outdoor heat exchanger 16. The dehumidification mode is executed when a predetermined frost formation condition is satisfied during the execution of the dehumidification / heating mode.

In the air conditioning control program of the present embodiment, the frost formation time in which the outdoor unit temperature Tout detected by the outdoor unit temperature sensor 61h is continuously equal to or lower than the predetermined reference frost temperature KToutf during the execution of the dehumidifying / heating mode. Measure Tmf. Then, when the frost formation time Tmf becomes equal to or longer than the reference frost formation time KTmf, it is determined that the frost formation condition is satisfied.

In the defrosting mode, the control device 60 sets the first expansion valve 14a in the fully open state and the second expansion valve 14b in the throttle state. Further, the control device 60 connects the refrigerant outlet side of the indoor condenser 12 and the refrigerant inlet / outlet side of one of the outdoor heat exchangers 16, and at the same time, at the same time, sucks in one of the inflow / outlet sides of the first expansion valve 14a and the compressor 11. The operation of the four-way valve 13 is controlled so as to connect to the mouth side.

Therefore, the refrigerating cycle device 10 in the defrosting mode is switched to the refrigerant circuit in which the refrigerant circulates in the same order as in the cooling mode, as shown by the white arrows in FIG.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, the control device 60 determines that the rotation speed of the control signal output to the compressor 11 is lower than that in the dehumidifying / heating mode. The control signal output to the compressor 11 is determined within a range in which the refrigerating machine oil mixed in the refrigerant can be returned to the compressor 11.

Further, regarding the control signal output to the inside / outside air switching device 33, the control device 60 determines that the inside air introduction port is fully opened and the outside air introduction port is fully closed. Further, the control device 60 determines that the rotation speed of the control signal output to the indoor blower 32 is lower than that in the dehumidifying / heating mode.

Further, regarding the control signal output to the electric actuator 34a for the air mix door, the control device 60 determines that the opening area of the inlet of the heating passage 35a is reduced by a predetermined amount as compared with the dehumidifying / heating mode. As a result, in the dehumidification mode, the amount of heating of the blown air in the indoor condenser 12 is reduced as compared with the dehumidification / heating mode.

The control signals and the like output to other controlled devices are determined in the same manner as in the dehumidifying / heating mode. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10 in the defrosting mode, as shown in the Moriel diagram of FIG. 5, the refrigerant discharged from the compressor 11 (point a5 in FIG. 5) flows into the indoor condenser 12. The refrigerant flowing into the indoor condenser 12 exchanges heat with the blown air and condenses (points a5 → b5 in FIG. 5). The refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 16.

The refrigerant flowing into the outdoor heat exchanger 16 dissipates heat to the outside air and the outdoor heat exchanger 16 and condenses (points b5 to c5 in FIG. 5). The refrigerant flowing out of the outdoor heat exchanger 16 is depressurized by the second expansion valve 14b (points c5 → d5 in FIG. 5) and flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 exchanges heat with the blown air and evaporates (point d5 → point e5 in FIG. 5). The refrigerant flowing out of the indoor evaporator 15 is sucked into the compressor 11 via the fully opened first expansion valve 14a and compressed again (point f5 → point a5 in FIG. 5).

That is, in the refrigerating cycle device 10 in the defrosting mode, the indoor condenser 12 and the outdoor heat exchanger 16 function as a condenser, and the indoor evaporator 15 functions as an evaporator. To.

In the refrigerating cycle device 10 in the defrosting mode, the blown air is heated by the indoor condenser 12. In the indoor evaporator 15, the blown air is cooled and dehumidified. Further, in the outdoor heat exchanger 16, the heat of the refrigerant flowing out of the indoor condenser 12 melts and removes the frost attached to the outdoor heat exchanger 16. That is, the outdoor heat exchanger 16 is defrosted.

Further, in the indoor air conditioning unit 30 in the defrosting mode, the inside air introduced into the casing 31 via the inside / outside air switching device 33 is used as blown air as schematically shown by the broken line arrow in the Moriel diagram of FIG. It is sucked into the indoor blower 32. The blown air blown from the indoor blower 32 is cooled and dehumidified as it passes through the indoor evaporator 15. Further, in the dehumidification mode, the dehumidification of the blown air passing through the indoor evaporator 15 is also performed by the adsorption action of the desiccant material 15a.

The blown air cooled and dehumidified by the indoor evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b according to the opening degree of the air mix door 34. The blown air flowing into the heating passage 35a is heated by the indoor condenser 12. The blown air flowing into the heating passage 35a and the blown air flowing into the cold air bypass passage 35b flow into the mixing space 36 and are mixed in the same manner as in the cooling mode. The blown air mixed in the mixing space 36 is blown out to an appropriate place in the vehicle interior through the opening hole.

In the defrosting mode, the rotation speed of the compressor 11 is lower than that in the dehumidifying and heating mode. Further, the air mix door 34 is displaced so that the opening area of the inlet of the heating passage 35a is smaller than that in the dehumidifying and heating mode. Therefore, although the amount of heating of the blown air in the indoor condenser 12 is smaller than that in the dehumidifying / heating mode, the dehumidifying / heating in the vehicle interior can be continued.

Further, the defrosting mode ends when a predetermined end condition is satisfied. When the defrosting mode ends, the mode shifts to the dehumidifying / heating mode. In the air-conditioning control program of the present embodiment, the end condition is when the execution time Tmdf of the defrosting mode becomes the standard defrosting time KTmdf or more and the outdoor unit temperature Tout becomes the predetermined standard defrosting temperature KToutdf or more. Is determined to have been established.

As described above, according to the vehicle air conditioner 1 of the present embodiment, comfortable air conditioning in the vehicle interior can be realized by switching the operation mode.

Further, in the vehicle air conditioner 1 of the present embodiment, the desiccant material 15a is applied to the indoor evaporator 15. Therefore, it is possible to dehumidify the blown air by utilizing the adsorption action of the desiccant material 15a during the adsorption process in the dehumidification / heating mode. According to this, it is possible to reduce the power consumption of the compressor 11 consumed for dehumidification and improve the coefficient of performance of the refrigeration cycle device 10. As a result, the operating efficiency of the vehicle air conditioner 1 can be improved.

Further, in the defrosting mode, the blown air cooled and dehumidified by the indoor evaporator 15 can be reheated by the indoor condenser 12. Therefore, even if the rotation speed of the compressor 11 is determined to the extent that the refrigerating machine oil can be appropriately returned to the compressor 11, the temperature drop in the vehicle interior can be suppressed.

That is, according to the vehicle air conditioner 1 of the present embodiment, the refrigerating machine oil can be used regardless of the operation mode while obtaining the effect of improving the operating efficiency by providing the indoor evaporator 15 coated with the desiccant material 15a. It can be properly returned to the compressor 11.

Further, in the vehicle air conditioner 1 of the present embodiment, the adsorption stroke and the desorption stroke are switched in the dehumidifying / heating mode. Then, in the adsorption process of the dehumidifying / heating mode, the inside / outside air switching device 33 increases the ratio of the inside air in the blown air flowing into the indoor evaporator 15 more than the outside air.

According to this, more inside air, which is hotter and more humid than outside air, can be introduced into the indoor evaporator 15 during the adsorption process. Therefore, the power consumption of the compressor 11 consumed for reheating the blown air can be reduced, and the coefficient of performance of the refrigeration cycle device 10 can be further improved. As a result, the operating efficiency of the vehicle air conditioner 1 can be further improved.

Further, in the dehumidification / heating mode desorption stroke, the inside / outside air switching device 33 increases the ratio of the outside air in the blown air flowing into the indoor evaporator 15 more than the inside air. According to this, during the desorption stroke, more outside air having a lower humidity than the inside air can be introduced into the indoor evaporator 15 than the inside air. Therefore, the desiccant material 15a can be efficiently regenerated.

Further, the vehicle air conditioner 1 of the present embodiment includes an auxiliary outside air introduction device 37. According to this, during the desorption stroke, the outside air having a lower humidity than the inside air can be reheated by the indoor condenser 12 and blown out into the vehicle interior. Therefore, even if the adsorption stroke is switched to the dehumidification stroke when the dehumidifying / heating mode is executed, the heating inside the vehicle interior can be continued. Further, it is possible to suppress the occurrence of fogging of the window glass of the vehicle during the desorption process.

Further, in the vehicle air conditioner 1 of the present embodiment, the heating amount of the blown air in the indoor condenser 12 is reduced in the defrosting mode. According to this, the heat of the refrigerant discharged from the compressor 11 in the defrosting mode can be used for defrosting the outdoor heat exchanger 16 in preference to heating the blown air. Therefore, the defrosting of the outdoor heat exchanger 16 can be completed quickly.

Further, the vehicle air conditioner 1 of the present embodiment includes an exhaust device 38, and exhausts the air after passing through the indoor evaporator 15 to the outside of the vehicle interior during the dehumidification / heating mode desorption stroke. According to this, it is possible to surely suppress the increase in the humidity in the vehicle interior due to the moisture desorbed from the desiccant material 15a. That is, it is possible to effectively suppress the occurrence of fogging of the vehicle window glass during the desorption stroke.

(Second Embodiment)
In this embodiment, the vehicle air conditioner 1a shown in the overall configuration diagram of FIGS. 6 and 7 will be described. The vehicle air conditioner 1a has a function of not only air-conditioning the interior of the vehicle but also cooling the battery 80, which is a heat generating device that generates heat during operation. Therefore, the vehicle air conditioner 1a is an air conditioner with a heat generating device cooling function.

The vehicle air conditioner 1a includes a refrigerating cycle device 10a, an indoor air conditioner unit 30, a high temperature side heat medium circuit 40, and a low temperature side heat medium circuit 50.

The inlet side of the refrigerant passage of the water refrigerant heat exchanger 12a is connected to the discharge port of the compressor 11 of the refrigeration cycle device 10a. The water-refrigerant heat exchanger 12a has a refrigerant passage for circulating the high-pressure refrigerant discharged from the compressor 11 and a water passage for circulating the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40.

The water refrigerant heat exchanger 12a is a heat medium heating heat exchange unit that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature side heat medium flowing through the water passage. In the water refrigerant heat exchanger 12a, the heat of the high-pressure refrigerant is radiated to the high-temperature side heat medium to condense the high-pressure refrigerant and heat the high-temperature side heat medium.

The inflow port side of the first three-way joint 17a is connected to the outlet of the refrigerant passage of the water refrigerant heat exchanger 12a. The first three-way joint 17a has three inflow ports that communicate with each other. As the first three-way joint 17a, a member formed by joining a plurality of pipes, a member formed by providing a plurality of refrigerant passages in a metal block or a resin block, and the like can be adopted.

Further, the refrigeration cycle device 10a includes a second three-way joint 17b to a fourth three-way joint 17d, as will be described later. The basic configuration of the second three-way joint 17b to the fourth three-way joint 17d is the same as that of the first three-way joint 17a.

In the first three-way joint 17a to the fourth three-way joint 17d, when one of the three inflow ports is used as an inflow port and two are used as an outflow port, the flow of the refrigerant flowing in from one inflow port is branched. Can be done. In the present embodiment, the first three-way joint 17a serves as a branch portion. Further, when two of the three inflow ports are used as inflow ports and one is used as the outflow port, the flows of the refrigerant flowing in from the two inflow ports can be merged.

The inlet side of the heating expansion valve 14c is connected to one of the outlets of the first three-way joint 17a. One inflow port side of the second three-way joint 17b is connected to the other outflow port of the first three-way joint 17a via a bypass passage 22a.

A high-pressure on-off valve 13a is arranged in the bypass passage 22a. The high-pressure on-off valve 13a is a solenoid valve that opens and closes the bypass passage 22a. The opening / closing operation of the high-voltage on-off valve 13a is controlled by the control voltage output from the control device 60.

Further, the refrigeration cycle device 10a includes a low pressure on-off valve 13b as described later. The basic configuration of the low-pressure on-off valve 13b is the same as that of the high-pressure on-off valve 13a. The high-pressure on-off valve 13a and the low-pressure on-off valve 13b can switch the refrigerant circuit in each operation mode by opening and closing the refrigerant passage. Therefore, the high-pressure on-off valve 13a and the low-pressure on-off valve 13b are the refrigerant circuit switching portions of the present embodiment.

The heating expansion valve 14c is an outdoor decompression unit that reduces the pressure of the refrigerant flowing into the outdoor heat exchanger 16 during the dehumidification / heating mode described later. The heating expansion valve 14c is an outdoor refrigerant flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing out to the downstream side. The basic configuration of the heating expansion valve 14c is the same as that of the first expansion valve 14a described in the first embodiment.

Further, the refrigerating cycle device 10a includes a cooling expansion valve 14d and a cooling expansion valve 14e, as will be described later. The basic configurations of the cooling expansion valve 14d and the cooling expansion valve 14e are the same as those of the first expansion valve 14a.

The heating expansion valve 14c, the cooling expansion valve 14d, and the cooling expansion valve 14e have a fully closing function of closing the refrigerant passage by fully closing the valve opening in addition to the above-mentioned fully opening function. ing. Therefore, the heating expansion valve 14c, the cooling expansion valve 14d, and the cooling expansion valve 14e also have a function as a refrigerant circuit switching unit for switching the refrigerant circuit by exerting a fully closed function.

Of course, the heating expansion valve 14c, the cooling expansion valve 14d, and the cooling expansion valve 14e may be formed by combining a variable throttle mechanism having no fully closed function and an on-off valve. In this case, the on-off valve serves as the refrigerant circuit switching unit.

The refrigerant inlet side of the outdoor heat exchanger 16, which is an outdoor heat exchange section, is connected to the outlet of the heating expansion valve 14c. The inlet side of the third three-way joint 17c is connected to the refrigerant outlet of the outdoor heat exchanger 16. One inlet side of the evaporation pressure adjusting valve 20 is connected to one outlet of the third three-way joint 17c via a heating passage 22b. A low-pressure on-off valve 13b for opening and closing the heating passage 22b is arranged in the heating passage 22b.

The other inlet side of the second three-way joint 17b is connected to the other outlet of the third three-way joint 17c. A check valve 18 is arranged in the refrigerant passage connecting the other outlet side of the third three-way joint 17c and the other inlet side of the second three-way joint 17b. The check valve 18 allows the refrigerant to flow from the third three-way joint 17c side to the second three-way joint 17b side, and prohibits the refrigerant from flowing from the second three-way joint 17b side to the third three-way joint 17c side.

The inlet side of the fourth three-way joint 17d is connected to the outlet of the second three-way joint 17b. The inlet side of the cooling expansion valve 14d is connected to one of the outlets of the fourth three-way joint 17d. The inlet side of the cooling expansion valve 14e is connected to the other outlet of the fourth three-way joint 17d. The cooling expansion valve 14d and the cooling expansion valve 14e are both cooling pressure reducing units for reducing the pressure of the refrigerant.

More specifically, the cooling expansion valve 14d is an air cooling pressure reducing unit that reduces the pressure of the refrigerant flowing into the indoor evaporator 15 in the single cooling mode described later. The cooling expansion valve 14d is an air refrigerant flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing out to the downstream side.

The refrigerant inlet side of the indoor evaporator 15 is connected to the outlet of the cooling expansion valve 14d. The indoor evaporator 15 is a cooling heat exchange unit that evaporates the refrigerant decompressed by the cooling expansion valve 14d in order to cool the object to be cooled. More specifically, the indoor evaporator 15 is an air cooling heat exchange unit for cooling the blown air.

Further, the cooling expansion valve 14e is a heat medium cooling pressure reducing unit that reduces the pressure of the refrigerant flowing into the chiller 19 during the cooling cooling mode described later. The cooling expansion valve 14e is a device cooling refrigerant flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing out to the downstream side.

The inlet side of the refrigerant passage of the chiller 19 is connected to the outlet of the cooling expansion valve 14e. The chiller 19 has a refrigerant passage through which the low-pressure refrigerant decompressed by the cooling expansion valve 14e is circulated, and a water passage through which the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50 is circulated.

The chiller 19 is a heat exchanger that exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage and the low-temperature side heat medium flowing through the water passage. In the chiller 19, the low-temperature side heat medium is cooled by evaporating the low-pressure refrigerant to exert an endothermic action. The third inlet side of the evaporation pressure adjusting valve 20 is connected to the outlet of the refrigerant passage of the chiller 19.

The evaporation pressure adjusting valve 20 is a pressure adjusting unit that individually adjusts the refrigerant pressure in the outdoor heat exchanger 16, the refrigerant pressure in the indoor evaporator 15, and the refrigerant pressure in the chiller 19. Further, the evaporation pressure adjusting valve 20 combines the flows of at least two or more of the refrigerants flowing out of the outdoor heat exchanger 16, the refrigerant flowing out of the indoor evaporator 15, and the refrigerant flowing out of the chiller 19. , Outflow to the downstream side.

Specifically, the evaporation pressure regulating valve 20 integrates three electric variable throttle mechanisms connected to the downstream side of the outdoor heat exchanger 16, the indoor evaporator 15, and the chiller 19 and the merging portion 17g. It was made to. The operation of the evaporation pressure adjusting valve 20 is controlled by a control signal output from the control device 60.

The inlet side of the accumulator 21 is connected to the refrigerant outlet of the confluence portion 17 g of the evaporation pressure adjusting valve 20. The accumulator 21 is a low-pressure side gas-liquid separator that separates the gas-liquid of the low-pressure refrigerant flowing out of the heat exchanger that functions as an evaporator. The accumulator 21 stores the separated liquid phase refrigerant as a surplus refrigerant in the cycle.

Therefore, the merging portion 17g of the evaporation pressure adjusting valve 20 merges the flow of the refrigerant flowing out from the outdoor heat exchanger 16, the flow of the refrigerant flowing out from the indoor evaporator 15, and the flow of the refrigerant flowing out from the chiller 19. It flows out to the suction side of the compressor 11.

Next, the high temperature side heat medium circuit 40 will be described. The high temperature side heat medium circuit 40 is a heat medium circulation circuit that circulates the high temperature side heat medium. In the high temperature side heat medium circuit 40, an ethylene glycol aqueous solution is adopted as the high temperature side heat medium. In the high temperature side heat medium circuit 40, a water passage of the water refrigerant heat exchanger 12a, a high temperature side heat medium pump 41, a heater core 42, and the like are arranged.

The high temperature side heat medium pump 41 is a water pump that pumps the high temperature side heat medium to the inlet side of the water passage of the water refrigerant heat exchanger 12a. The high temperature side heat medium pump 41 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 60.

The heat medium inlet side of the heater core 42 is connected to the outlet of the water passage of the water refrigerant heat exchanger 12a. The heater core 42 is arranged in the casing 31 of the indoor air conditioning unit 30 in the same manner as the indoor condenser 12 described in the first embodiment.

The heater core 42 is an air heating heat exchange unit that exchanges heat between the high temperature side heat medium heated by the water refrigerant heat exchanger 12a and the blown air. In the heater core 42, the heat of the high temperature side heat medium is radiated to the blown air to heat the blown air. The suction port side of the high temperature side heat medium pump 41 is connected to the heat medium outlet of the heater core 42.

Therefore, in the present embodiment, each component of the water refrigerant heat exchanger 12a and the high temperature side heat medium circuit 40 forms a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source. ..

Further, in the high temperature side heat medium circuit 40, the high temperature side heat medium pump 41 adjusts the flow rate of the high temperature side heat medium flowing into the heater core 42, whereby the amount of heat exchange between the high temperature side heat medium and the blown air in the heater core 42. Also changes. Therefore, the high temperature side heat medium pump 41 is a heating amount adjusting unit that adjusts the heating amount of the blown air in the indoor condenser 12.

Next, the low temperature side heat medium circuit 50 will be described. The low temperature side heat medium circuit 50 is a heat medium circulation circuit that circulates the low temperature side heat medium. As the low temperature side heat medium, a fluid of the same type as the high temperature side heat medium can be adopted. In the low temperature side heat medium circuit 50, a water passage of the chiller 19, a low temperature side heat medium pump 51, a cooling water passage 80a of the battery 80, and the like are arranged.

The low temperature side heat medium pump 51 is a water pump that pumps the low temperature side heat medium to the inlet side of the water passage of the chiller 19. The basic configuration of the low temperature side heat medium pump 51 is the same as that of the high temperature side heat medium pump 41. The inlet side of the cooling water passage 80a of the battery 80 is connected to the outlet of the water passage of the chiller 19.

The battery 80 is a secondary battery (in this embodiment, a lithium ion battery) that stores electric power supplied to an in-vehicle device such as an electric motor. The battery 80 is a heat generating device that generates heat during operation (that is, during charging / discharging). The temperature of the battery 80 needs to be maintained within an appropriate temperature range (15 ° C. or higher and 55 ° C. or lower in this embodiment) in order to fully utilize the charge / discharge capacity of the battery 80.

The cooling water passage 80a is a heat exchange unit for heat medium equipment formed inside a battery case that houses the battery cell of the battery 80. The cooling water passage 80a has a configuration in which a plurality of passages are connected in parallel inside the battery case. As a result, the cooling water passage 80a can evenly cool all the battery cells. The suction port side of the low temperature side heat medium pump 51 is connected to the outlet of the cooling water passage 80a.

Therefore, in the present embodiment, each component device of the chiller 19 and the low temperature side heat medium circuit 50 forms a device cooling unit for cooling the battery 80 that generates heat during operation. Further, the chiller 19 is a cooling heat exchange unit that evaporates the refrigerant decompressed by the cooling expansion valve 14e in order to cool the object to be cooled. More specifically, the chiller 19 is a heat exchange unit for cooling a heat medium for cooling the battery 80.

Next, the outline of the electric control unit of the vehicle air conditioner 1a will be described with reference to FIG. The control device 60 of the present embodiment controls the operation of various controlled devices 11, 13a, 13b, 14c to 14e, 20, 32, 33, 34a, 37, 38, 41, 61, etc. connected to the output side. ..

Further, on the input side of the control device 60, as shown in FIG. 8, in addition to the various control sensors described in the first embodiment, the battery temperature sensor 61j, the high temperature side heat medium temperature sensor 61k, and the low temperature side heat are placed. A medium temperature sensor 61 m or the like has been added.

The battery temperature sensor 61j is a battery temperature detection unit that detects the battery temperature TB, which is the temperature of the battery 80. The battery temperature sensor 61j has a plurality of temperature detection units, and detects the temperature of a plurality of points of the battery 80. Therefore, the control device 60 can also detect the temperature difference of each part of the battery 80. Further, as the battery temperature TB, the average value of the detected values of a plurality of temperature sensors is adopted.

The high temperature side heat medium temperature sensor 61k is a high temperature side heat medium temperature detection unit that detects the high temperature side heat medium temperature TWH, which is the temperature of the high temperature side heat medium flowing out from the water passage of the water refrigerant heat exchanger 12a. The low temperature side heat medium temperature sensor 61m is a low temperature side heat medium temperature detecting unit that detects the low temperature side heat medium temperature TWL which is the temperature of the low temperature side heat medium flowing out from the water passage of the chiller 19.

Further, in the present embodiment, among the control devices 60, the configuration for controlling the operation of the high-pressure on-off valve 13a and the low-pressure on-off valve 13b, which are the refrigerant circuit switching units, is the refrigerant circuit control unit 60a. The configuration for controlling the operation of the high temperature side heat medium pump 41 is the high temperature side pump control unit 60d. The configuration for controlling the operation of the low-pressure side heat medium pump 61 is the low-pressure side pump control unit 60e.

Next, the operation of the vehicle air conditioner 1a will be described. The vehicle air conditioner 1a not only air-conditions the interior of the vehicle, but also switches various operation modes in order to cool the battery 80. The operation mode is switched by executing the air conditioning control program stored in the control device 60 in advance, as in the first embodiment. The operation of each operation mode will be described below.

(A) Cooling mode The cooling mode of the vehicle air conditioner 1a includes an independent cooling mode and a cooling cooling mode. The single cooling mode is an operation mode in which the interior of the vehicle is cooled without cooling the battery 80. The single cooling mode is executed when the execution conditions of the cooling mode similar to those of the first embodiment are satisfied and it is determined that the battery 80 does not need to be cooled.

The cooling / cooling mode is an operation mode in which the battery 80 is cooled and the interior of the vehicle is cooled. The cooling / cooling mode is executed when the execution conditions of the cooling mode similar to those of the first embodiment are satisfied and it is determined that the battery 80 needs to be cooled.

To determine whether or not the battery 80 needs to be cooled, the battery 80 needs to be cooled when the battery temperature TB detected by the battery temperature sensor 61j is equal to or higher than the predetermined reference cooling temperature KTB. Is determined. Further, when the battery temperature TB is lower than the reference cooling temperature KTB, it is determined that the battery 80 does not need to be cooled. The determination as to whether or not the battery 80 needs to be cooled is similarly performed in the following operation modes.

(A-1) Single cooling mode In the single cooling mode, the control device 60 closes the high-pressure on-off valve 13a and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully open state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigerating cycle device 10a in the single cooling mode, as shown by the white arrow in FIG. 6, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a and the heating expansion valve 14c which is fully open. , The outdoor heat exchanger 16, the check valve 18, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure adjusting valve 20, the accumulator 21, and the suction port of the compressor 11 are switched to the refrigerant circuit in which the refrigerant circulates in this order.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity. Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines to stop the low temperature side heat medium pump 51. Specifically, the control voltage is determined to be 0V.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as in the cooling mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigeration cycle device 10a in the single cooling mode, the water-refrigerant heat exchanger 12a and the outdoor heat exchanger 16 function as a condenser, and the indoor evaporator 15 functions as an evaporator. It is composed. In the refrigerating cycle device 10a in the single cooling mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. The blown air is cooled by the indoor evaporator 15.

Further, in the high temperature side heat medium circuit 40 in the single cooling mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the indoor air conditioning unit 30 in the independent cooling mode, the outside air introduced into the casing 31 via the inside / outside air switching device 33 is sucked into the indoor blower 32 as blown air. The blown air blown from the indoor blower 32 is cooled as it passes through the indoor evaporator 15. The blown air cooled by the indoor evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b according to the opening degree of the air mix door 34.

The blown air flowing into the heating passage 35a is heated when passing through the heater core 42. The blown air heated by the heater core 42 flows into the mixing space 36 as in the cooling mode of the first embodiment. The blown air flowing into the cold air bypass passage 35b flows into the mixing space 36 as in the cooling mode of the first embodiment.

Then, the blown air mixed in the mixing space 36 and whose temperature is adjusted is blown out to an appropriate place in the vehicle interior through the opening hole. As a result, cooling of the passenger compartment is realized.

(A-2) Cooling / cooling mode In the cooling / cooling mode, the control device 60 closes the high-pressure on-off valve 13a and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in the fully open state, the cooling expansion valve 14d in the throttle state, and the cooling expansion valve 14e in the throttle state.

Therefore, in the refrigerating cycle device 10a in the cooling / cooling mode, as shown by the black arrow in FIG. 6, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a and the heating expansion valve 14c which is fully open. , The outdoor heat exchanger 16, the check valve 18, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure adjusting valve 20, the accumulator 21, and the suction port of the compressor 11 circulate in this order. At the same time, the refrigerant discharged from the compressor 11 is a water refrigerant heat exchanger 12a, a fully open heating expansion valve 14c, an outdoor heat exchanger 16, a check valve 18, a cooling expansion valve 14e, a chiller 19, and the like. It is switched to a refrigerant circuit in which the refrigerant circulates in the order of the evaporative pressure adjusting valve 20, the accumulator 21, and the suction port of the compressor 11.

That is, in the refrigerating cycle device 10a in the cooling / cooling mode, one of the refrigerants branched at the fourth three-way joint 17d flows into the cooling expansion valve 14d and the indoor evaporator 15 side, and the other refrigerant flows into the cooling expansion valve 14e. And flows into the chiller 19 side. Then, the refrigerant flowing out of the indoor evaporator 15 and the refrigerant flowing out of the chiller 19 are switched to the refrigerant circuit where they merge at the merging portion 17g of the evaporation pressure adjusting valve 20.

That is, in the refrigerating cycle device 10a in the cooling / cooling mode, the indoor evaporator 15 and the chiller 19 are switched to the refrigerant circuit connected in parallel with the refrigerant flow.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines that the low temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Further, regarding the control signal output to the evaporation pressure adjusting valve 20, the control device 60 determines that the refrigerant evaporation pressure in the indoor evaporator 15 and the refrigerant evaporation pressure in the chiller 19 are appropriate values.

The determination of the control signal and the like output to other controlled devices is determined in the same manner as in the single cooling mode. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigeration cycle device 10a in the cooling / cooling mode, the water-refrigerant heat exchanger 12a and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 15 and the chiller 19 function as evaporators. A refrigeration cycle is configured. In the refrigerating cycle apparatus 10a in the cooling / cooling mode, the heat medium on the high temperature side is heated by the water refrigerant heat exchanger 12a. The blown air is cooled by the indoor evaporator 15. The low temperature side heat medium is cooled by the chiller 19.

Further, in the high temperature side heat medium circuit 40 in the cooling / cooling mode, the high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42 as in the single cooling mode.

Further, in the low temperature side heat medium circuit 50 in the cooling / cooling mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows through the cooling water passage 80a of the battery 80. This cools the battery 80.

Further, in the indoor air conditioning unit 30 in the cooling battery cooling mode, the temperature of the blown air is adjusted and blown out to an appropriate place in the vehicle interior as in the single cooling mode. As a result, cooling of the passenger compartment is realized.

(B) Dehumidifying / heating mode The dehumidifying / heating mode of the vehicle air conditioner 1a includes a single dehumidifying / heating mode and a cooling dehumidifying / heating mode. The single dehumidifying / heating mode is an operation mode in which the dehumidifying / heating of the vehicle interior is performed without cooling the battery 80. The single dehumidifying / heating mode is executed when the execution conditions of the dehumidifying / heating mode similar to those of the first embodiment are satisfied and it is determined that the battery 80 does not need to be cooled.

The cooling / dehumidifying / heating mode is an operation mode in which the battery 80 is cooled and the vehicle interior is dehumidified / cooled. The cooling / dehumidifying / heating mode is executed when the execution conditions of the dehumidifying / heating mode similar to those of the first embodiment are satisfied and it is determined that the battery 80 needs to be cooled.

Further, also in the vehicle air conditioner 1a, the blown air is dehumidified by utilizing the adsorption action of the desiccant material 15a in the dehumidification / heating mode. Therefore, in the dehumidifying / heating mode, the adsorption stroke and the desorption stroke are switched at a predetermined cycle as in the first embodiment.

(B-1) Single dehumidifying / heating mode In the adsorption process of the single dehumidifying / heating mode, the control device 60 opens the high-pressure on-off valve 13a and the low-pressure on-off valve 13b. Further, the control device 60 puts the heating expansion valve 14c in the throttled state, the cooling expansion valve 14d in the throttled state, and the cooling expansion valve 14e in the fully closed state.

Therefore, in the refrigerating cycle device 10a in the adsorption process of the single dehumidifying / heating mode, as shown by the white arrow in FIG. 7, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the first three-way joint 17a, and the like. Refrigerant circulates in the order of the heating expansion valve 14c, the outdoor heat exchanger 16, the heating passage 22b, the evaporation pressure adjusting valve 20, the accumulator 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is a water refrigerant heat exchanger 12a, a first three-way joint 17a, a bypass passage 22a, a cooling expansion valve 14d, an indoor evaporator 15, an evaporation pressure adjusting valve 20, an accumulator 21, and compression. The refrigerant circulates in the order of the suction port of the machine 11.

That is, in the refrigerating cycle device 10a in the adsorption process of the single dehumidifying and heating mode, one of the refrigerants branched at the first three-way joint 17a flows into the heating expansion valve 14c and the outdoor heat exchanger 16 side, and the other refrigerant flows into the heating expansion valve 14c and the outdoor heat exchanger 16. It flows into the cooling expansion valve 14d and the indoor evaporator 15 side. Then, the refrigerant flowing out of the outdoor heat exchanger 16 and the refrigerant flowing out of the indoor evaporator 15 are switched to the refrigerant circuit where they merge at the merging portion 17g of the evaporation pressure adjusting valve 20.

That is, in the refrigerating cycle device 10a in the adsorption process of the single dehumidifying and heating mode, the outdoor heat exchanger 16 and the indoor evaporator 15 are switched to a refrigerant circuit connected in parallel with the refrigerant flow.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity. Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines to stop the low temperature side heat medium pump 51.

Further, regarding the control signal output to the evaporation pressure adjusting valve 20, the control device 60 determines that the refrigerant evaporation pressure in the outdoor heat exchanger 16 and the refrigerant evaporation pressure in the indoor evaporator 15 are appropriate values.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the adsorption process of the dehumidifying / heating mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10a in the adsorption process of the single dehumidifying and heating mode, as shown in the Moriel diagram of FIG. 9, the refrigerant discharged from the compressor 11 (point a9 in FIG. 9) is the water refrigerant heat exchanger 12a. Inflow to. The refrigerant flowing into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and condenses (points a9 → b9 in FIG. 9). The flow of the refrigerant flowing out of the water-refrigerant heat exchanger 12a is branched at the first three-way joint 17a.

One of the refrigerants branched at the first three-way joint 17a is depressurized by the heating expansion valve 14c (points b9 to c9 in FIG. 9) and flows into the outdoor heat exchanger 16. The refrigerant flowing into the outdoor heat exchanger 16 exchanges heat with the outside air and evaporates (point c9 → point d9 in FIG. 9).

The other refrigerant branched at the first three-way joint 17a is depressurized by the cooling expansion valve 14d (points b9 → e9 in FIG. 9) and flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 exchanges heat with the blown air and evaporates (points e9 → f9 in FIG. 9). The refrigerant flowing out of the indoor evaporator 15 is depressurized by the evaporation pressure adjusting valve 20 until the pressure becomes equivalent to that of the refrigerant flowing out of the outdoor heat exchanger 16 (points f9 to d9 in FIG. 9).

The refrigerant flowing out of the indoor evaporator 15 and the refrigerant flowing out of the outdoor heat exchanger 16 merge at the merging portion 17g. The refrigerant flowing out from the merging portion 17g flows into the accumulator 21 and is separated into gas and liquid. The gas phase refrigerant flowing out of the accumulator 21 is sucked into the compressor 11 and compressed again (point g9 → point a9 in FIG. 9).

That is, in the refrigerating cycle device 10a in the adsorption process of the single dehumidifying and heating mode, the water refrigerant heat exchanger 12a functions as a condenser, and the outdoor heat exchanger 16 and the indoor evaporator 15 function as an evaporator. Refrigeration cycle is configured. In the refrigerating cycle device 10a in the adsorption process of the single dehumidifying and heating mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. In the indoor evaporator 15, the blown air is cooled and dehumidified.

Further, in the high temperature side heat medium circuit 40 in the adsorption process of the single dehumidifying / heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the indoor air conditioning unit 30 in the adsorption process of the single dehumidifying and heating mode, the inside air introduced into the casing 31 via the inside / outside air switching device 33 is schematically shown by the broken line arrow in the Moriel diagram of FIG. , Is sucked into the indoor blower 32 as blown air. The blown air blown from the indoor blower 32 is cooled and dehumidified as it passes through the indoor evaporator 15.

Further, in the adsorption process, the suction action of the desiccant material 15a also dehumidifies the blown air passing through the indoor evaporator 15. The blown air cooled and dehumidified by the indoor evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b according to the opening degree of the air mix door 34. The blown air flowing into the heating passage 35a exchanges heat with the high-temperature side heat medium and is heated when passing through the heater core 42.

Note that FIG. 9 shows the blown air flowing into the heating passage 35a as if it passes through the water-refrigerant heat exchanger 12a, but FIG. 9 illustrates the transfer of heat between the blown air and the refrigerant. Is shown. That is, FIG. 9 shows that the blown air flowing into the heating passage 35a is heated by using the heat radiated by the refrigerant in the water refrigerant heat exchanger 12a as a heat source. This also applies to the Moriel diagram using the following water-refrigerant heat exchanger 12a and chiller 19.

The blown air flowing into the heating passage 35a and the cold air bypass passage 35b is mixed in the mixing space 36 as in the single cooling mode. The blown air mixed in the mixing space 36 and adjusted in temperature is blown out to an appropriate place in the vehicle interior through the opening hole. As a result, dehumidifying and heating of the vehicle interior is realized.

Next, in the dehumidification / heating mode desorption stroke, the control device 60 opens the high-pressure on-off valve 13a and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully closed state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigerating cycle device 10a in the desorption stroke of the single dehumidifying / heating mode, as shown by the diagonal hatched arrows in FIG. 7, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the bypass passage 22a, and the like. The cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure adjusting valve 20, the accumulator 21, and the suction port of the compressor 11 circulate in this order.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, the control signal output to the compressor 11 is determined so as to exhibit a predetermined refrigerant discharge capacity for the desorption stroke.

Further, the control signal output to the cooling expansion valve 14d is determined so as to have a predetermined reference throttle opening for the desorption stroke. The reference throttle opening for the desorption stroke is determined so that the temperature of the refrigerant flowing into the indoor evaporator 15 is a temperature at which water can be desorbed from the desiccant material 15a. Further, the reference throttle opening degree for the desorption stroke is determined so that the pressure of the refrigerant flowing into the indoor evaporator 15 does not exceed the pressure resistance of the indoor evaporator 15. Therefore, at the time of the desorption stroke, the cooling expansion valve 14 may be fully opened.

Further, regarding the control signal output to the evaporation pressure adjusting valve 20, the control device 60 determines that the refrigerant evaporation pressure in the accumulator 21 becomes an appropriate value.

Further, the control voltage output to the high temperature side heat medium pump 41 and the control voltage output to the low temperature side heat medium pump 51 are determined in the same manner as in the adsorption stroke.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the dehumidifying / heating mode dehumidifying / heating mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10a in the dehumidification and heating mode, as shown in the Moriel diagram of FIG. 10, the refrigerant discharged from the compressor 11 (point a10 in FIG. 10) is a water refrigerant heat exchanger. It flows into 12a. The refrigerant flowing into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and dissipates heat (points a10 → b10 in FIG. 10).

The refrigerant flowing out of the water-refrigerant heat exchanger 12a flows into the cooling expansion valve 14d via the bypass passage 22a and is depressurized (points b10 to c10 in FIG. 10). The refrigerant decompressed by the cooling expansion valve 14d flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 dissipates heat to the outside air and the desiccant material 15a (points c10 → d10 in FIG. 10).

The refrigerant flowing out of the indoor evaporator 15 flows into the evaporation pressure adjusting valve 20 and is depressurized (point d10 → point e10 in FIG. 10). The refrigerant decompressed by the evaporation pressure adjusting valve 20 flows into the accumulator 21. The gas phase refrigerant flowing out of the accumulator 21 is sucked into the compressor 11 and compressed again (point d10 → point a10 in FIG. 10).

That is, in the refrigerating cycle device 10a in the dehumidifying and heating mode, the water-refrigerant heat exchanger 12a and the indoor evaporator 15 function as radiators, so-called hot gas cycle is configured. In the refrigerating cycle device 10a in the desorption stroke, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a.

Further, in the high temperature side heat medium circuit 40 in the desorption stroke of the single dehumidifying / heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the indoor air conditioning unit 30 in the dehumidifying and heating mode, the outside air introduced into the casing 31 via the inside / outside air switching device 33 is sucked into the indoor blower 32.

A part of the outside air blown from the indoor blower 32 is humidified by the moisture desorbed from the desiccant material as it passes through the indoor evaporator 15, as schematically shown by the broken line arrow in the Moriel diagram of FIG. To. As a result, the desiccant material 15a is regenerated. The outside air that has passed through the indoor evaporator 15 is exhausted to the outside of the vehicle interior from the exhaust port 31b of the exhaust device 38, as in the dehumidification / heating mode desorption step of the first embodiment.

Another part of the outside air blown from the indoor blower 32 flows into the heating passage 35a from the auxiliary outside air introduction port 31a via the outside air bypass passage 35c. The outside air flowing into the heating passage 35a is the heat radiated by the refrigerant in the water-refrigerant heat exchanger 12a when passing through the heater core 42 as blown air, as in the dehumidification / heating mode desorption step of the first embodiment. Is heated as a heat source and blown into the passenger compartment. As a result, the interior of the vehicle can be heated even during the dehumidification / removal stroke of the single dehumidifying / heating mode.

(B-2) Cooling / Dehumidifying / Heating Mode In the adsorption process of the cooling / dehumidifying / heating mode, the control device 60 opens the high-pressure on-off valve 13a and the low-pressure on-off valve 13b. Further, the control device 60 puts the heating expansion valve 14c in the throttle state, the cooling expansion valve 14d in the throttle state, and the cooling expansion valve 14e in the throttle state.

Therefore, in the refrigerating cycle device 10a in the adsorption process of the cooling / dehumidifying / heating mode, as shown by the black arrow in FIG. 7, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the first three-way joint 17a, and the like. Refrigerant circulates in the order of the heating expansion valve 14c, the outdoor heat exchanger 16, the heating passage 22b, the evaporation pressure adjusting valve 20, the accumulator 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is a water refrigerant heat exchanger 12a, a first three-way joint 17a, a bypass passage 22a, a fourth three-way joint 17d, a cooling expansion valve 14d, an indoor evaporator 15, and an evaporation pressure adjusting valve. The refrigerant circulates in the order of 20, the accumulator 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is a water refrigerant heat exchanger 12a, a first three-way joint 17a, a bypass passage 22a, a fourth three-way joint 17d, a cooling expansion valve 14e, a chiller 19, an evaporation pressure adjusting valve 20, The refrigerant circulates in the order of the accumulator 21 and the suction port of the compressor 11.

That is, in the refrigerating cycle device 10a in the adsorption process of the cooling / dehumidifying / heating mode, one of the refrigerants branched at the first three-way joint 17a flows into the heating expansion valve 14c and the outdoor heat exchanger 16 side, and the other refrigerant flows into the heating expansion valve 14c and the outdoor heat exchanger 16. It flows into the fourth three-way joint 17d. Further, one of the refrigerants branched at the fourth three-way joint 17d flows into the cooling expansion valve 14d and the indoor evaporator 15, and the other refrigerant flows into the cooling expansion valve 14e and the chiller 19 side.

Then, the refrigerant flowing out of the outdoor heat exchanger 16, the refrigerant flowing out of the indoor evaporator 15, and the refrigerant flowing out of the chiller 19 are switched to a refrigerant circuit in which the refrigerants flow out at the merging portion 17g of the evaporation pressure adjusting valve 20.

That is, in the refrigerating cycle device 10a in the adsorption process of the cooling / dehumidifying / heating mode, the outdoor heat exchanger 16, the indoor evaporator 15, and the chiller 19 are switched to a refrigerant circuit connected in parallel to the refrigerant flow.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity. Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines that the low temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Further, regarding the control signal output to the evaporation pressure adjusting valve 20, the control device 60 appropriately determines the refrigerant evaporation pressure in the indoor evaporator 15, the refrigerant evaporation pressure in the outdoor heat exchanger 16, and the refrigerant evaporation pressure in the chiller 19. Determine to be a value.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the adsorption process of the dehumidifying / heating mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10a in the adsorption process of the cooling / dehumidifying / heating mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the outdoor heat exchanger 16, the indoor evaporator 15, and the chiller 19 function as steam. A compression refrigeration cycle is constructed.

In the refrigerating cycle device 10a in the adsorption process of the cooling / dehumidifying / heating mode, the high-temperature side heat medium is heated by the water-refrigerant heat exchanger 12a. In the indoor evaporator 15, the blown air is cooled and dehumidified. The low temperature side heat medium is cooled by the chiller 19.

Further, in the high temperature side heat medium circuit 40 in the adsorption process of the cooling / dehumidifying / heating mode, the high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42 as in the adsorption process of the single dehumidifying / heating mode. ..

Further, in the low temperature side heat medium circuit 50 in the adsorption process of the cooling / dehumidifying / heating mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows through the cooling water passage 80a of the battery 80. This cools the battery 80.

Further, in the indoor air conditioning unit 30 in the adsorption process of the cooling / dehumidifying / heating mode, the blown air is dehumidified and the temperature is adjusted in the same manner as in the adsorption process of the single dehumidifying / heating mode, and the air is blown out to an appropriate place in the vehicle interior. As a result, dehumidifying and heating of the vehicle interior is realized.

Next, in the desorption stroke of the cooling / dehumidifying / heating mode, the control device 60 opens the high-pressure on-off valve 13a and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully closed state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state. Therefore, in the refrigerating cycle device 10a of the dehumidification cycle of the single dehumidification / heating mode, a refrigerant circuit in which the refrigerant circulates in the same order as the dehumidification / heating mode of the single dehumidification / heating mode is formed.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, the control voltage output to the high temperature side heat medium pump 41 and the control voltage output to the low temperature side heat medium pump 51 are determined in the same manner as in the adsorption stroke.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the dehumidifying / heating mode dehumidifying / heating mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigeration cycle device 10a in the dehumidification / heating mode desorption stroke, the water refrigerant heat exchanger 12a and the indoor evaporator 15 function as radiators in the hot gas cycle as in the dehumidification / heating mode desorption stroke. Is configured. Then, in the refrigerating cycle device 10a in the desorption stroke, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a.

Further, in the high temperature side heat medium circuit 40 in the desorption stroke of the cooling / dehumidifying / heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the low temperature side heat medium circuit 50 in the desorption stroke of the cooling / dehumidifying / heating mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 circulates. Therefore, during the desorption stroke, the battery 80 can be continuously cooled by the low temperature side heat medium cooled during the adsorption stroke. That is, the encapsulation amount of the low temperature side heat medium is determined to have a heat capacity sufficient to continue the refrigerant of the battery 80 during the desorption stroke.

Further, in the indoor air conditioning unit 30 in the dehumidification / heating mode desorption process, the desiccant material 15a of the indoor evaporator 15 is regenerated in the same manner as in the dehumidification / heating mode desorption process. The outside air humidified when passing through the indoor evaporator 15 is exhausted to the outside of the vehicle interior through the exhaust port 31b of the exhaust device 38.

Further, the outside air flowing into the heating passage 35a through the outside air bypass passage 35c exchanges heat with the high temperature side heat medium heated by the water refrigerant heat exchanger 12a when passing through the heater core 42 as blown air. It is heated and blown into the passenger compartment. As a result, the interior of the vehicle can be heated even during the desorption stroke of the cooling / dehumidifying / heating mode.

(C) Defrosting mode The defrosting mode of the vehicle air conditioner 1a includes a single defrosting mode and a waste heat defrosting mode. The single defrosting mode is an operation mode in which the outdoor heat exchanger 16 is defrosted without cooling the battery 80. The single dehumidification mode is executed when the frost formation condition is satisfied during the execution of the single dehumidification / heating mode. The single defrost mode ends when the end condition is satisfied. When the defrosting mode ends, the mode shifts to the independent dehumidifying / heating mode.

The waste heat defrosting mode is an operation mode in which the battery 80 is cooled and the outdoor heat exchanger 16 is defrosted. The waste heat dehumidification mode is executed when the frost formation condition is satisfied during the execution of the cooling dehumidification / heating mode. The waste heat defrosting mode ends when the end condition is satisfied. When the defrosting mode ends, the mode shifts to the cooling / dehumidifying / heating mode.

(C-1) Single defrost mode In the single defrost mode, the control device 60 closes the high-pressure on-off valve 13a and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully open state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state. Therefore, in the refrigerating cycle device 10a in the single defrosting mode, as shown by the white arrow in FIG. 6, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates in the same order as in the single cooling mode.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, the control voltage output to the high-temperature side heat medium pump 41 is determined so as to exhibit a lower pumping capacity than in the single dehumidifying / heating mode. Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines to stop the low temperature side heat medium pump 51.

Further, with respect to the compressor 11, the control device 60 determines a control signal output to the compressor 11 so that the rotation speed is lower than that in the single dehumidifying / heating mode. The control signal output to the compressor 11 is determined within a range in which the refrigerating machine oil mixed in the refrigerant can be returned to the compressor 11.

Further, regarding the control signal output to the electric actuator 34a for the air mix door, the control device 60 determines that the opening area of the inlet of the heating passage 35a is reduced by a predetermined amount as compared with the dehumidifying / heating mode. As a result, in the dehumidification mode, the amount of heating of the blown air in the indoor condenser 12 is reduced as compared with the dehumidification / heating mode.

The control signals and the like output to other controlled devices are determined in the same manner as in the defrosting mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10a in the single defrosting mode, as shown in the Moriel diagram of FIG. 11, the refrigerant discharged from the compressor 11 (point a11 in FIG. 11) flows into the water refrigerant heat exchanger 12a. .. The refrigerant flowing into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and condenses (points a11 → b11 in FIG. 11). The flow of the refrigerant flowing out of the water-refrigerant heat exchanger 12a flows into the outdoor heat exchanger 16 via the fully opened heating expansion valve 14c.

The refrigerant flowing into the outdoor heat exchanger 16 dissipates heat to the outside air and the outdoor heat exchanger 16 and condenses (points b11 to c11 in FIG. 11). The refrigerant flowing out of the outdoor heat exchanger 16 is depressurized by the cooling expansion valve 14d (point c11 → point d11 in FIG. 11) and flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 exchanges heat with the blown air and evaporates (point d11 → point e11 in FIG. 11).

The refrigerant flowing out of the indoor evaporator 15 flows into the accumulator 21 and is gas-liquid separated. The gas phase refrigerant flowing out of the accumulator 21 is sucked into the compressor 11 and compressed again (point f11 → point a11 in FIG. 11).

That is, in the refrigeration cycle device 10a in the single defrost mode, the water refrigerant heat exchanger 12a and the outdoor heat exchanger 16 function as a condenser, and the indoor evaporator 15 functions as an evaporator. Is configured.

In the refrigerating cycle device 10a in the single defrosting mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. In the indoor evaporator 15, the blown air is cooled and dehumidified. Further, in the outdoor heat exchanger 16, the heat of the refrigerant flowing out of the indoor condenser 12 melts and removes the frost attached to the outdoor heat exchanger 16. That is, the outdoor heat exchanger 16 is defrosted.

Further, in the high temperature side heat medium circuit 40 in the single defrosting mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the indoor air conditioning unit 30 in the single defrosting mode, the blown air cooled and dehumidified by the indoor evaporator 15 passes through the heater core 42, as schematically shown by the broken line arrow in the Moriel diagram of FIG. At that time, the water-refrigerant heat exchanger 12a reheats the heat radiated by the refrigerant as a heat source.

In the single dehumidification mode, the rotation speed of the compressor 11 is lower than that in the single dehumidification / heating mode. The air mix door 34 is displaced so that the opening area at the entrance of the heating passage 35a is smaller than that in the single dehumidifying / heating mode. Further, the pumping capacity of the high temperature side heat medium pump 41 is lowered as compared with the single dehumidifying and heating mode. Therefore, although the amount of heating of the blown air in the heater core 42 is smaller than that in the single dehumidifying and heating mode, the dehumidifying and heating of the vehicle interior can be continued.

(C-2) Waste heat defrosting mode In the waste heat defrosting mode, the control device 60 closes the high-pressure on-off valve 13a and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in the fully open state, the cooling expansion valve 14d in the throttle state, and the cooling expansion valve 14e in the throttle state. Therefore, in the refrigerating cycle device 10a in the waste heat defrosting mode, as shown by the black arrow in FIG. 6, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates in the same order as the cooling / cooling mode.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, the control voltage output to the high-temperature side heat medium pump 41 is determined so as to exhibit a lower pumping capacity than in the single dehumidifying / heating mode. Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines that the low temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Further, regarding the control signal output to the evaporation pressure adjusting valve 20, the control device 60 determines that the refrigerant evaporation pressure in the indoor evaporator 15 and the refrigerant evaporation pressure in the chiller 19 are appropriate values.

The determination of the control signal and the like output to the other controlled devices is determined in the same manner as in the defrosting mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigeration cycle device 10a in the waste heat defrost mode, the water-refrigerant heat exchanger 12a and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 15 and the chiller 19 function as steam compressors. The formula refrigeration cycle is constructed.

In the refrigerating cycle device 10a in the waste heat defrosting mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. In the indoor evaporator 15, the blown air is cooled and dehumidified. The low temperature side heat medium is cooled by the chiller 19. Further, in the outdoor heat exchanger 16, the heat of the refrigerant flowing out of the indoor condenser 12 melts and removes the frost attached to the outdoor heat exchanger 16. That is, the outdoor heat exchanger 16 is defrosted.

Further, in the high temperature side heat medium circuit 40 in the waste heat defrosting mode, the high temperature side heat medium pressure-fed from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the low temperature side heat medium circuit 50 in the waste heat defrosting mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows through the cooling water passage 80a of the battery 80. This cools the battery 80.

Further, in the indoor air conditioning unit 30 in the waste heat defrosting mode, dehumidifying and heating of the vehicle interior is realized as in the single dehumidifying mode. In the waste heat defrosting mode, the heating amount of the blown air in the heater core 42 is smaller than that in the cooling dehumidifying / heating mode, but the dehumidifying / heating in the vehicle interior can be continued as in the single defrosting mode.

As described above, according to the vehicle air conditioner 1a of the present embodiment, it is possible to realize comfortable air conditioning in the vehicle interior and appropriate cooling of the heat generating device by switching the operation mode.

Further, in the vehicle air conditioner 1a of the present embodiment, since the desiccant material 15a is applied to the indoor evaporator 15, the same effect as that of the first embodiment can be obtained. That is, according to the vehicle air conditioner 1a of the present embodiment, the refrigerating machine oil can be used regardless of the operation mode while obtaining the effect of improving the operating efficiency by providing the indoor evaporator 15 coated with the desiccant material 15a. It can be properly returned to the compressor 11.

Further, in the vehicle air conditioner 1a of the present embodiment, a cooling expansion valve 14e is provided as a cooling pressure reducing unit, and a chiller 19 is provided as a cooling heat exchange unit. According to this, the battery 80 can be cooled. Further, in the waste heat dehumidification mode, the refrigerant circuit is switched so that the refrigerant flowing out from the outdoor heat exchanger 16 flows into the cooling expansion valve 14e. According to this, the waste heat of the battery 80 can be used as a heat source for defrosting the outdoor heat exchanger 16.

(Third Embodiment)
In this embodiment, the vehicle air conditioner 1b shown in the overall configuration diagram of FIGS. 12 and 13 will be described. Like the vehicle air conditioner 1a described in the second embodiment, the vehicle air conditioner 1b has a function of not only air-conditioning the vehicle interior but also cooling the battery 80. Therefore, the vehicle air conditioner 1b is an air conditioner with a heat generating device cooling function.

The vehicle air conditioner 1b includes a refrigeration cycle device 10b, an indoor air conditioner unit 30, a high temperature side heat medium circuit 40, and a low temperature side heat medium circuit 50.

In FIGS. 12 and 13, the indoor air conditioning unit 30 is not shown for the sake of clarity. Therefore, the indoor evaporator 15 of the refrigeration cycle device 10b is arranged in the casing 31 of the indoor air conditioning unit 30. The heater core 42 of the high temperature side heat medium circuit 40 is arranged in the casing 31 of the indoor air conditioning unit 30.

In the refrigeration cycle device 10b, the accumulator 21 is abolished and the receiver 23 is adopted. The receiver 23 is a high-pressure side gas-liquid separator that separates the gas-liquid of the high-pressure refrigerant flowing out of the heat exchanger that functions as a condenser. The receiver 23 causes a part of the separated liquid-phase refrigerant to flow out to the downstream side, and stores the remaining liquid-phase refrigerant as the surplus refrigerant in the cycle.

The inlet side of the heating expansion valve 14c is connected to one outlet of the first three-way joint 17a of the refrigeration cycle device 10b via the first high-pressure on-off valve 13c and the fifth three-way joint 17e. The inlet side of the receiver 23 is connected to the other outlet of the first three-way joint 17a via the inlet side passage 22c. A second high-pressure on-off valve 13d and a second three-way joint 17b are arranged in the inlet side passage 22c.

The first high-pressure on-off valve 13c is a solenoid valve that opens and closes a refrigerant passage from one outlet of the first three-way joint 17a to one inlet of the fifth three-way joint 17e. The outlet side of the receiver 23 is connected to the other inlet of the fifth three-way joint 17e via the outlet side passage 22d. A sixth three-way joint 17f and a second check valve 18b are arranged in the outlet side passage 22d. The inlet side of the fourth three-way joint 17d is connected to the remaining outlet of the sixth three-way joint 17f.

The second check valve 18b allows the refrigerant to flow from the 6th three-way joint 17f side to the 5th three-way joint 17e side, and prohibits the refrigerant from flowing from the 5th three-way joint 17e side to the 6th three-way joint 17f side. is doing. In other words, the second check valve 18b allows the refrigerant to flow from the outlet side of the receiver 23 to the inlet side of the heating expansion valve 14c, and allows the refrigerant to flow from the inlet side of the heating expansion valve 14c to the outlet side of the receiver 23. Is prohibited from flowing.

The basic configuration of the fifth three-way joint 17e and the sixth three-way joint 17f is the same as that of the first three-way joint 17a and the like. The basic configurations of the first high-pressure on-off valve 13c and the second high-pressure on-off valve 13d are the same as those of the high-pressure on-off valve 13a and the like described in the first embodiment. The first high-pressure on-off valve 13c and the second high-pressure on-off valve 13d are refrigerant circuit switching units. The basic configuration of the second check valve 18b is the same as that of the check valve 18 described in the first embodiment.

In this embodiment, the check valve 18 described in the first embodiment is referred to as a first check valve 18a for the sake of clarification of the description. The configuration of the other vehicle air conditioner 1b is the same as that of the vehicle air conditioner 1a described in the second embodiment.

Next, the operation of the vehicle air conditioner 1b will be described. The vehicle air conditioner 1b can execute the same operation mode as the vehicle air conditioner 1a described in the second embodiment. The operation of each operation mode will be described below.

(A-1) Single cooling mode In the single cooling mode, the control device 60 opens the first high-pressure on-off valve 13c, closes the second high-pressure on-off valve 13d, and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully open state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigerating cycle device 10b in the single cooling mode, as shown by the white arrow in FIG. 12, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a and the heating expansion valve 14c which is fully open. , Switch to the refrigerant circuit in which the refrigerant circulates in the order of the outdoor heat exchanger 16, the first check valve 18a, the receiver 23, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11. Be done.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control signal output to the cooling expansion valve 14d, the control device 60 determines that the outlet-side refrigerant of the indoor evaporator 15 approaches a predetermined target superheat degree.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as in the single cooling mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices. Therefore, in the vehicle air conditioner 1b in the single cooling mode, the interior of the vehicle can be cooled as in the second embodiment.

Further, in the refrigerating cycle device 10b in the single cooling mode, the surplus refrigerant of the cycle is stored in the receiver 23, so that the outlet-side refrigerant of the indoor evaporator 15 can have a degree of superheat. Therefore, it is possible to increase the amount of heat absorbed by the refrigerant in the indoor evaporator 15 and improve the cooling capacity of the blown air, as compared with the cycle in which the excess refrigerant in the cycle is stored in the accumulator.

(A-2) Cooling / Cooling Mode In the cooling / cooling mode, the control device 60 opens the first high-pressure on-off valve 13c, closes the second high-pressure on-off valve 13d, and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in the fully open state, the cooling expansion valve 14d in the throttle state, and the cooling expansion valve 14e in the throttle state.

Therefore, in the refrigerating cycle device 10b in the cooling / cooling mode, as shown by the black arrow in FIG. 12, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a and the heating expansion valve 14c which is fully open. , The outdoor heat exchanger 16, the first check valve 18a, the receiver 23, the fourth three-way joint 17d, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11 in this order. Circulate. At the same time, the refrigerant discharged from the compressor 11 is a water refrigerant heat exchanger 12a, a fully open heating expansion valve 14c, an outdoor heat exchanger 16, a first check valve 18a, a receiver 23, and a fourth three-way joint. It is switched to a refrigerant circuit in which the refrigerant circulates in the order of 17d, the cooling expansion valve 14e, the chiller 19, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11.

That is, in the refrigerating cycle device 10b in the cooling / cooling mode, the indoor evaporator 15 and the chiller 19 are switched to the refrigerant circuit connected in parallel to the refrigerant flow, as in the second embodiment.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control signal output to the cooling expansion valve 14d, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 15 approaches the target degree of superheat. Further, regarding the control signal output to the cooling expansion valve 14e, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the chiller 19 approaches the target degree of superheat.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as in the cooling / cooling mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices. Therefore, in the vehicle air conditioner 1b in the cooling / cooling mode, the battery 80 can be cooled and the interior of the vehicle can be cooled as in the second embodiment.

Further, in the refrigerating cycle device 10b in the cooling / cooling mode, the outlet-side refrigerant of the indoor evaporator 15 and the outlet-side refrigerant of the chiller 19 can be given a degree of superheat. Therefore, as in the single cooling mode, the amount of heat absorbed by the refrigerant in the indoor evaporator 15 can be increased to improve the cooling capacity of the blown air. Further, the heat absorption amount of the refrigerant in the chiller 19 can be increased to improve the cooling capacity of the battery 80.

(B-1) Single dehumidifying / heating mode In the adsorption stroke of the single dehumidifying / heating mode, the control device 60 closes the first high-pressure on-off valve 13c, opens the second high-pressure on-off valve 13d, and opens the low-pressure on-off valve 13b. Further, the control device 60 puts the heating expansion valve 14c in the throttled state, the cooling expansion valve 14d in the throttled state, and the cooling expansion valve 14e in the fully closed state.

Therefore, in the refrigerating cycle device 10b in the adsorption process of the single dehumidifying / heating mode, as shown by the white arrow in FIG. 13, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the inlet side passage 22c, and the receiver. The refrigerant circulates in the order of 23, the sixth three-way joint 17f of the outlet side passage 22d, the heating expansion valve 14c, the outdoor heat exchanger 16, the heating passage 22b, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 evaporates from the water refrigerant heat exchanger 12a, the inlet side passage 22c, the receiver 23, the sixth three-way joint 17f of the outlet side passage 22d, the cooling expansion valve 14d, the indoor evaporator 15, and the refrigerant. The refrigerant circulates in the order of the pressure regulating valve 20 and the suction port of the compressor 11.

That is, in the refrigerating cycle device 10b in the adsorption process of the single dehumidifying and heating mode, the outdoor heat exchanger 16 and the indoor evaporator 15 are switched to the refrigerant circuit connected in parallel to the refrigerant flow, as in the second embodiment. Be done.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control signal output to the heating expansion valve 14c, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the outdoor heat exchanger 16 approaches the target degree of superheat. Further, regarding the control signal output to the cooling expansion valve 14d, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 15 approaches the target degree of superheat.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the adsorption process of the single dehumidifying / heating mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices. Therefore, in the vehicle air conditioner 1b in the adsorption process of the single dehumidifying / heating mode, the dehumidifying / heating of the vehicle interior can be performed by utilizing the adsorption action of the desiccant material 15a as in the second embodiment.

Further, in the refrigerating cycle device 10b in the adsorption process of the single dehumidifying / heating mode, the outlet-side refrigerant of the outdoor heat exchanger 16 and the outlet-side refrigerant of the indoor evaporator 15 can be given a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased to improve the heating capacity of the blown air. Further, the amount of heat absorbed by the refrigerant in the indoor evaporator 15 can be increased to improve the cooling capacity of the blown air.

Next, in the dehumidification / heating mode desorption stroke, the control device 60 closes the first high-pressure on-off valve 13c, opens the second high-pressure on-off valve 13d, and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully closed state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigerating cycle device 10b in the dehumidifying and heating mode, as shown by the diagonal hatched arrow in FIG. 13, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a and the inlet side passage 22c. The refrigerant circulates in the order of the receiver 23, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11.

Further, the control device 60 appropriately determines the control signals output to the various controlled devices, as in the dehumidification / heating mode desorption step of the second embodiment.

Therefore, in the refrigerating cycle device 10b in the dehumidifying and heating mode, the water-refrigerant heat exchanger 12a and the indoor evaporator 15 form a hot gas cycle that functions as a radiator. Further, in the refrigerating cycle device 10b in the desorption stroke, the receiver 23 functions as a refrigerant passage because the high-temperature vapor-phase refrigerant flows into the receiver 23.

Therefore, in the vehicle air conditioner 1b in the dehumidification / heating mode desorption process, the desiccant material 15a can be regenerated and the vehicle interior can be heated in the same manner as in the dehumidification / heating mode desorption process of the second embodiment. can.

(B-2) Cooling / Dehumidifying / Heating Mode In the adsorption stroke of the cooling / dehumidifying / heating mode, the control device 60 closes the first high-pressure on-off valve 13c, opens the second high-pressure on-off valve 13d, and opens the low-pressure on-off valve 13b. Further, the control device 60 puts the heating expansion valve 14c in the throttle state, the cooling expansion valve 14d in the throttle state, and the cooling expansion valve 14e in the throttle state.

Therefore, in the refrigerating cycle device 10b in the adsorption process of the cooling / dehumidifying / heating mode, as shown by the black arrow in FIG. 13, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the inlet side passage 22c, and the receiver. The refrigerant circulates in the order of 23, the sixth three-way joint 17f of the outlet side passage 22d, the expansion valve 14c for heating, the outdoor heat exchanger 16, the passage 22b for heating, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is a water refrigerant heat exchanger 12a, an inlet side passage 22c, a receiver 23, a sixth three-way joint 17f of the outlet side passage 22d, a fourth three-way joint 17d, a cooling expansion valve 14d, and the like. The refrigerant circulates in the order of the indoor evaporator 15, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the inlet side passage 22c, the receiver 23, the sixth three-way joint 17f of the outlet side passage 22d, the fourth three-way joint 17d, and the cooling expansion valve 14e. The refrigerant circulates in the order of the chiller 19, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11.

That is, in the refrigerating cycle device 10b in the adsorption process of the cooling / dehumidifying / heating mode, the outdoor heat exchanger 16, the indoor evaporator 15, and the chiller 19 are connected in parallel to the refrigerant flow, as in the second embodiment. Switch to circuit.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control signal output to the heating expansion valve 14c, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the outdoor heat exchanger 16 approaches the target degree of superheat.

Further, regarding the control signal output to the cooling expansion valve 14d, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 15 approaches the target degree of superheat. Further, regarding the control signal output to the cooling expansion valve 14e, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the chiller 19 approaches the target degree of superheat.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the adsorption process of the cooling / dehumidifying / heating mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various control target devices. Therefore, in the vehicle air conditioner 1b in the adsorption process of the cooling / dehumidifying / heating mode, the battery 80 can be cooled and the vehicle interior can be dehumidified / heated, as in the second embodiment.

Further, in the adsorption stroke refrigerating cycle device 10b in the cooling / dehumidifying / heating mode, the outlet-side refrigerant of the outdoor heat exchanger 16, the outlet-side refrigerant of the indoor evaporator 15, and the outlet-side refrigerant of the chiller 19 can have a degree of overheating. ..

Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased to improve the heating capacity of the blown air. The amount of heat absorbed by the refrigerant in the indoor evaporator 15 can be increased to improve the cooling capacity of the blown air. Further, the heat absorption amount of the refrigerant in the chiller 19 can be increased to improve the cooling capacity of the battery 80.

Next, in the desorption stroke of the cooling / dehumidifying / heating mode, the control device 60 closes the first high-pressure on-off valve 13c, opens the second high-pressure on-off valve 13d, and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully closed state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigerating cycle device 10b of the dehumidification and heating mode desorption stroke, as shown by the arrow with diagonal hatching in FIG. 13, the refrigerant circuit is such that the refrigerant circulates in the same order as the dehumidification and dehumidification stroke of the single dehumidification and heating mode.

Further, the control device 60 appropriately determines the control signals output to the various controlled devices, as in the dehumidification / heating mode desorption step of the second embodiment. Therefore, in the vehicle air conditioner 1b in the desorption stroke of the cooling / dehumidifying / heating mode, the desiccant material 15a can be regenerated, the battery 80 can be continuously cooled, and the vehicle interior can be heated, as in the second embodiment.

(C-1) Single defrost mode In the single defrost mode, the control device 60 opens the first high-pressure on-off valve 13c, closes the second high-pressure on-off valve 13d, and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in a fully open state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state. Therefore, the refrigerating cycle device 10b in the single defrosting mode is switched to the refrigerant circuit in which the refrigerant circulates in the same order as in the single cooling mode, as shown by the white arrows in FIG.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control signal output to the cooling expansion valve 14d, the control device 60 determines that the outlet-side refrigerant of the indoor evaporator 15 approaches a predetermined target superheat degree.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as in the single defrosting mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices. Therefore, in the vehicle air conditioner 1b in the single dehumidification mode, dehumidification of the outdoor heat exchanger 16 and dehumidification and heating of the vehicle interior can be continued as in the second embodiment.

(C-2) Waste heat defrosting mode In the waste heat defrosting mode, the control device 60 opens the first high-pressure on-off valve 13c, closes the second high-pressure on-off valve 13d, and closes the low-pressure on-off valve 13b. Further, the control device 60 sets the heating expansion valve 14c in the fully open state, the cooling expansion valve 14d in the throttle state, and the cooling expansion valve 14e in the throttle state. Therefore, in the refrigerating cycle device 10b in the single defrosting mode, as shown by the black arrow in FIG. 12, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates in the same order as in the single cooling mode.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control signal output to the cooling expansion valve 14d, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 15 approaches the target degree of superheat. Further, regarding the control signal output to the cooling expansion valve 14e, the control device 60 determines that the degree of superheat of the refrigerant on the outlet side of the chiller 19 approaches the target degree of superheat.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the waste heat defrosting mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices. Therefore, in the vehicle air conditioner 1b in the waste heat defrosting mode, cooling of the battery 80, defrosting of the outdoor heat exchanger 16, and dehumidifying and heating of the vehicle interior can be continued as in the second embodiment.

As described above, according to the vehicle air conditioner 1b of the present embodiment, it is possible to realize comfortable air conditioning in the vehicle interior and appropriate cooling of the heat generating device by switching the operation mode.

Further, the vehicle air conditioner 1b of the present embodiment can also obtain the same effect as the vehicle air conditioner 1a described in the second embodiment. That is, the refrigerating machine oil can be appropriately returned to the compressor 11 regardless of which operation mode is switched, while obtaining the effect of improving the operating efficiency by providing the indoor evaporator 15 coated with the desiccant material 15a.

Further, in the refrigerating cycle apparatus 10b of the present embodiment, since the refrigerant on the outlet side of the heat exchanger functioning as an evaporator can have a degree of superheat, the amount of heat absorbed by the refrigerant in the heat exchanger functioning as an evaporator is increased. Can be made to. As a result, the coefficient of performance of the refrigeration cycle device 10b can be improved, and the operating efficiency of the vehicle air conditioner 1b can be further improved.

(Fourth Embodiment)
In this embodiment, the vehicle air conditioner 1c shown in the overall configuration diagram of FIGS. 14 to 19 will be described. The vehicle air conditioner 1c is an air conditioner with a heat generating device cooling function, similar to the vehicle air conditioner 1a described in the second embodiment.

The vehicle air conditioner 1c includes a refrigeration cycle device 10c, an indoor air conditioner unit 30, a high temperature side heat medium circuit 40a, and a low temperature side heat medium circuit 50a.

Note that, in FIGS. 14 to 19, the indoor air conditioning unit 30 is not shown for the sake of clarity, as in the third embodiment. Therefore, the indoor evaporator 15 of the refrigeration cycle device 10c is arranged in the casing 31 of the indoor air conditioning unit 30. The heater core 42 of the high temperature side heat medium circuit 40a is arranged in the casing 31 of the indoor air conditioning unit 30.

In the refrigeration cycle device 10c, the first three-way joint 17a, the heating expansion valve 14c, the outdoor heat exchanger 16, and the like are abolished with respect to the refrigeration cycle device 10a described in the second embodiment. Therefore, the inlet side of the fourth three-way joint 17d is connected to the outlet of the refrigerant passage of the water refrigerant heat exchanger 12a via the receiver 23. Therefore, in the refrigeration cycle device 10c, the fourth three-way joint 17d becomes a branch portion.

An inlet side of a cooling expansion valve 14d similar to that of the second embodiment is connected to one outlet of the fourth three-way joint 17d. The cooling expansion valve 14d of the present embodiment is an air cooling pressure reducing unit that reduces the pressure of one of the refrigerants branched by the fourth three-way joint 17d.

The refrigerant inlet side of the indoor evaporator 15 as in the first embodiment is connected to the outlet of the cooling expansion valve 14d. The indoor evaporator 15 of the present embodiment is an air cooling heat exchange unit that cools the blown air by evaporating the refrigerant decompressed by the cooling expansion valve 14d.

The inlet side of the cooling expansion valve 14e similar to that of the second embodiment is connected to the other outlet of the fourth three-way joint 17d. The cooling expansion valve 14e of the present embodiment is a cooling pressure reducing unit that reduces the pressure of the other refrigerant branched by the fourth three-way joint 17d.

The inlet side of the refrigerant passage of the chiller 19 as in the second embodiment is connected to the outlet of the cooling expansion valve 14e. The chiller 19 of the present embodiment is a cooling heat exchange unit that exchanges heat between the refrigerant decompressed by the cooling expansion valve 14e and the low temperature side heat medium circulating in the low temperature side heat medium circuit 50a.

The inlet side of the evaporation pressure adjusting valve 20 is connected to the refrigerant outlet of the indoor evaporator 15 and the outlet of the refrigerant passage of the chiller 19. The evaporation pressure adjusting valve 20 of this embodiment individually adjusts the refrigerant pressure in the indoor evaporator 15 and the refrigerant pressure in the chiller 19. The other basic configurations of the refrigerating cycle device 10c are the same as those of the refrigerating cycle device 10a described in the second embodiment.

Next, the high temperature side heat medium circuit 40a will be described. In the high temperature side heat medium circuit 40a, a high temperature side three-way valve 43, a high temperature side radiator 44, and a high temperature side merging portion 45 are added to the high temperature side heat medium circuit 40a described in the second embodiment.

In the high temperature side heat medium circuit 40a, the inflow port side of the high temperature side three-way valve 43 is connected to the outlet of the water passage of the water refrigerant heat exchanger 12a. The high temperature side three-way valve 43 continuously adjusts the flow rate of the heat medium flowing out to the radiator 44 side on the high temperature side and the flow rate of the heat medium flowing out to the heater core 42 side among the heat medium on the high temperature side flowing out from the water refrigerant heat exchanger 12a. It is a possible three types of flow control valve.

The high temperature side three-way valve 43 can also allow the high temperature side heat medium flowing out of the water refrigerant heat exchanger 12a to flow into either the high temperature side radiator 44 or the heater core 42. Therefore, the high temperature side three-way valve 43 is a high temperature side circuit switching unit. The operation of the high temperature side three-way valve 43 is controlled by a control signal output from the control device 60.

The high temperature side radiator 44 is a high temperature side outside air heat exchange unit that exchanges heat between the high temperature side heat medium heated by the water refrigerant heat exchanger 12a and the outside air blown from the outside air fan (not shown). The high temperature side radiator 44 is arranged on the front side in the drive device room, similarly to the outdoor heat exchanger 16 described in the second embodiment. One inlet side of the high temperature side merging portion 45 is connected to the heat medium outlet of the high temperature side radiator 44.

The high temperature side merging portion 45 merges the flow of the heat medium flowing out from the high temperature side radiator 44 and the flow of the heat medium flowing out from the heater core 42. The high temperature side merging portion 45 is a three-way joint similar to the fourth three-way joint 17d and the like. Therefore, the other inlet side of the high temperature side merging portion 45 is connected to the heat medium outlet of the heater core 42 of the present embodiment. The suction port side of the high temperature side heat medium pump 41 is connected to the outlet of the high temperature side merging portion 45.

Next, the low temperature side heat medium circuit 50a will be described. In the low temperature side heat medium circuit 50a, the low temperature side three-way valve 53, the low temperature side radiator 54, and the low temperature side confluence portion 55 are arranged with respect to the low temperature side heat medium circuit 50 described in the second embodiment.

In the low temperature side heat medium circuit 50a, the inflow port side of the low temperature side three-way valve 53 is connected to the outlet of the water passage of the chiller 19. Of the low temperature side heat medium flowing out from the chiller 19, the low temperature side three-way valve 53 causes the heat medium flow rate to flow out to the low temperature side radiator 54 side and flows out to the cooling water passage 80a side of the battery 80 which is the heat exchange unit of the heat medium equipment. It is a three-type flow control valve that can continuously adjust the flow rate of the heat medium.

The basic configuration of the low temperature side three-way valve 53 is the same as that of the high temperature side three-way valve 43. The low temperature side three-way valve 53 can also allow the low temperature side heat medium flowing out of the chiller 19 to flow into either the low temperature side radiator 54 or the cooling water passage 80a of the battery 80. Therefore, the low temperature side three-way valve 53 is a low temperature side circuit switching unit.

The low temperature side radiator 54 is a low temperature side outside air heat exchange unit that exchanges heat between the low temperature side heat medium cooled by the chiller 19 and the outside air blown from the outside air fan (not shown). The low temperature side radiator 54 is located on the front side of the drive unit room and on the downstream side of the outside air flow of the high temperature side radiator 44.

Therefore, the low temperature side radiator 54 causes heat exchange between the outside air after passing through the high temperature side radiator 44 and the low temperature side heat medium. Further, the high temperature side radiator 44 and the low temperature side radiator 54 of the present embodiment are integrated so that the heat of the high temperature side heat medium and the heat of the low temperature side heat medium can be transferred to each other.

Specifically, in the high temperature side radiator 44 and the low temperature side radiator 54 of the present embodiment, some components (heat exchange fins in the present embodiment) are formed of common members. Then, the heat of the high temperature side heat medium and the heat of the low temperature side heat medium can be transferred to each other through some common components. Thereby, for example, the heat of the high temperature side heat medium flowing through the high temperature side radiator 44 can be transferred to the low temperature side radiator 54.

The high temperature side three-way valve 43 of the high temperature side heat medium circuit 40a has the heat medium flow rate supplied to the heater core 42 and the high temperature side radiator 44 among the high temperature side heat media heated by the heat of the refrigerant discharged from the compressor 11. The flow rate of the heat medium supplied to the can be adjusted.

That is, the high temperature side three-way valve 43 can adjust the amount of heat radiated from the high temperature side heat medium to the blown air by the heater core 42 and the amount of heat transferred to the low temperature side radiator 54 via the high temperature side radiator 44. Therefore, the high temperature side three-way valve 43 is a heat amount distribution unit that distributes the amount of heat supplied to the heating unit and the amount of heat supplied to the low temperature side outside air heat exchange unit via the high temperature side outside air heat exchange unit.

Next, the outline of the electric control unit of the vehicle air conditioner 1c will be described with reference to FIG. The control device 60 of the present embodiment controls the operation of various controlled devices 11, 14d, 14e, 20, 32, 33, 34a, 37, 38, 41, 43, 61, 53, etc. connected to the output side. .. Further, in the present embodiment, among the control devices 60, the configuration for controlling the operation of the high temperature side three-way valve 43 is the high temperature side circuit control unit 60f. The configuration for controlling the operation of the low temperature side three-way valve 53, which is the low temperature side circuit switching unit, is the low temperature side circuit control unit 60g.

The configuration of the other vehicle air conditioner 1c is the same as that of the vehicle air conditioner 1a described in the second embodiment.

Next, the operation of the vehicle air conditioner 1c will be described. The vehicle air conditioner 1c can execute the same operation mode as the vehicle air conditioner 1a described in the second embodiment. The operation of each operation mode will be described below.

(A-1) Single cooling mode In the single cooling mode, the control device 60 sets the cooling expansion valve 14d in a throttled state and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigerating cycle device 10c in the single cooling mode, as shown by the white arrow in FIG. 14, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the receiver 23, the cooling expansion valve 14d, and the room. It is switched to a refrigerant circuit in which the refrigerant circulates in the order of the evaporator 15, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity. Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines to stop the low temperature side heat medium pump 51.

As for the high temperature side three-way valve 43, in the control device 60, as shown by the solid line arrow in FIG. 14, the high temperature side heat medium flowing out from the water refrigerant heat exchanger 12a flows into both the high temperature side radiator 44 and the heater core 42. Determine to be a heat medium circuit. Further, in the single cooling mode, the control device 60 controls the operation of the high temperature side three-way valve 43 so that the flow rate of the heat medium flowing into the radiator 44 on the high temperature side is larger than the flow rate of the heat medium flowing into the heater core 42.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as in the single cooling mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigeration cycle device 10c in the single cooling mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 functions as an evaporator, and a steam compression type refrigeration cycle is configured. In the refrigerating cycle device 10c in the single cooling mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. The blown air is cooled by the indoor evaporator 15.

Further, in the high temperature side heat medium circuit 40a in the single cooling mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42 and the high temperature side radiator 44. The high temperature side heat medium flowing into the high temperature side radiator 44 exchanges heat with the outside air and dissipates heat to the outside air. The high-temperature side heat medium that has flowed into the heater core 42 exchanges heat with the blown air and dissipates heat according to the opening degree of the air mix door 34.

Further, in the indoor air conditioning unit 30 in the single cooling mode, the temperature of the blown air is adjusted and blown out to an appropriate place in the vehicle interior as in the single cooling mode of the third embodiment. As a result, cooling of the passenger compartment is realized.

(A-2) Cooling / Cooling Mode In the cooling / cooling mode, the control device 60 sets the cooling expansion valve 14d in the throttled state and the cooling expansion valve 14e in the throttled state.

Therefore, in the refrigerating cycle device 10c in the cooling / cooling mode, as shown by the black arrow in FIG. 15, the refrigerant discharged from the compressor 11 is the water refrigerant heat exchanger 12a, the receiver 23, the cooling expansion valve 14d, and the room. The refrigerant circulates in the order of the evaporator 15, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 circulates in the order of the water refrigerant heat exchanger 12a, the receiver 23, the cooling expansion valve 14e, the chiller 19, the evaporation pressure adjusting valve 20, and the suction port of the compressor 11. Switch to circuit.

That is, in the refrigerating cycle device 10c in the cooling / cooling mode, the indoor evaporator 15 and the chiller 19 are switched to the refrigerant circuit connected in parallel with the refrigerant flow.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity.

As for the high temperature side three-way valve 43, in the control device 60, as shown by the solid line arrow in FIG. 15, the high temperature side heat medium flowing out from the water refrigerant heat exchanger 12a flows into both the high temperature side radiator 44 and the heater core 42. Determine to be a heat medium circuit. Further, in the cooling / cooling mode, the control device 60 controls the operation of the high temperature side three-way valve 43 so that the flow rate of the heat medium flowing into the high temperature side radiator 44 is larger than the flow rate of the heat medium flowing into the heater core 42.

Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines that the low temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Regarding the low temperature side three-way valve 53, the control device 60 becomes a heat medium circuit in which the low temperature side heat medium flowing out of the chiller 19 flows into the cooling water passage 80a of the battery 80, as shown by the broken line arrow in FIG. To decide.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as in the cooling / cooling mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10c in the cooling / cooling mode, a steam compression type refrigerating cycle is configured in which the water-refrigerant heat exchanger 12a functions as a condenser and the indoor evaporator 15 and the chiller 19 function as an evaporator. .. In the refrigerating cycle device 10c in the single cooling mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. The blown air is cooled by the indoor evaporator 15. The low temperature side heat medium is cooled by the chiller 19.

Further, in the high temperature side heat medium circuit 40a in the single cooling mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42 and the high temperature side radiator 44. The high temperature side heat medium flowing into the high temperature side radiator 44 exchanges heat with the outside air and dissipates heat to the outside air.

Further, in the low temperature side heat medium circuit 50a in the cooling / cooling mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows into the cooling water passage 80a of the battery 80. The low temperature side heat medium flowing into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. This cools the battery 80.

Further, in the indoor air conditioning unit 30 in the cooling / cooling mode, the temperature of the blown air is adjusted and blown out to an appropriate place in the vehicle interior as in the cooling / cooling mode of the third embodiment. As a result, cooling of the passenger compartment is realized.

(B-1) Single Dehumidifying and Heating Mode In the adsorption stroke of the single dehumidifying and heating mode, the control device 60 sets the cooling expansion valve 14d in the throttled state and the cooling expansion valve 14e in the throttled state. Therefore, in the refrigerating cycle device 10c in the adsorption process of the single dehumidifying / heating mode, as shown by the black arrow in FIG. 16, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates, as in the cooling / cooling mode.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity.

Regarding the high temperature side three-way valve 43, as shown by the solid line arrow in FIG. 16, the control device 60 has a high temperature side three-way valve so that the high temperature side heat medium flowing out of the water refrigerant heat exchanger 12a flows into the heater core 42. It controls the operation of the valve 43.

Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines that the low temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Regarding the low temperature side three-way valve 53, as shown by the broken line arrow in FIG. 16, the control device 60 controls the low temperature side three-way valve 53 so that the low temperature side heat medium flowing out of the chiller 19 flows into the low temperature side radiator 54. Control the operation of.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the adsorption process of the single dehumidifying / heating mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10c in the adsorption process of the single dehumidifying and heating mode, as shown in the Moriel diagram of FIG. 21, the refrigerant discharged from the compressor 11 (point a21 in FIG. 21) is the water refrigerant heat exchanger 12a. Inflow to. The refrigerant flowing into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and condenses (points a21 to b21 in FIG. 21). The flow of the refrigerant flowing out of the water-refrigerant heat exchanger 12a is branched at the fourth three-way joint 17d.

One of the refrigerants branched at the fourth three-way joint 17d is depressurized by the cooling expansion valve 14d (point b21 → point e21 in FIG. 21) and flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 exchanges heat with the blown air and evaporates (point e21 → point f21 in FIG. 21).

The other refrigerant branched at the fourth three-way joint 17d is depressurized by the cooling expansion valve 14e (points b21 to c21 in FIG. 21) and flows into the chiller 19. The refrigerant flowing into the chiller 19 exchanges heat with the low temperature side heat medium and evaporates (point c21 → point d21 in FIG. 21).

The refrigerant flowing out of the cooling expansion valve 14d and the refrigerant flowing out of the chiller 19 are adjusted to the same pressure by the evaporation pressure adjusting valve 20 and merge at the merging portion 17g. The refrigerant flowing out from the merging portion 17g flows into the accumulator 21 and is separated into gas and liquid. The gas phase refrigerant flowing out of the accumulator 21 is sucked into the compressor 11 and compressed again (point g21 → point a21 in FIG. 21).

That is, in the refrigeration cycle device 10c of the adsorption process in the single dehumidification / heating mode, the water refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and the chiller 19 function as an evaporator. Is configured. Although FIG. 21 has described an example in which the refrigerant evaporation pressure in the indoor evaporator 15 is higher than the refrigerant pressure in the chiller 19, the refrigerant evaporation pressure in the indoor evaporator 15 is higher than the refrigerant pressure in the chiller 19. It may be low.

Then, in the refrigerating cycle device 10c in the adsorption process of the single dehumidifying and heating mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. The blown air is cooled by the indoor evaporator 15. The low temperature side heat medium is cooled by the chiller 19. In other words, in the chiller 19, the low-pressure refrigerant absorbs heat from the low-temperature side heat medium and evaporates.

Further, in the high temperature side heat medium circuit 40a in the adsorption process of the single dehumidifying / heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the low temperature side heat medium circuit 50a in the adsorption process of the single dehumidifying / heating mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows into the low temperature side radiator 54. The low temperature side heat medium flowing into the low temperature side radiator 54 exchanges heat with the outside air and absorbs the heat of the outside air.

Further, in the indoor air-conditioning unit 30 in the adsorption process of the single dehumidification / heating mode, as shown by the dashed arrow in the Moriel diagram of FIG. 21, the air is blown in the same manner as in the adsorption process of the single dehumidification / heating mode of the second embodiment. The temperature of the air is adjusted and it is blown out to the appropriate place in the passenger compartment. Therefore, in the vehicle air conditioner 1c in the adsorption process of the single dehumidifying / heating mode, the dehumidifying / heating of the vehicle interior can be performed by utilizing the adsorption action of the desiccant material 15a as in the second embodiment.

Next, in the dehumidification and heating mode desorption stroke, the control device 60 sets the cooling expansion valve 14d in a throttled state and the cooling expansion valve 14e in a fully closed state. Therefore, in the refrigerating cycle device 10c in the dehumidifying and heating mode, the refrigerating cycle device 10c is switched to a refrigerant circuit in which the refrigerant circulates, as shown by the white arrows in FIG.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity.

Regarding the high temperature side three-way valve 43, as shown by the solid line arrow in FIG. 17, the control device 60 has a high temperature side three-way valve so that the high temperature side heat medium flowing out of the water refrigerant heat exchanger 12a flows into the heater core 42. It controls the operation of the valve 43.

Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines to stop the low temperature side heat medium pump 51.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the desorption step of the single dehumidifying / heating mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10c in the dehumidification and heating mode, as shown in the Moriel diagram of FIG. 22, the refrigerant discharged from the compressor 11 (point a22 in FIG. 22) is a water refrigerant heat exchanger. It flows into 12a. The refrigerant flowing into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and dissipates heat (points a22 → b22 in FIG. 22).

The refrigerant flowing out of the water-refrigerant heat exchanger 12a flows into the cooling expansion valve 14d via the receiver 23 and is depressurized (points b22 to c22 in FIG. 22). The refrigerant decompressed by the cooling expansion valve 14d flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 dissipates heat to the outside air and the desiccant material 15a (points c22 → d22 in FIG. 22).

The refrigerant flowing out of the indoor evaporator 15 is depressurized by the evaporation pressure adjusting valve 20 (point d22 → point e22 in FIG. 22). The vapor phase refrigerant flowing out of the evaporation pressure adjusting valve 20 is sucked into the compressor 11 and compressed again (point e22 → point a22 in FIG. 22).

That is, in the refrigerating cycle device 10c in the dehumidifying and heating mode, the water-refrigerant heat exchanger 12a and the indoor evaporator 15 form a hot gas cycle that functions as a radiator. In the refrigerating cycle device 10c in the desorption stroke, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. Further, in the refrigerating cycle device 10c in the desorption stroke, the receiver 23 functions as a refrigerant passage because the high-temperature vapor-phase refrigerant flows into the receiver 23.

Further, in the high temperature side heat medium circuit 40a in the desorption stroke of the single dehumidifying / heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the indoor air conditioning unit 30 in the dehumidifying and heating mode, as shown by the dashed arrow in the Moliel diagram of FIG. 22, the outside air blown from the indoor blower 32 is similarly shown in the second embodiment. A part of the above passes through the indoor evaporator 15 and is humidified. As a result, the desiccant material 15a is regenerated. The outside air that has passed through the indoor evaporator 15 and is humidified is exhausted to the outside of the vehicle interior through the exhaust port 31b of the exhaust device 38.

Another part of the outside air blown from the indoor blower 32 flows into the heating passage 35a from the auxiliary outside air introduction port 31a via the outside air bypass passage 35c. The outside air flowing into the heating passage 35a is heated by the heater core 42 as blown air and blown out into the vehicle interior. As a result, the interior of the vehicle can be heated even during the dehumidification / removal stroke of the single dehumidifying / heating mode.

(B-2) Cooling / Dehumidifying / Heating Mode In the adsorption stroke of the cooling / dehumidifying / heating mode, the control device 60 sets the cooling expansion valve 14d in the throttled state and the cooling expansion valve 14e in the throttled state. Therefore, in the refrigerating cycle device 10c in the adsorption process of the cooling / dehumidifying / heating mode, as shown by the black arrow in FIG. 18, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates in the same order as the cooling / cooling mode.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity.

Regarding the high temperature side three-way valve 43, as shown by the solid line arrow in FIG. 18, the control device 60 has a high temperature side three-way valve so that the high temperature side heat medium flowing out of the water refrigerant heat exchanger 12a flows into the heater core 42. It controls the operation of the valve 43.

Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines that the low temperature side heat medium pump 51 exerts a predetermined pumping capacity.

As for the low temperature side three-way valve 53, in the control device 60, as shown by the broken line arrow in FIG. 18, the low temperature side heat medium flowing out from the chiller 19 is both the low temperature side radiator 54 and the cooling water passage 80a of the battery 80. The operation of the low temperature side three-way valve 53 is controlled so as to flow into.

If the blown air can be sufficiently reheated by the heat of the battery 80, the total flow rate of the low temperature side heat medium flowing out of the chiller 19 is low so as to flow into the cooling water passage 80a of the battery 80. The operation of the side three-way valve 53 may be controlled.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the adsorption process of the cooling / dehumidifying / heating mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10c in the adsorption process of the cooling / dehumidifying / heating mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and the chiller 19 function as an evaporator. Is configured.

In the refrigerating cycle device 10c in the adsorption process of the cooling / dehumidifying / heating mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12a in the same manner as in the adsorption process in the single dehumidifying / heating mode. The blown air is cooled by the indoor evaporator 15. The low temperature side heat medium is cooled by the chiller 19. In other words, in the chiller 19, the low-pressure refrigerant absorbs heat from the low-temperature side heat medium and evaporates.

Further, in the high temperature side heat medium circuit 40a in the adsorption process of the cooling / dehumidifying / heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the low temperature side heat medium circuit 50a in the adsorption process of the cooling / dehumidifying / heating mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows into the cooling water passage 80a of the low temperature side radiator 54 and the battery 80.

The low temperature side heat medium flowing into the low temperature side radiator 54 exchanges heat with the outside air and absorbs the heat of the outside air. The low temperature side heat medium flowing into the cooling water passage 80a of the battery 80 absorbs the heat of the battery 80. This cools the battery 80.

Further, in the indoor air conditioning unit 30 in the adsorption process of the cooling / dehumidifying / heating mode, the temperature of the blown air is adjusted and blown out to an appropriate place in the vehicle interior as in the adsorption process of the single dehumidifying / heating mode. Therefore, in the vehicle air conditioner 1c in the adsorption process of the single dehumidifying / heating mode, the dehumidifying / heating of the vehicle interior can be performed by utilizing the adsorption action of the desiccant material 15a.

Next, in the desorption stroke of the cooling / dehumidifying / heating mode, the control device 60 sets the cooling expansion valve 14d in the throttled state and the cooling expansion valve 14e in the fully closed state. Therefore, in the refrigerating cycle device 10c in the desorption stroke of the cooling / dehumidifying / heating mode, as shown by the white arrow in FIG. 19, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates in the same order as in the single dehumidifying / heating mode.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, with respect to the control voltage output to the high temperature side heat medium pump 41, the control device 60 determines that the high temperature side heat medium pump 41 exerts a predetermined pumping capacity.

Regarding the high temperature side three-way valve 43, as shown by the solid line arrow in FIG. 19, the control device 60 has a high temperature side three-way valve so that the high temperature side heat medium flowing out of the water refrigerant heat exchanger 12a flows into the heater core 42. It controls the operation of the valve 43.

Further, regarding the control voltage output to the low temperature side heat medium pump 51, the control device 60 determines that the low temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Regarding the low temperature side three-way valve 53, the control device 60 becomes a heat medium circuit in which the low temperature side heat medium flowing out of the chiller 19 flows into the cooling water passage 80a of the battery 80, as shown by the broken line arrow in FIG. To decide.

Therefore, in the refrigeration cycle device 10c in the dehumidification / heating mode desorption stroke, the water refrigerant heat exchanger 12a and the indoor evaporator 15 function as radiators in the hot gas cycle as in the dehumidification / heating mode desorption stroke. Is configured. Then, in the refrigerating cycle device 10a in the desorption stroke, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12c.

Further, in the high temperature side heat medium circuit 40a in the desorption stroke of the cooling / dehumidifying / heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42.

Further, in the low temperature side heat medium circuit 50a in the desorption stroke of the cooling / dehumidifying / heating mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 circulates between the chiller 19 and the cooling water passage 80a of the battery 80. do. Therefore, during the desorption stroke, the battery 80 can be continuously cooled by the low temperature side heat medium cooled during the adsorption stroke, as in the second embodiment.

Further, in the indoor air conditioning unit 30 in the dehumidification / heating mode desorption process, the desiccant material 15a of the indoor evaporator 15 is regenerated in the same manner as in the dehumidification / heating mode desorption process. The outside air humidified when passing through the indoor evaporator 15 is exhausted to the outside of the vehicle interior through the exhaust port 31b of the exhaust device 38.

Further, the outside air flowing into the heating passage 35a through the outside air bypass passage 35c exchanges heat with the high temperature side heat medium heated by the water refrigerant heat exchanger 12a when passing through the heater core 42 as blown air. It is heated and blown into the passenger compartment. As a result, the interior of the vehicle can be heated even during the desorption stroke of the cooling / dehumidifying / heating mode.

(C) Defrosting mode In the vehicle air conditioner 1c, in the dehumidifying / heating mode, the low temperature side radiator 54 heats the blown air using the heat absorbed from the outside air by the low temperature side heat medium as a heat source. Therefore, frost may occur on the low temperature side radiator 54 in the dehumidifying / heating mode. Therefore, in the defrosting mode of the present embodiment, the low temperature side radiator 54 is defrosted.

(C-1) Single defrosting mode In the single defrosting mode, the control device 60 sets the cooling expansion valve 14d in a throttled state and the cooling expansion valve 14e in a fully closed state. Therefore, the refrigerating cycle device 10c in the single cooling mode is switched to the refrigerant circuit in which the refrigerant circulates in the same order as in the single cooling mode, as shown by the white arrows in FIG.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, the control voltage output to the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 is determined in the same manner as in the single cooling mode.

As for the high temperature side three-way valve 43, in the control device 60, as shown by the solid line arrow in FIG. 14, the high temperature side heat medium flowing out from the water refrigerant heat exchanger 12a is the high temperature side radiator 44, as in the single cooling mode. It is determined that the heat medium circuit flows into both the heater core 42 and the heater core 42. Therefore, the high-temperature side three-way valve 43, which is a heat distribution unit, increases the flow rate of the high-temperature side heat medium flowing into the high-temperature side radiator 44 in the single dehumidification mode as compared with the single dehumidification / heating mode.

As described above, the high temperature side radiator 44 and the low temperature side radiator 54 of the present embodiment are integrated so that the heat of the high temperature side heat medium can be transferred to the low temperature side radiator 54. Therefore, the high temperature side three-way valve 43 increases the amount of heat supplied to the low temperature side radiator 54 in the single dehumidification mode as compared with the single dehumidification / heating mode.

The determination of the control signal and the like output to the other controlled devices is determined in the same manner as in the single defrosting mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10c in the single defrosting mode, as shown in the Moriel diagram of FIG. 23, the refrigerant discharged from the compressor 11 (point a23 in FIG. 23) flows into the water refrigerant heat exchanger 12a. .. The refrigerant flowing into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and condenses (points a23 → b23 in FIG. 23).

The refrigerant flowing out of the water-refrigerant heat exchanger 12a is depressurized by the cooling expansion valve 14d (points b23 to c23 in FIG. 23) and flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 exchanges heat with the blown air and evaporates (point d23 → point e23 in FIG. 23). The refrigerant flowing out of the indoor evaporator 15 is sucked into the compressor 11 via the accumulator 21 and compressed again (point f23 → point a23 in FIG. 23).

That is, in the refrigeration cycle device 10c in the single defrost mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 functions as an evaporator, forming a steam compression type refrigeration cycle. In the refrigerating cycle device 10c in the single cooling mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. The blown air is cooled by the indoor evaporator 15.

Further, in the high temperature side heat medium circuit 40a in the single defrosting mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42 and the high temperature side radiator 44.

The heat of the high temperature side heat medium that has flowed into the high temperature side radiator 44 is transferred to the integrated low temperature side radiator 54. As a result, the frost on the low temperature radiator 54 is melted and removed. That is, the low temperature side radiator 54 is defrosted.

Further, in the indoor air conditioning unit 30 in the independent defrosting mode, the blown air cooled and dehumidified by the indoor evaporator 15 passes through the heater core 42, as schematically shown by the broken line arrow in the Moriel diagram of FIG. 23. At that time, the water-refrigerant heat exchanger 12a reheats the heat radiated by the refrigerant as a heat source. Therefore, the dehumidifying and heating of the vehicle interior can be continued.

(C-2) Waste heat defrosting mode In the waste heat defrosting mode, the control device 60 sets the cooling expansion valve 14d in the throttled state and the cooling expansion valve 14e in the throttled state. Therefore, in the refrigerating cycle device 10c in the waste heat defrosting mode, as shown by the black arrow in FIG. 15, the refrigerant circuit is switched to the refrigerant circuit in which the refrigerant circulates in the same order as the cooling / cooling mode.

Further, the control device 60 appropriately determines control signals output to various controlled devices. For example, the control voltage output to the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 is determined in the same manner as in the cooling / cooling mode.

Further, regarding the high temperature side three-way valve 43, as in the cooling / cooling mode, in the control device 60, as shown by the solid line arrow in FIG. 15, the high temperature side heat medium flowing out from the water refrigerant heat exchanger 12a is the high temperature side radiator 44. It is determined that the heat medium circuit flows into both the heater core 42 and the heater core 42. Therefore, the high temperature side three-way valve 43 increases the flow rate of the high temperature side heat medium flowing into the high temperature side radiator 44 in the waste heat dehumidification mode as compared with the cooling dehumidification / heating mode.

Further, regarding the low temperature side three-way valve 53, in the control device 60, as shown by the broken line arrow in FIG. 15, the low temperature side heat medium flowing out from the chiller 19 goes to the cooling water passage 80a of the battery 80, as in the cooling cooling mode. Determine to be an inflowing heat medium circuit.

The determination of the control signal or the like output to the other controlled device is determined in the same manner as the waste heat defrosting mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to various controlled devices.

Therefore, in the refrigerating cycle device 10c in the waste heat defrosting mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and the chiller 19 form a steam compression type refrigerating cycle that functions as an evaporator. Will be done. In the refrigerating cycle device 10c in the single cooling mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 12a. The blown air is cooled by the indoor evaporator 15. The low temperature side heat medium is cooled by the chiller 19.

Further, in the high temperature side heat medium circuit 40a in the waste heat defrosting mode, the high temperature side heat medium pressure-fed from the high temperature side heat medium pump 41 flows into the water refrigerant heat exchanger 12a. The high temperature side heat medium heated by the water refrigerant heat exchanger 12a flows into the heater core 42 and the high temperature side radiator 44.

The heat of the high temperature side heat medium that has flowed into the high temperature side radiator 44 is transferred to the integrated low temperature side radiator 54. As a result, the frost on the low temperature radiator 54 is melted and removed. That is, the low temperature side radiator 54 is defrosted.

Further, in the low temperature side heat medium circuit 50a in the waste heat defrosting mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows into the cooling water passage 80a of the battery 80. The low temperature side heat medium flowing into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. This cools the battery 80.

Further, in the indoor air conditioning unit 30 in the single dehumidification mode, the blown air cooled and dehumidified by the indoor evaporator 15 is reheated by the heater core 42, as in the waste heat defrost mode of the third embodiment. This makes it possible to continue dehumidifying and heating the interior of the vehicle.

As described above, according to the vehicle air conditioner 1c of the present embodiment, it is possible to realize comfortable air conditioning in the vehicle interior and appropriate cooling of the heat generating device by switching the operation mode.

Further, in the vehicle air conditioner 1c of the present embodiment, the desiccant material 15a is applied to the indoor evaporator 15. Therefore, the operating efficiency can be improved in the same manner as that of the vehicle air conditioner 1 of the first embodiment.

Further, in the dehumidification mode, the flow rate of the high temperature side heat medium that the high temperature side three-way valve 43 flows into the high temperature side radiator 44 is increased as compared with the dehumidification heating mode. That is, in the dehumidification mode, the amount of heat supplied to the low temperature side radiator 54 via the high temperature side radiator 44 is increased as compared with the dehumidification heating mode. Therefore, the frost can be melted and removed from the low temperature radiator 54.

Further, in the defrosting mode, the high temperature side three-way valve 43 also supplies the high temperature side heat medium to the heater core 42. Therefore, even if the blown air is cooled by the indoor evaporator 15 in the defrosting mode, it can be reheated by the heater core 42. As a result, the temperature drop in the air-conditioned space can be suppressed even if the rotation speed of the compressor 11 is determined so that the refrigerating machine oil can be appropriately returned to the compressor 11.

Therefore, according to the vehicle air conditioner 1c of the present embodiment, the same effect as that of the vehicle air conditioner 1 described in the first embodiment can be obtained. That is, the refrigerating machine oil can be appropriately returned to the compressor 11 regardless of which operation mode is switched, while obtaining the effect of improving the operating efficiency by providing the indoor evaporator 15 coated with the desiccant material 15a.

Further, in the vehicle air conditioner 1c of the present embodiment, the cooling water passage 80a of the battery 80 is provided as a heat exchange unit for the heat medium device. According to this, the battery 80 can be cooled.

Further, in the waste heat dehumidification mode, the low temperature side three-way valve 53 switches the low temperature side heat medium circuit 50a so that the low temperature side heat medium is circulated between the chiller 19 and the cooling water passage 80a of the battery 80. According to this, the waste heat of the battery 80 can be used as a heat source for defrosting the outdoor heat exchanger 16 (another embodiment).
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

(1) In the above-described embodiment, an example in which the air conditioner according to the present invention is applied to the vehicle air conditioners 1 to 1c has been described, but the present invention is not limited thereto. For example, the air conditioner according to the present invention may be applied to a stationary air conditioner.

Further, in the vehicle air conditioners 1a to 1c, an example of cooling the battery 70 as a heat generating device has been described, but the present invention is not limited to this. For example, in-vehicle devices that generate heat during operation, such as an electric motor for driving that outputs driving force for driving, an inverter that supplies electric power to the electric motor, a transformer axle that is a power transmission mechanism, and a control device for an advanced driving support system. It may be cooled. When applied to an air conditioner applicable to a stationary air conditioner, other heat generating devices may be cooled.

(2) The operation modes in which the vehicle air conditioners 1 to 1c can be executed are not limited to those described in the above-described embodiment. In the vehicle air conditioners 1 to 1c, the above-mentioned effect can be obtained if at least the dehumidifying / heating mode and the defrosting mode described in each embodiment can be switched. That is, the refrigerating machine oil can be appropriately returned to the compressor 11 while obtaining the effect of improving the operating efficiency by providing the heat exchanger having the adsorption portion.

Therefore, the vehicle air conditioners 1 to 1c may be capable of executing another operation mode. For example, in the vehicle air conditioner 1a described in the second embodiment, the series dehumidification / heating mode may be executed as another dehumidification / heating mode.

Specifically, the high-pressure on-off valve 13a of the refrigeration cycle device 10a is closed, and the low-pressure on-off valve 13b is closed. The heating expansion valve 14c is in a throttled state, and the cooling expansion valve 14d and the cooling expansion valve 14e are in a fully closed state. Other components may be controlled in the same manner as in the dehumidifying / heating mode. Therefore, in the series dehumidification / heating mode, the outdoor heat exchanger 16 and the indoor evaporator 15 are switched to the refrigerant circuit connected in series with the refrigerant flow.

Further, for example, in the vehicle air conditioner 1a described in the second embodiment, the heating mode may be further executed. In the heating mode, the heated blast air is blown into the vehicle interior without dehumidifying by cooling the blast air with the indoor evaporator 15.

Specifically, the high-pressure on-off valve 13a of the refrigeration cycle device 10a is closed, and the low-pressure on-off valve 13b is opened. Further, the heating expansion valve 14c is set to the throttle state, and the cooling expansion valve 14d and the cooling expansion valve 14e are set to the fully closed state. Other components may be controlled in the same manner as in the cooling mode. According to this, it is possible to realize heating in the vehicle interior by blowing out the blown air heated by the heater core 42 into the vehicle interior.

Further, for example, the heating mode may be executed in the vehicle air conditioner 1b described in the third embodiment.

Specifically, the low-pressure on-off valve 13b of the refrigeration cycle device 10b is opened, the first high-pressure on-off valve 13c is closed, and the second high-pressure on-off valve 13d is opened. Further, the heating expansion valve 14c is set to the throttle state, and the cooling expansion valve 14d and the cooling expansion valve 14e are set to the fully closed state. Other components may be controlled in the same manner as in the cooling mode. According to this, it is possible to realize heating in the vehicle interior by blowing out the blown air heated by the heater core 42 into the vehicle interior.

Further, for example, the heating mode may be executed in the vehicle air conditioner 1c described in the fourth embodiment.

Specifically, the cooling expansion valve 14d of the refrigeration cycle device 10c is fully closed, and the cooling expansion valve 14e is in a throttled state. Further, the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 are operated so as to exert a predetermined pumping capacity. Further, the high temperature side three-way valve 43 is operated so that the high temperature side heat medium flows into the heater core 42 side. Further, the low temperature side three-way valve 53 is operated so that the low temperature side heat medium flows into the low temperature side radiator 54.

According to this, it is possible to realize heating in the vehicle interior by blowing out the blown air heated by the heater core 42 into the vehicle interior.

Further, in the vehicle air conditioners 1a to 1c described in the second to fourth embodiments, defrosting may be performed using only the waste heat of the heat generating device as a heat source. Specifically, the cooling expansion valve 14d may be fully closed in the waste heat defrosting mode.

(3) The execution conditions for executing each operation mode or the switching conditions for switching the operation modes are not limited to those disclosed in the above-described embodiment.

For example, during the execution of the dehumidifying / heating mode, the frost formation condition is satisfied when the time Tmf2 in which the outside air temperature Tam is continuously equal to or less than the reference frost outside temperature Ktamf becomes equal to or more than the reference frost formation time KTmf. May be determined. For example, it may be determined that the termination condition is satisfied when the outdoor unit temperature Tout becomes equal to or higher than the predetermined reference defrosting temperature KToutdf during the execution of the defrosting mode.

For example, during the execution of each operation mode, the battery 80 needs to be cooled when the low temperature side heat medium temperature TWL detected by the low temperature side heat medium temperature sensor 61 m is equal to or higher than the predetermined reference heat medium temperature KTWL. It may be determined that. Further, when the low temperature side heat medium temperature TWL is lower than the reference heat medium temperature KTWL, it may be determined that the battery 80 does not need to be cooled.

For example, in the dehumidifying / heating mode, even if the control signal output to the compressor 11 is determined so that the high temperature side heat medium temperature TWH detected by the high temperature side heat medium temperature sensor 61k approaches the target high temperature side heat medium TWHO. good.

(4) Each configuration of the refrigerating cycle apparatus 10, 10a to 10c is not limited to those disclosed in the above-described embodiment.

In the refrigeration cycle device 10, an example in which a four-way valve 13 is adopted as a refrigerant circuit switching unit has been described, but the present invention is not limited to this. For example, a refrigerant circuit switching unit may be formed by combining a plurality of (for example, four) on-off valves.

In the refrigeration cycle devices 10a to 10c, an example in which the evaporation pressure adjusting valve 20 is adopted as the pressure adjusting unit has been described, but the present invention is not limited to this. For example, a mechanical evaporation pressure adjusting valve that maintains the refrigerant evaporation pressure in the indoor evaporator 15 or higher may be arranged in the refrigerant flow path from the refrigerant outlet of the indoor evaporator 15 to the confluence portion 17g. As the mechanical evaporation pressure adjusting valve, a variable throttle mechanism that increases the valve opening degree as the pressure of the refrigerant on the refrigerant outlet side of the indoor evaporator 15 rises can be adopted.

Further, in the above-described embodiment, an example in which R1234yf is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C and the like may be adopted. Alternatively, a mixed refrigerant or the like in which a plurality of these refrigerants are mixed may be adopted.
(5) The configuration of the indoor air conditioning unit 30 is not limited to that disclosed in the above-described embodiment. For example, a passage dedicated to the inside air that exclusively circulates the inside air and a passage dedicated to the outside air that exclusively circulates the outside air may be formed in the casing 31. Then, a heating passage and a cold air bypass passage may be formed in both the inside air exclusive passage and the outside air exclusive passage.

Further, in the adsorption process of the dehumidifying / heating mode of the above-described embodiment, an example in which the operation of the inside / outside air switching device 33 is controlled so that the inside air introduction port is fully opened and the outside air introduction port is fully closed has been described. Not limited. In the adsorption process, the operation of the inside / outside air switching device 33 may be controlled so that the ratio of the inside air in the blown air flowing into the indoor evaporator 15 is larger than the ratio of the outside air.

Similarly, in the dehumidifying / heating mode desorption stroke, an example in which the operation of the inside / outside air switching device 33 is controlled so that the inside air introduction port is fully closed and the outside air introduction port is fully opened has been described, but the present invention is not limited thereto. In the desorption stroke, the operation of the inside / outside air switching device 33 may be controlled so that the ratio of the outside air in the blown air flowing into the indoor evaporator 15 is larger than the ratio of the inside air.

Further, in the cooling mode and the defrosting mode, an example in which the operation of the inside / outside air switching device 33 is controlled so that the inside air introduction port is fully closed and the outside air introduction port is fully opened has been described, but the present invention is not limited thereto. In the cooling mode and the defrosting mode, the operation of the inside / outside air switching device 33 may be controlled so that the ratio of the outside air in the blown air flowing into the indoor evaporator 15 is larger than the ratio of the inside air.

Further, in the above-described embodiment, the example in which the outside air bypass passage 35c is provided has been described, but the outside air bypass passage 35c may be abolished and the outside air may be introduced directly from the auxiliary outside air introduction port 31a. In this case, it is desirable to provide a dedicated auxiliary outside air blower for allowing the outside air to flow into the auxiliary outside air introduction port 31a. Then, when the control device 60 opens the auxiliary outside air introduction port 31a, the auxiliary outside air blower may be activated.

(6) The configurations of the high temperature side heat medium circuits 40 and 40a and the low temperature side heat medium circuits 50 and 50a are not limited to those disclosed in the above-described embodiment. For example, an electric heater as an auxiliary heat source for heating the high temperature side heat medium may be arranged in the high temperature side heat medium circuit 40.

Further, the high temperature side heat medium circuit 40 is provided with a bypass passage for passing the high temperature side heat medium by bypassing the heater core 42, and the high temperature side heat medium flow rate flowing into the heater core 42 and the high temperature side heat medium flow rate flowing into the bypass passage are provided. A three-way valve that adjusts the flow rate ratio may be arranged. Then, the three-way valve may be used as a heating amount adjusting unit.

Further, in the above-described embodiment, an example in which an ethylene glycol aqueous solution is used as the high-temperature side heat medium and the low-temperature side heat medium has been described, but the heat medium is not limited to this. For example, dimethylpolysiloxane, a solution containing nanofluid or the like, an antifreeze solution, an aqueous liquid refrigerant containing alcohol or the like, a liquid medium containing oil or the like may be adopted.

(7) Further, the means disclosed in each of the above embodiments may be appropriately combined to the extent practicable.

For example, as the heating unit of the vehicle air conditioner 1 described in the first embodiment, the constituent devices of the water refrigerant heat exchanger 12a and the high temperature side heat medium circuit 40 may be adopted. Similarly, the indoor condenser 12 may be adopted as the heating unit of the vehicle air conditioners 1a and 1b described in the second and third embodiments.

1-1c ... Vehicle air conditioner, 10-10c ... Refrigeration cycle device, 11 ... Compressor,
12 ... Indoor condenser (heating part), 12a ... Water refrigerant heat exchanger (heating part),
13 ... Four-way valve (refrigerant circuit switching unit), 13a ... High-pressure on-off valve (refrigerant circuit switching unit),
13b ... High-pressure on-off valve (refrigerant circuit switching unit), 13c ... First high-pressure on-off valve (refrigerant circuit switching unit),
13d ... Second high-pressure on-off valve (refrigerant circuit switching section),
14a ... 1st expansion valve (1st pressure reducing part), 14b ... 2nd expansion valve (2nd pressure reducing part),
14c ... Heating expansion valve (outdoor decompression section), 14d ... Cooling expansion valve (cooling decompression section),
14e ... Cooling expansion valve (cooling decompression unit),
15 ... Indoor evaporator (heat exchange part for cooling), 15a ... Desiccant material (adsorption part),
16 ... Outdoor heat exchanger (outdoor heat exchanger),
17a, 17d ... 1st and 4th three-way joints (branch part), 17g ... merging part 19 ... chiller (cooling heat exchange part), 20 ... evaporation pressure adjusting valve (pressure adjusting part),
40, 40a ... High temperature side heat medium circuit (heating part), 50, 50a ... Low temperature side heat medium circuit

Claims (10)

A compressor (11) that compresses and discharges the refrigerant mixed with refrigerating machine oil, and
A heating unit (12, 12a, 40) that heats the blown air blown to the air-conditioned space using the refrigerant discharged from the compressor as a heat source.
A first decompression unit (14a) and a second decompression unit (14b) for depressurizing the refrigerant,
An air cooling heat exchange unit (15) that evaporates the refrigerant and cools the blown air before it is heated by the heating unit.
An outdoor heat exchange unit (16) that exchanges heat between the refrigerant and the outside air,
A refrigerant circuit switching unit (13) for switching the refrigerant circuit for circulating the refrigerant is provided.
The air cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air.
The refrigerant circuit switching unit is
In the dehumidifying / heating mode for dehumidifying and heating the air-conditioned space, the refrigerant discharged from the compressor is used in the heating unit, the first decompression unit, the air cooling heat exchange unit, the outdoor heat exchange unit, and the outdoor heat exchange unit. Switch to the refrigerant circuit that circulates in the order of the suction side of the compressor,
In the defrosting mode for removing frost on the outdoor heat exchange section, the refrigerant discharged from the compressor is used in the heating section, the outdoor heat exchange section, the second decompression section, and the air cooling heat. An air conditioner that switches to a refrigerant circuit that circulates in the order of the exchange unit and the suction side of the compressor. A compressor (11) that compresses and discharges the refrigerant mixed with refrigerating machine oil, and
A heating unit (12, 12a, 40) that heats the blown air blown to the air-conditioned space using the refrigerant discharged from the compressor as a heat source.
A branch portion (17a) that branches the flow of the refrigerant flowing out of the heating portion, and a branch portion (17a).
An outdoor decompression unit (14c) for depressurizing the refrigerant, a cooling decompression unit (14d, 14e), and the like.
An outdoor heat exchange unit (16) that exchanges heat between the refrigerant decompressed by the outdoor decompression unit and the outside air.
A cooling heat exchange unit (15, 19, 50) that evaporates the refrigerant decompressed by the cooling decompression unit to cool the object to be cooled, and a cooling heat exchange unit (15, 19, 50).
A confluence section (17 g) that merges the flow of the refrigerant flowing out of the cooling heat exchange section and the flow of the refrigerant flowing out of the outdoor heat exchange section and flows out to the suction side of the compressor.
A refrigerant circuit switching unit (13a ... 13d) for switching the refrigerant circuit for circulating the refrigerant is provided.
The cooling heat exchange unit has an air cooling heat exchange unit (15) for cooling the blown air before being heated by the heating unit.
The air cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air.
The cooling decompression unit has an air cooling decompression unit (14d) for depressurizing the refrigerant flowing into the air cooling heat exchange unit.
The refrigerant circuit switching unit is
In the dehumidifying / heating mode for dehumidifying and heating the air-conditioned space, the refrigerant discharged from the compressor is used in the heating section, the branch section, the outdoor decompression section, the outdoor heat exchange section, the confluence section, and the above. While circulating in the order of the suction side of the compressor, the refrigerant discharged from the compressor is circulated in the heating section, the branch section, the air cooling decompression section, the air cooling heat exchange section, the confluence section, and the above. Switch to the refrigerant circuit that circulates in the order of the suction side of the compressor,
In the defrosting mode for removing frost on the outdoor heat exchange section, the refrigerant discharged from the compressor is used in the heating section, the outdoor heat exchange section, the cooling decompression section, and the cooling heat exchange. An air conditioner that switches to a refrigerant circuit that circulates in the order of the unit and the suction side of the compressor. The cooling heat exchange unit has a heat medium cooling heat exchange unit (19) for cooling a heat generating device (80) that generates heat during operation.
The cooling decompression unit has a heat medium cooling decompression unit (14e) for depressurizing the refrigerant flowing into the heat medium cooling heat exchange unit.
The refrigerant circuit switching unit is
The air conditioner according to claim 2, wherein in the defrosting mode, the refrigerant flowing out of the outdoor heat exchange section is switched to a refrigerant circuit that flows into the heat medium cooling decompression section. A compressor (11) that compresses and discharges the refrigerant mixed with refrigerating machine oil, and
A heating unit (12a, 40a) that heats the blown air blown to the air-conditioned space using the refrigerant discharged from the compressor as a heat source.
A branch portion (17d) that branches the flow of the refrigerant flowing out of the heating portion, and a branch portion (17d).
An air cooling decompression unit (14d) that decompresses one of the refrigerants branched at the branch portion, and a decompression unit (14d).
An air cooling heat exchange unit (15) that evaporates the refrigerant decompressed by the air cooling decompression unit and cools the blown air before being heated by the heating unit.
The low temperature side heat medium circuit (50a) that circulates the low temperature side heat medium,
A heat medium cooling decompression unit (14e) for depressurizing the other refrigerant branched at the branch portion, and a decompression unit (14e).
A heat medium cooling heat exchange unit (19) for heat exchange between the refrigerant decompressed by the heat medium cooling decompression unit and the low temperature side heat medium.
A confluence portion (17 g) that merges the flow of the refrigerant flowing out of the air cooling heat exchange section and the flow of the refrigerant flowing out of the heat medium cooling heat exchange section and flows out to the suction side of the compressor. ,
A low-temperature side outside air heat exchange unit (54) arranged in the low-temperature side heat medium circuit to exchange heat between the low-temperature side heat medium and the outside air.
A heat quantity distribution unit (43) for distributing the amount of heat supplied to the heating unit and the amount of heat supplied to the low temperature side outside air heat exchange unit among the heat contained in the refrigerant discharged from the compressor is provided.
The air cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air.
The heat distribution unit is
In the dehumidifying / heating mode for dehumidifying and heating the air-conditioned space, the heat of the refrigerant discharged from the compressor is supplied to the heating unit.
An air conditioning device that increases the amount of heat supplied to the low temperature side outside air heat exchange section in the defrosting mode for removing frost on the low temperature side outside air heat exchange section as compared with the dehumidifying heating mode. A heat medium device heat exchange unit (80a) arranged in the low temperature side heat medium circuit to exchange heat between the low temperature side heat medium and a heat generating device (80) that generates heat during operation.
A low temperature side circuit switching unit (53) for switching the circuit configuration of the low temperature side heat medium circuit is provided.
The low temperature side circuit switching unit is a low temperature side heat medium circuit so as to circulate the low temperature side heat medium between the heat medium cooling heat exchange unit and the heat medium equipment heat exchange unit in the defrosting mode. The air conditioner according to claim 4. The heating unit includes a high-temperature side heat medium circuit (40a) that circulates the high-temperature side heat medium, and a heat medium heating heat exchange unit (12a) that exchanges heat between the high-temperature side heat medium and the refrigerant discharged from the compressor. , And an air heating heat exchange unit (42) for heat exchange between the high temperature side heat medium and the blown air.
The heat distribution section has a flow rate of the high temperature side heat medium supplied to the air heating heat exchange section and a flow rate of the high temperature side heat medium supplied to a portion capable of transferring heat to the low temperature side outside air heat exchange section. The air conditioner according to claim 4 or 5, which is coordinated with. The inside / outside air ratio adjusting unit (33) for adjusting the ratio of the outside air to the inside air in the blown air flowing into the air cooling heat exchange unit is provided.
In the adsorption process of adsorbing the moisture to the adsorption unit in the dehumidifying and heating mode, the inside / outside air ratio adjusting unit sets the ratio of the inside air in the blown air flowing into the air cooling heat exchange unit from the ratio of the outside air. The air conditioner according to any one of claims 1 to 6, which also increases. The inside / outside air ratio adjusting unit (33) for adjusting the ratio of the outside air to the inside air in the blown air flowing into the air cooling heat exchange unit is provided.
In the desorption process of desorbing the moisture from the suction portion in the dehumidifying / heating mode, the inside / outside air ratio adjusting unit sets the ratio of the outside air in the blown air flowing into the air cooling heat exchange unit to the inside air. The air conditioner according to any one of claims 1 to 7, wherein the ratio is increased more than the ratio. An exhaust unit (38) for exhausting the blown air that has passed through the air cooling heat exchange unit to the outside of the air-conditioned space is provided.
The one according to any one of claims 1 to 8, wherein the exhaust unit exhausts the blown air to the outside of the air-conditioned space during the desorption stroke for desorbing the moisture from the adsorption unit in the dehumidifying / heating mode. Air conditioner. A heating amount adjusting unit (34, 41) for adjusting the heating amount of the blown air in the heating unit is provided.
The air conditioner according to any one of claims 1 to 9, wherein the heating amount adjusting unit reduces the heating amount in the dehumidification mode as compared with the dehumidification / heating mode.

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