JP7655710B2 - Air conditioning equipment - Google Patents

Description

The present invention relates to an air conditioner equipped with a heat exchanger having an adsorption section.

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

The refrigeration cycle device of Patent Document 1 is equipped with multiple heat exchangers and is configured to be able to switch the refrigerant circuit depending on the operating mode. For example, in a dehumidification and heating mode that dehumidifies and heats the vehicle interior, the refrigerant circuit is switched to one in which the temperature control heat exchanger functions as a condenser and the humidity control heat exchanger and the exterior heat exchanger function as evaporators.

As a result, in the vehicle air conditioning system of Patent Document 1, the ventilation air that has been cooled and dehumidified in the humidity control heat exchanger is reheated in the temperature control heat exchanger and blown out into the vehicle cabin, thereby realizing dehumidification and heating of the vehicle cabin.

Furthermore, the vehicle air conditioning system of Patent Document 1 employs a heat exchanger (specifically, a heat exchanger with a desiccant material applied to its outer surface) that has an adsorption section that adsorbs moisture contained in the blown air as a heat exchanger for humidity adjustment. In the dehumidification 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 by the adsorption section.

As a result, the vehicle air conditioning system of Patent Document 1 reduces the energy consumed to dehumidify the air being blown in dehumidifying heating mode, improving operating efficiency.

Patent Document 2 also discloses an air conditioning system having a refrigeration cycle device. The refrigeration cycle device of Patent Document 2 is equipped with an indoor heat exchanger and an outdoor heat exchanger, and is configured to be able to switch the refrigerant circuit depending on the operation mode. Furthermore, the air conditioning system of Patent Document 2 employs a heat exchanger having an adsorption section similar to that of Patent Document 1 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 during a heating mode in which the room is heated. Also, during a defrost mode in which frost that has built up on the outdoor heat exchanger is removed, the refrigerant circuit switches to a refrigerant circuit in which the outdoor heat exchanger functions as a condenser and the indoor heat exchanger functions as an evaporator.

Furthermore, in the air conditioning system of Patent Document 2, in the defrost mode, the heat of adsorption generated when the adsorption section of the indoor heat exchanger adsorbs moisture contained in the blown air is used as a heat source for melting and removing the frost on the outdoor heat exchanger.

As a result, the air conditioning system of Patent Document 2 aims to prevent the temperature in the space to be air-conditioned from dropping when switching from heating mode to defrost mode.

JP 2018-176936 A JP 2019-66090 A

However, even in the vehicle air conditioning system of Patent Document 1, frost may form on the exterior heat exchanger that functions as an evaporator in the dehumidification heating mode. Therefore, it is conceivable that the vehicle air conditioning system of Patent Document 1 may also operate in a defrosting mode similar to the air conditioning system of Patent Document 2.

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

Here, in order to suppress the temperature drop in the air-conditioned space after switching from the dehumidifying heating mode to the defrost mode, it is necessary to suppress the drop in the refrigerant evaporation temperature in the indoor heat exchanger. To achieve this, it is desirable to reduce the compressor rotation speed after switching from the dehumidifying heating mode to the defrost mode.

However, the required refrigerant flow rate required to circulate through the cycle in defrost mode is less than the required refrigerant flow rate in dehumidification heating mode. For this reason, if the rotation speed of the compressor of the refrigeration cycle device is reduced in defrost mode in order to suppress the drop in temperature of the blown air after switching from dehumidification heating mode to defrost mode, there is a possibility that the refrigeration oil mixed into the refrigerant cannot be returned to the compressor.

In other words, in the vehicle air conditioning system of Patent Document 1, in the dehumidification heating mode, the adsorption action of the adsorption unit can be used to improve the operating efficiency, but when the system is operated in the defrost mode, it becomes impossible to properly return refrigerant oil to the compressor. As a result, there is a risk that this could have a negative impact on the durability and life of the compressor.

In view of the above, the present invention aims to provide an air conditioner that can appropriately return refrigeration oil to the compressor while obtaining the effect of improving the operating efficiency by providing a heat exchanger having an adsorption section.

In order to achieve the above-mentioned object, the air conditioning system described in claim 1 is an air conditioning system applied to a vehicle, and includes a compressor (11), a heating section (12, 12a, 40), a first pressure reduction section (14a), a second pressure reduction section (14b), an air cooling heat exchange section (15), an outdoor heat exchange section (16), a refrigerant circuit switching section (13), an inside/outside air ratio adjustment section (33), an exhaust section (38), and an auxiliary outside air introduction section (37).

The compressor compresses and discharges a refrigerant mixed with refrigeration oil. The heating section heats the blown air to be blown to the space to be air-conditioned using the refrigerant discharged from the compressor as a heat source. The first and second pressure reducing sections reduce the pressure of the refrigerant. The air cooling heat exchange section evaporates the refrigerant and cools the blown air before it is heated by the heating section. The outdoor heat exchange section exchanges heat between the refrigerant and outside air. The refrigerant circuit switching section switches the refrigerant circuit that circulates the refrigerant. The inside/outside air ratio adjustment section (33) adjusts the ratio of outside air and inside air in the blown air flowing into the air cooling heat exchange section. The exhaust section (38) exhausts the blown air that has passed through the air cooling heat exchange section to the outside of the space to be air-conditioned. The auxiliary outside air introduction section (37) introduces outside air into the heating section.

The air cooling heat exchanger has an adsorption section (15a) that adsorbs moisture contained in the blown air. The inside/outside air ratio adjustment section is disposed upstream of the blown air flow of the heating passage (35a), the cold air bypass passage (35b), and the outside air bypass passage (35c). The heating passage is an air passage that passes through the air cooling heat exchanger and causes the blown air that has passed through the air cooling heat exchanger to pass through the heating section. The cold air bypass passage is an air passage that passes through the air cooling heat exchanger and causes the blown air that has passed through the air cooling heat exchanger to bypass the heating section. The outside air bypass passage is an air passage that passes through the blown air that has flowed in from the inside/outside air ratio adjustment section and causes the blown air to bypass the air cooling heat exchanger. The exhaust section is configured to be able to exhaust the entire amount of blown air that has flowed through the cold air bypass passage to the outside of the space to be air-conditioned.

The refrigerant circuit switching unit switches to a refrigerant circuit that circulates the refrigerant discharged from the compressor through the heating unit, the first pressure reduction unit, the air-cooling heat exchange unit, the outdoor heat exchange unit, and the suction side of the compressor in this order during a dehumidification heating mode in which the conditioned space is dehumidified and heated. Also, the refrigerant circuit switching unit switches to a refrigerant circuit that circulates the refrigerant discharged from the compressor through the heating unit, the outdoor heat exchange unit, the second pressure reduction unit, the air-cooling heat exchange unit, and the suction side of the compressor in this order during a defrosting mode in which frost on the outdoor heat exchange unit is removed.
In the adsorption process in which moisture is adsorbed into the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes inside air to flow into the air-cooling heat exchange section. In the desorption process in which moisture is desorbed from the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes outside air to flow into the air-cooling heat exchange section. In the desorption process, the exhaust section exhausts the entire volume of the blown air that has passed through the air-cooling heat exchange section to outside the air-conditioned space via the cold air bypass passage without flowing into the air-conditioned space. In the desorption process, the auxiliary outside air introduction section introduces outside air into the heating section via the outside air bypass passage , and the blown air heated by the heating section is blown into the air-conditioned space.

Accordingly, when the refrigerant circuit switching unit (13) switches to the refrigerant circuit in the dehumidification heating mode, a vapor compression refrigeration cycle can be configured in which 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) function as evaporators.

The blown air that has been cooled and dehumidified in the air cooling heat exchange section (15) is then reheated in the heating section (12, 12a, 40) and blown out into the space to be air-conditioned, thereby dehumidifying and heating the space to be air-conditioned.

Furthermore, the air cooling heat exchange section (15) has an adsorption section (15a). Therefore, in the dehumidification heating mode, the adsorption action of the adsorption section (15a) can be used to dehumidify the blown air. As a result, the power consumption of the compressor (11) can be reduced, and the operating efficiency of the air conditioning system as a whole can be improved.

In addition, when the refrigerant circuit switching unit (13) switches to the defrost mode refrigerant circuit, the heating unit (12, 12a, 40) and the outdoor heat exchange unit (16) can function as a condenser, and the air cooling heat exchange unit (15) can function as an evaporator. Therefore, the frost on the outdoor heat exchange unit (16) can be melted and removed.

Furthermore, in the defrost mode, the high-temperature refrigerant discharged from the compressor (11) is caused to flow into the heating section (12, 12a, 40). Therefore, even if the blown air is cooled in the air-cooling heat exchange section (15) during the defrost mode, it can be reheated in the heating section (12, 12a, 40). As a result, even if the rotation speed of the compressor (11) is determined so that the refrigeration oil can be appropriately returned to the compressor (11), a decrease in the temperature of the space to be air-conditioned can be suppressed.

That is, according to the air conditioner described in claim 1, the refrigeration oil can be appropriately returned to the compressor (11) while obtaining the effect of improving the operating efficiency by providing an air-cooling heat exchange section (15) having an adsorption section (15a).

The air conditioning system according to claim 2 is an air conditioning system applied to a vehicle, and includes a compressor (11), a heating section (12, 12a, 40), a branching section (17a), an outdoor pressure reduction section (14c), an outdoor heat exchange section (16), a cooling pressure reduction section (14d, 14e), a cooling heat exchange section (15, 19, 50), a junction section (17g), and a refrigerant circuit switching section (13a...13d).

The compressor compresses and discharges a refrigerant mixed with refrigeration oil. The heating unit heats the air to be blown to the space to be air-conditioned using the refrigerant discharged from the compressor as a heat source. The branching unit branches the flow of the refrigerant flowing out from the heating unit. The outdoor pressure reduction unit and the cooling pressure reduction unit reduce the pressure of the refrigerant. The outdoor heat exchange unit exchanges heat between the refrigerant reduced in pressure by the outdoor pressure reduction unit and outside air. The cooling heat exchange unit evaporates the refrigerant reduced in pressure by the cooling pressure reduction unit in order to cool the object to be cooled . The confluence unit merges the flow of the refrigerant flowing out from the cooling heat exchange unit and the flow of the refrigerant flowing out from the outdoor heat exchange unit, and causes the refrigerant to flow 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 section has an air-cooling heat exchange section (15) for cooling the blown air before it is heated by the heating section. The air-cooling heat exchange section has an adsorption section (15a) for adsorbing moisture contained in the blown air. The cooling pressure reduction section has an air-cooling pressure reduction section (14d) for reducing the pressure of the refrigerant flowing into the air-cooling heat exchange section.
The air conditioner according to claim 2 further comprises an inside/outside air ratio adjusting section (33), an exhaust section (38), and an auxiliary outside air introduction section (37). The inside/outside air ratio adjusting section (33) adjusts the ratio of outside air and inside air in the blown air flowing into the air-cooling heat exchange section. The exhaust section (38) exhausts the blown air that has passed through the air-cooling heat exchange section to the outside of the space to be air-conditioned. The auxiliary outside air introduction section (37) introduces outside air into the heating section. The inside/outside air ratio adjusting section is disposed upstream of the blown air flow of the heating passage (35a), the cold air bypass passage (35b), and the outside air bypass passage (35c). The heating passage is an air passage that causes the blown air that has passed through the air-cooling heat exchange section to pass through the heating section. The cold air bypass passage is an air passage that causes the blown air that has passed through the air-cooling heat exchange section to bypass the heating section. The outside air bypass passage is an air passage through which the blown air flowing in from the inside/outside air ratio adjusting section is caused to bypass the air-cooling heat exchange section. The exhaust section is configured to exhaust the entire amount of blown air that has flowed through the cold air bypass passage to the outside of the space to be air-conditioned.

The refrigerant circuit switching unit circulates the refrigerant discharged from the compressor in the order of heating unit, branch unit, air cooling pressure reduction unit, air cooling heat exchange unit, junction unit, and suction side of the compressor during a dehumidification heating mode in which the conditioned space is dehumidified and heated. At the same time, the refrigerant circuit switching unit switches to a refrigerant circuit that circulates the refrigerant discharged from the compressor in the order of heating unit, branch unit, outdoor pressure reduction unit, outdoor heat exchange unit, junction unit, and suction side of the compressor. In addition, the refrigerant circuit switching unit switches to a refrigerant circuit that circulates the refrigerant discharged from the compressor in the order of heating unit, outdoor heat exchange unit, cooling pressure reduction unit, cooling heat exchange unit, and suction side of the compressor during a defrosting mode in which frost on the outdoor heat exchange unit is removed.
In the adsorption process in which moisture is adsorbed into the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes inside air to flow into the air-cooling heat exchange section. In the desorption process in which moisture is desorbed from the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes outside air to flow into the air-cooling heat exchange section. In the desorption process, the exhaust section exhausts the entire volume of the blown air that has passed through the air-cooling heat exchange section to outside the air-conditioned space via the cold air bypass passage without flowing into the air-conditioned space. In the desorption process, the auxiliary outside air introduction section introduces outside air into the heating section via the outside air bypass passage , and the blown air heated by the heating section is blown into the air-conditioned space.

As a result, when the refrigerant circuit switching unit (13a...13d) switches to the refrigerant circuit in the dehumidification heating mode, a vapor compression refrigeration cycle can be configured in which 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) function as evaporators.

The blown air that has been cooled and dehumidified in the air cooling heat exchange section (15) is then reheated in the heating section (12, 12a, 40) and blown out into the space to be air-conditioned, thereby dehumidifying and heating the space to be air-conditioned.

Furthermore, the air cooling heat exchange section (15) has an adsorption section (15a). Therefore, in the dehumidification heating mode, the adsorption action of the adsorption section (15a) can be used to dehumidify the blown air. As a result, the power consumption of the compressor (11) can be reduced, and the operating efficiency of the air conditioning system as a whole can be improved.

In addition, when the refrigerant circuit switching unit (13a...13d) switches to the defrost mode refrigerant circuit, the heating unit (12, 12a, 40) and the outdoor heat exchange unit (16) can function as a condenser, and 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.

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

That is, according to the air conditioner described in claim 2, the refrigeration oil can be appropriately returned to the compressor (11) while obtaining the effect of improving the operating efficiency by providing an air-cooling heat exchange section (15) having an adsorption section (15a).

The air conditioner according to claim 4 is an air conditioner applied to a vehicle, and includes a compressor (11), a heating section (12a, 40a), a branching section (17d), an air cooling pressure reduction section (14d), an air cooling heat exchange section (15), a low-temperature side heat medium circuit (50a), a heat medium cooling pressure reduction section (14e), a heat medium cooling heat exchange section (19), a pressure adjustment section (20), a junction section (17g), a low-temperature side outside air heat exchange section (54), a heat quantity distribution section (43), an inside/outside air ratio adjustment section (33), an exhaust section (38), and an auxiliary outside air introduction section (37).

The compressor compresses and discharges a refrigerant mixed with refrigeration oil. The heating unit heats the blown air to be blown to the space to be air-conditioned using the refrigerant discharged from the compressor as a heat source. The branching unit branches the flow of the refrigerant flowing out from the heating unit. The air cooling decompression unit decompresses one of the refrigerants branched at the branching unit. The air cooling heat exchange unit evaporates the refrigerant decompressed at the air cooling decompression unit to cool the blown air before it is heated at the heating unit. The low-temperature side heat medium circuit circulates the low-temperature side heat medium. The heat medium cooling decompression unit decompresses the other of the refrigerant branched at the branching unit. The heat medium cooling heat exchange unit exchanges heat between the refrigerant decompressed at the heat medium cooling decompression unit and the low-temperature side heat medium. The pressure adjustment 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 confluence unit merges the flow of refrigerant flowing out from the air-cooling heat exchange unit and the flow of refrigerant flowing out from the heat medium cooling heat exchange unit, and causes the refrigerant to flow out to the suction side of the compressor. The low-temperature side outside air heat exchange unit is disposed in the low-temperature side heat medium circuit and exchanges heat between the low-temperature side heat medium and outside air. The heat quantity distribution unit distributes the heat contained in the refrigerant discharged from the compressor between 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. The inside/outside air ratio adjustment unit adjusts the ratio of outside air to inside air in the blown air flowing into the air-cooling heat exchange unit. The exhaust unit exhausts the blown air that has passed through the air-cooling heat exchange unit to outside the space to be air-conditioned. The auxiliary outside air introduction unit introduces outside air to the heating unit.

The air cooling heat exchanger has an adsorption section (15a) that adsorbs moisture contained in the blown air. The inside/outside air ratio adjustment section is disposed upstream of the blown air flow of the heating passage (35a), the cold air bypass passage (35b), and the outside air bypass passage (35c). The heating passage is an air passage that passes through the air cooling heat exchanger and causes the blown air that has passed through the air cooling heat exchanger to pass through the heating section. The cold air bypass passage is an air passage that passes through the air cooling heat exchanger and causes the blown air that has passed through the air cooling heat exchanger to bypass the heating section. The outside air bypass passage is an air passage that passes through the blown air that has flowed in from the inside/outside air ratio adjustment section and causes the blown air to bypass the air cooling heat exchanger. The exhaust section is configured to be able to exhaust the entire amount of blown air that has flowed through the cold air bypass passage to the outside of the space to be air-conditioned.

The heat distribution unit supplies heat contained in the refrigerant discharged from the compressor to the heating unit in a dehumidification heating mode for dehumidifying and heating the air-conditioned space. Also, in a defrost mode for removing frost on the low-temperature side outdoor air heat exchange unit, the heat distribution unit increases the amount of heat supplied to the low-temperature side outdoor air heat exchange unit compared to the dehumidification heating mode.
In the adsorption process in which moisture is adsorbed into the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes inside air to flow into the air-cooling heat exchange section. In the desorption process in which moisture is desorbed from the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes outside air to flow into the air-cooling heat exchange section. In the desorption process, the exhaust section exhausts the entire volume of the blown air that has passed through the air-cooling heat exchange section to outside the air-conditioned space via the cold air bypass passage without flowing into the air-conditioned space. In the desorption process, the auxiliary outside air introduction section introduces outside air into the heating section via the outside air bypass passage , and the blown air heated by the heating section is blown into the air-conditioned space.

Accordingly, in the dehumidifying and heating mode, the heat distribution section (43) supplies the heat contained in the refrigerant discharged from the compressor to the heating section. Therefore, in the dehumidifying and heating mode, the blown air that has been cooled and dehumidified in the air cooling heat exchange section (15) is reheated in the heating section (12a, 40a) and blown out into the space to be air-conditioned, thereby performing dehumidifying and heating of the space to be air-conditioned.

Furthermore, the air cooling heat exchange section (15) has an adsorption section (15a). Therefore, in the dehumidification heating mode, the adsorption action of the adsorption section (15a) can be used to dehumidify the blown air. As a result, the power consumption of the compressor (11) can be reduced, and the operating efficiency of the air conditioning system as a whole can be improved.

In addition, in the defrost mode, the heat distribution section (43) increases the amount of heat supplied to the low-temperature side outdoor air heat exchange section (54) more than in the dehumidification heating mode. Therefore, the frost on the low-temperature side outdoor air heat exchange section (54) can be melted and removed.

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

That is, according to the air conditioner described in claim 4, the refrigeration oil can be appropriately returned to the compressor (11) while obtaining the effect of improving the operating efficiency by providing an air-cooling heat exchange section (15) having an adsorption section (15a).

The reference symbols in parentheses for each means described in this section and in the claims are examples showing the correspondence with the specific means described in the embodiments described below.

1 is an overall configuration diagram of a vehicle air conditioning device according to a first embodiment; 2 is a block diagram showing an electric control unit of the vehicle air conditioner according to the first embodiment; FIG. FIG. 4 is a Mollier diagram showing a change in state of a refrigerant during an adsorption process in a dehumidification heating mode in the refrigeration cycle device of the first embodiment. FIG. 4 is a Mollier diagram showing a change in state of a refrigerant during a desorption process in a dehumidification heating mode in the refrigeration cycle device of the first embodiment. FIG. 4 is a Mollier diagram showing a change in state of a refrigerant in a defrost mode in the refrigeration cycle device of the first embodiment. FIG. 11 is an overall configuration diagram showing the flow of refrigerant in a cooling mode and a defrosting mode of a vehicle air conditioner according to a second embodiment; FIG. 11 is an overall configuration diagram showing a refrigerant flow in a dehumidifying and heating mode of a vehicle air conditioner according to a second embodiment. FIG. 11 is a block diagram showing an electric control unit of a vehicle air conditioner according to a second embodiment. FIG. 11 is a Mollier diagram showing a change in state of a refrigerant during an adsorption process in a single dehumidification and heating mode in the refrigeration cycle device of the second embodiment. FIG. 11 is a Mollier diagram showing a change in state of a refrigerant during a desorption process in a dehumidification heating mode in a refrigeration cycle device of a second embodiment. FIG. 11 is a Mollier diagram showing a change in state of a refrigerant in a single defrost mode in the refrigeration cycle device of the second embodiment. FIG. 11 is an overall configuration diagram showing the flow of refrigerant in a cooling mode and a defrosting mode of a vehicle air conditioner according to a third embodiment. FIG. 11 is an overall configuration diagram showing a refrigerant flow in a dehumidifying and heating mode of a vehicle air conditioner according to a third embodiment. FIG. 13 is an overall configuration diagram showing the flows of refrigerant and heat medium in a single cooling mode and a single defrosting mode of a vehicle air conditioner according to a fourth embodiment. FIG. 13 is an overall configuration diagram showing the flows of refrigerant and heat medium in a cooling/air-cooling mode and a waste heat defrosting mode of a vehicle air conditioner according to a fourth embodiment. FIG. 13 is an overall configuration diagram showing the flows of the refrigerant and the heat medium during the adsorption process in a single dehumidification and heating mode of a vehicle air conditioner according to a fourth embodiment. FIG. 13 is an overall configuration diagram showing the flows of the refrigerant and the heat medium during a desorption process in a single dehumidification and heating mode of a vehicle air conditioner according to a fourth embodiment. FIG. 13 is an overall configuration diagram showing the flows of the refrigerant and the heat medium during the adsorption process in a cooling, dehumidifying and heating mode of a vehicle air conditioner according to a fourth embodiment. FIG. 13 is an overall configuration diagram showing the flows of the refrigerant and the heat medium during a desorption process in a cooling, dehumidifying, heating mode of a vehicle air conditioner according to a fourth embodiment. FIG. 13 is a block diagram showing an electric control unit of a vehicle air conditioner according to a fourth embodiment. FIG. 13 is a Mollier diagram showing a change in the state of a refrigerant during an adsorption process in a single dehumidification and heating mode in a refrigeration cycle device of a fourth embodiment. FIG. 13 is a Mollier diagram showing a change in state of a refrigerant during a desorption process in a dehumidification heating mode in a refrigeration cycle device of a fourth embodiment. FIG. 13 is a Mollier diagram showing a change in state of a refrigerant in a single defrost mode in the refrigeration cycle device of the fourth embodiment.

Below, several embodiments for carrying out the present invention will be described with reference to the drawings. In each embodiment, parts corresponding to matters described in the preceding embodiment will be given the same reference numerals, and duplicated explanations may be omitted. In cases where only a portion of the configuration is described in each embodiment, other previously described embodiments may be applied to the other portions of the configuration. In addition to combinations of parts that are specifically specified as being possible in each embodiment, it is also possible to partially combine embodiments even if not specified, as long as there is no particular problem with the combination.

First Embodiment
A first embodiment of an air conditioner according to the present invention will be described below with reference to the drawings. In this embodiment, the air conditioner according to the present invention is applied to a 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 conditioner 1 conditions the interior of the vehicle cabin, which is the space to be air-conditioned, in the electric vehicle.

As shown in the overall configuration diagram of Figure 1, the vehicle air conditioner 1 has a refrigeration cycle device 10 and an interior air conditioning unit 30.

First, the refrigeration cycle device 10 will be described. The refrigeration cycle device 10 adjusts the temperature of the air blown into the vehicle cabin in the vehicle air conditioner 1. The refrigeration cycle device 10 is configured to be able to switch the refrigerant circuit that circulates the refrigerant depending on the operating mode.

The refrigeration cycle device 10 uses an HFO refrigerant (specifically, R1234yf) as the refrigerant. The refrigeration cycle device 10 forms 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. The refrigerant is mixed with refrigeration oil to lubricate the compressor 11. The refrigeration oil is PAG oil (polyalkylene glycol oil) that is compatible with liquid-phase refrigerants. A portion of the refrigeration oil circulates through the cycle together with the refrigerant.

The compressor 11 in the refrigeration cycle device 10 draws in, compresses, and discharges the refrigerant. The compressor 11 is disposed in a drive unit room at the front of the vehicle cabin. The drive unit room is an exterior space in which at least a portion of the drive unit (e.g., an electric motor) for outputting the driving force for traveling is disposed.

The compressor 11 is an electric compressor that uses an electric motor to rotate a fixed-capacity compression mechanism with a fixed discharge capacity. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 60, which will be described later.

The discharge port of the compressor 11 is connected to the refrigerant inlet side of the indoor condenser 12. The indoor condenser 12 is disposed within 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, condensing the high-pressure refrigerant and heating the blown air. Therefore, the indoor condenser 12 is a heating section that heats the blown air using the high-pressure refrigerant discharged from the compressor 11 as a heat source.

The refrigerant outlet of the indoor condenser 12 is connected to one of the inlet and outlet sides of the four-way valve 13. 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 can be switched to a refrigerant circuit that connects the refrigerant outlet side of the indoor condenser 12 to one of the inlet/outlet sides of the first expansion valve 14a, and at the same time connects one of the refrigerant inlet/outlet sides of the outdoor heat exchanger 16, which will be described later, to the suction side of the compressor 11. Furthermore, the four-way valve 13 can be switched to a refrigerant circuit that connects one of the inlet/outlet sides of the first expansion valve 14a to the suction side of the compressor 11, and at the same time connects the refrigerant outlet side of the indoor condenser 12 to one of the refrigerant inlet/outlet sides of the outdoor heat exchanger 16, which will be described later.

One of the inlet/outlet sides of the first expansion valve 14a is connected to another inlet/outlet of the four-way valve 13. The first expansion valve 14a is a first pressure reducing section that reduces the pressure of the refrigerant. The first expansion valve 14a is a first refrigerant flow rate adjusting section that adjusts the flow rate of the refrigerant flowing downstream.

The first expansion valve 14a is an electric variable throttle mechanism having a valve body that changes the throttle opening 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. Furthermore, the first expansion valve 14a has a full-open function that functions simply as a refrigerant passage by fully opening the valve, with almost no refrigerant pressure reduction or flow rate adjustment action.

The other inlet/outlet of the first expansion valve 14a is connected to one of the refrigerant inlet/outlet sides of the indoor evaporator 15. The indoor evaporator 15 is located inside the casing 31 of the indoor air conditioning unit 30, upstream of the indoor condenser 12 in the blown air flow.

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 exchanger that cools the object to be cooled by evaporating the low-pressure refrigerant and exerting a heat absorption effect. The indoor evaporator 15 is an air cooling heat exchanger that cools the blown air before it flows into the indoor condenser 12 as the object to be cooled.

Furthermore, in this embodiment, a so-called tank-and-tube type heat exchanger is used as the indoor evaporator 15. The tank-and-tube type heat exchanger has multiple refrigerant tubes and a pair of refrigerant tanks.

The refrigerant tubes are metal tubes through which the refrigerant flows. A number of the refrigerant tubes are stacked and arranged at intervals in a specific direction. An air passage is formed between adjacent tubes to allow the flow of blown air. Heat exchange fins are arranged in the air passage to promote heat exchange between the refrigerant and the blown air. The heat exchange fins are corrugated fins formed by bending a thin metal plate into a corrugated shape.

The refrigerant tank is a bottomed cylindrical metal member that extends in the stacking direction of the multiple refrigerant tubes. The pair of refrigerant tanks are connected to both ends of the refrigerant tubes. Inside the refrigerant tank, a distribution space that distributes the refrigerant to the multiple refrigerant tubes and a collection space that collects the refrigerant flowing out from the multiple refrigerant tubes are formed. Therefore, in a tank-and-tube type heat exchanger, a heat exchange core part that exchanges heat between the refrigerant and the blown air is formed mainly by the refrigerant tubes and heat exchange fins.

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

The other refrigerant inlet/outlet of the indoor evaporator 15 is connected to one of the inlet/outlet sides of the second expansion valve 14b. The second expansion valve 14b is a second pressure reduction section that reduces the pressure of the refrigerant. The second expansion valve 14b is a second refrigerant flow rate adjustment section that adjusts the flow rate of the refrigerant that flows out downstream. 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 exterior heat exchanger 16 is connected to the other refrigerant inlet/outlet side of the second expansion valve 14b. The exterior heat exchanger 16 is an exterior heat exchange section that exchanges heat between the refrigerant flowing inside and the exterior air blown by an exterior air fan (not shown). The exterior heat exchanger 16 is disposed at the front side of the drive unit compartment. Therefore, when the vehicle is traveling, the traveling wind can be applied to the exterior heat exchanger 16 as the exterior air.

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

Next, the interior air conditioning unit 30 will be described. The interior air conditioning unit 30 is a unit in the vehicle air conditioner 1 that blows out air adjusted to an appropriate temperature toward an appropriate location in the vehicle cabin. The interior air conditioning unit 30 is located inside the instrument panel (i.e., the instrument panel) located at the very front of the vehicle cabin.

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

An inside/outside air switching device 33 is disposed on the most upstream side of the blown air flow in the casing 31. The inside/outside air switching device 33 adjusts the ratio of inside air (i.e., air inside the vehicle cabin) and outside air (i.e., air outside the vehicle cabin) introduced into the casing 31. Thus, the inside/outside air switching device 33 is an inside/outside air ratio adjustment unit that adjusts the ratio of inside air and outside air in the blown air flowing into the interior 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, etc. The electric actuator for the inside/outside air door displaces the inside/outside air door 33a. As a result, the inside/outside air door 33a adjusts the area ratio between the opening area of the inside air inlet that introduces inside air into the air passage in the casing 31 and the opening area of the outside air inlet that introduces outside air into the air passage. The operation of the electric actuator for the inside/outside air door is controlled by a control signal output from the control device 60.

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

The downstream side of the airflow from the indoor blower 32 is divided into multiple air passages. Furthermore, in the air passage downstream of the airflow from the indoor blower 32, the indoor evaporator 15 and the indoor condenser 12 are arranged in this order with respect to the airflow. In other words, the indoor evaporator 15 is arranged upstream of the airflow from the indoor condenser 12.

More specifically, the air passage downstream of the indoor evaporator 15 is divided into a heating passage 35a and a cold air bypass passage 35b. The indoor condenser 12 is disposed in the heating passage 35a. The heating passage 35a is a passage that allows the blown air that has passed through the indoor evaporator 15 to pass further through the indoor condenser 12 and flow downstream. The cold air bypass passage 35b is a passage that allows the blown air that has passed through the indoor evaporator 15 to bypass the indoor condenser 12 and flow downstream.

In addition, an outside air bypass passage 35c is formed downstream of the air flow from the indoor blower 32, allowing the air to bypass the indoor evaporator 15. The most downstream part of the air flow of the outside air bypass passage 35c is connected to the auxiliary outside air inlet 31a, which will be described later.

An air mix door 34 is disposed in the air passage downstream of the indoor evaporator 15 and upstream of the heating passage 35a and the cold air bypass passage 35b. The air mix door 34 adjusts the ratio of the volume of air that flows into the heating passage 35a and the cold air bypass passage 35b after passing 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 entrance of the heating passage 35a and the opening area of the entrance 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.

When the air mix door 34 changes the opening area of the entrance to 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 exchanged between the refrigerant and the blown air in the indoor condenser 12 also changes. Therefore, the air mix door 34 is a heat amount adjustment unit that adjusts the amount of heating of the blown air in the indoor condenser 12.

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

Furthermore, at the most downstream part of the blown air flow of the casing 31, multiple opening holes (not shown) are formed for blowing the blown air (conditioned air) mixed in the mixing space 36 into the vehicle cabin.

Therefore, the air mix door 34 can adjust the ratio of the air volume passing through the heating passage 35a to the air volume passing through the cold air bypass passage 35b, thereby adjusting the temperature of the blown air mixed in the mixing space 36. In other words, by displacing the air mix door 34, the temperature of the blown air blown into the vehicle cabin from each opening can be adjusted.

Specifically, the openings include a face opening, a foot opening, and a defroster opening (none of which are shown). The face opening is an opening for blowing conditioned air toward the upper bodies of occupants in the vehicle cabin. The foot opening is an opening for blowing conditioned air toward the feet of occupants. The defroster opening is an opening for blowing conditioned air toward the inside surface of the vehicle front windshield.

A blowing mode switching door (not shown) is located upstream of these openings. The blowing mode switching door switches the opening from which the conditioned air is blown out by opening and closing each opening. The operation of the electric actuator for driving the blowing mode switching door is controlled by a control signal output from the control device 60.

In addition, an auxiliary outside air introduction device 37 is disposed in the portion of the casing 31 that forms the heating passage 35a. The auxiliary outside air introduction device 37 is an auxiliary outside air introduction section that introduces outside air from the downstream side of the air mix door 34 into the indoor condenser 12 during the desorption process described below.

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 in 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 a 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 to open the auxiliary outside air introduction port 31a, the blown air that has flowed into the outside air bypass passage 35c is introduced into the indoor condenser 12 via the auxiliary outside air introduction port 31a.

In addition, an exhaust device 38 is disposed at the most downstream side of the cold air bypass passage 35b of the casing 31. The exhaust device 38 is an exhaust section that exhausts the blown air that has flowed through the cold air bypass passage 35b to the outside of the vehicle cabin during the desorption process in the dehumidification heating mode described below.

The exhaust device 38 has an exhaust door 38a that opens and closes the 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 a control signal output from the control device 60.

When the electric actuator for the exhaust door displaces the exhaust door 38a to fully open the exhaust port 31b, not only does the exhaust port 31b open, but the communication between the cold air bypass passage 35b and the mixing space 36 is closed. As a result, the entire volume of blown air that has flowed through the cold air bypass passage 35b is exhausted to the outside of the vehicle compartment through the exhaust port 31b.

When the electric actuator for the exhaust door displaces the exhaust door 38a 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 entire volume of blown air that has flowed through the cold air bypass passage 35b flows into the mixing space 36 without being exhausted to the outside.

Next, an overview of the electrical control unit of the vehicle air conditioner 1 will be described with reference to FIG. 2. The control device 60 is composed of a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuits. The control device 60 performs various calculations and processes based on an air conditioning control program stored in the ROM, and controls the operation of various controlled devices 11, 13, 14a, 14b, 32, 33, 34a, 37, 38, etc. connected to the output side.

As shown in FIG. 2, various control sensors are connected to the input side of the control device 60. The control sensors include an inside air temperature sensor 61a, an outside air temperature sensor 61b, and a solar radiation sensor 61c. Further control sensors include a high 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 interior air temperature sensor 61a is an interior air temperature detection unit that detects the interior air temperature Tr, which is the temperature inside the vehicle cabin. The exterior air temperature sensor 61b is an exterior air temperature detection unit that detects the exterior air temperature Tam, which is the temperature outside the vehicle cabin. The solar radiation sensor 61c is an exterior air radiation detection unit that detects the amount of solar radiation As irradiated into the vehicle cabin. The detection values of these detection units are used when calculating the target air outlet 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 detection unit that detects the temperature TAV of the air blown out from the mixing space 36 into the vehicle cabin.

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. Specifically, the evaporator temperature sensor 61f detects the temperature of the heat exchange fins of the indoor evaporator 15.

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

The outdoor unit temperature sensor 61h is an outdoor unit temperature detection 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. In this embodiment, the outdoor unit temperature sensor 61h specifically detects the temperature of the other refrigerant inlet/outlet side of the outdoor heat exchanger 16 (the refrigerant inlet/outlet side to which the second expansion valve 14b is connected).

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

Furthermore, an operation panel 62 located near the instrument panel at the front of the vehicle interior is connected to the input side of the control device 60, and operation signals are input from various operation switches provided on this operation panel 62.

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, etc.

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

The control device 60 of this embodiment is also configured as an integrated control unit that controls the various control target devices connected to the output side. In other words, in the control device 60, the configuration (i.e., hardware and software) that controls the operation of each control target device becomes the control unit that controls the operation of each control target device.

For example, in the control device 60, the component that controls the operation of the four-way valve 13, which is the refrigerant circuit switching unit, is the refrigerant circuit control unit 60a. The component that controls the operation of the inside/outside air switching device 33, which is the inside/outside air ratio adjustment unit, is the inside/outside air switching control unit 60b. The component 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. The vehicle air conditioner 1 switches between various operating modes to condition the vehicle interior. The operating modes are switched by executing an air conditioning control program that is pre-stored in the control device 60. The air conditioning control program is executed when the auto switch on the operation panel 62 is turned on.

The air conditioning control program calculates the target outlet temperature TAO of the air blown into the vehicle cabin based on the detection signals of the control sensors and the operation signals of the operation panel 62. Furthermore, the air conditioning control program switches the operation mode based on the target outlet temperature TAO, the detection signals of the control sensors, and the operation signals of the operation panel 62. The operation of each operation mode is described in detail below.

(a) Cooling Mode The cooling mode is an operation mode in which cooled ventilation air is blown into the passenger compartment to cool the passenger compartment.

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 outside air temperature KTam and the target air outlet temperature TAO is equal to or lower than the cooling reference temperature KTao.

The reference outside air temperature KTam is generally set to a value at which it is determined that 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 reference outside air temperature KTam. The cooling reference temperature KTao is generally set to a temperature at which it is determined that cooling of the vehicle interior is necessary when the target air outlet temperature TAO is equal to or lower than the cooling reference temperature KTao.

In the cooling mode, the control device 60 opens the first expansion valve 14a fully and throttles the second expansion valve 14b to reduce the pressure of the refrigerant. The control device 60 also controls the operation of the four-way valve 13 to connect the refrigerant outlet side of the indoor condenser 12 to one of the refrigerant inlet/outlet sides of the outdoor heat exchanger 16, while simultaneously connecting one of the inlet/outlet sides of the first expansion valve 14a to the suction side of the compressor 11.

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

Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices. For example, with regard to the control signal to be output to the compressor 11, the control device 60 determines it so 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 air outlet temperature TAO and by referring to a control map for the cooling mode that is stored in advance in the control device 60. In the control map for the cooling mode, the target evaporator temperature TEO is determined to a temperature (specifically, 1°C or higher) that can suppress frost formation on the indoor evaporator 15.

In addition, the control device 60 determines the control signal to be output to the inside/outside air switching device 33 so that the inside air inlet is fully closed and the outside air inlet is fully open. Note that, even in the cooling mode, if high cooling performance is desired, the control signal to be output to the inside/outside air switching device 33 may be determined so that the inside air inlet is fully open and the outside air inlet is fully closed.

The control device 60 determines the control voltage to be output to the indoor blower 32 based on the target blowing temperature TAO. The control device 60 determines the control signal to be output to the electric actuator 34a for the air mix door so that the blowing air temperature TAV detected by the air conditioning air temperature sensor 61e approaches the target blowing temperature TAO.

In addition, for 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. In addition, for the control signal output to the exhaust device 38, the control device 60 determines to close the exhaust port 31b.

The control device 60 then outputs the control signals determined as described above to the various devices to be controlled.

In the air conditioning control program, control routines such as reading the detection signal and operation signal, calculating the target air outlet temperature TAO, determining the operation mode, determining the control signals to be output to various controlled devices according to the operation mode, and outputting the determined control signals are repeated at each predetermined control period until a request is made to stop the air conditioning in the vehicle cabin. This repetition of control routines is also performed in other operation modes.

Therefore, in the refrigeration cycle device 10 in cooling mode, the indoor condenser 12 and the outdoor heat exchanger 16 function as condensers that condense the refrigerant by dissipating heat, and the indoor evaporator 15 functions as an evaporator that evaporates the refrigerant, forming a vapor compression refrigeration cycle.

In the cooling mode of the refrigeration cycle device 10, the refrigerant dissipates heat to the blown air in the indoor condenser 12, thereby heating the blown air. In the indoor evaporator 15, the refrigerant evaporates and exerts a heat absorption effect, thereby cooling the blown air.

In addition, in the indoor air conditioning unit 30 in cooling mode, 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 depending on the opening degree of the air mix door 34.

The blown air that flows into the heating passage 35a is heated as it passes 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, outside air does not flow into the heating passage 35a through the auxiliary outside air introduction port 31a.

The blown air that flows 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 entire volume of blown air that has flowed through the cold air bypass passage 35b flows into the mixing space 36.

In the mixing space 36, the blown air (hot 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 to become blown air (conditioned air) at an appropriate temperature. The blown air mixed in the mixing space 36 and temperature-adjusted is blown out through the opening hole to an appropriate location in the vehicle cabin. This achieves cooling of the vehicle cabin.

The indoor evaporator 15 is coated with a desiccant material 15a, which acts as an adsorption section. Therefore, when the air passes through the indoor evaporator 15, the moisture contained in the air is adsorbed by the desiccant material 15a until the adsorption amount of the desiccant material 15a reaches a saturation amount.

However, in the cooling mode, the outside air temperature Tam is equal to or higher than the reference outside air temperature KTam, so the vehicle window glass is less likely to fog up. For this reason, in the cooling mode, even if the adsorption amount of the desiccant material 15a reaches saturation, the desorption process, which desorbs moisture from the desiccant material 15a and regenerates it, is not performed. Therefore, in the cooling mode, the vehicle interior can be continuously cooled.

(b) Dehumidifying and heating mode The dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blown air is reheated and blown into the passenger compartment to dehumidify and heat the passenger compartment. The dehumidifying and heating mode is executed when the outside air temperature Tam is lower than the reference outside air temperature KTam or when the target blowing temperature TAO is higher than the cooling reference temperature KTao.

In the vehicle air conditioner 1, when performing dehumidification and heating of the vehicle interior, the adsorption action of the desiccant material 15a is used to dehumidify the blown air. For this reason, in the dehumidification and heating mode, it is necessary to desorb moisture from the desiccant material 15a and regenerate it before the adsorption amount of the desiccant material 15a reaches its saturation amount.

Therefore, in the dehumidifying heating mode, the system switches between an adsorption process in which moisture is adsorbed onto the desiccant material 15a to dehumidify the blown air, and a desorption process in which moisture is desorbed from the desiccant material 15a to regenerate the desiccant material 15a, at a predetermined interval.

First, in the adsorption process of the dehumidification heating mode, the control device 60 throttles the first expansion valve 14a and throttles or fully opens the second expansion valve 14b. The control device 60 also controls the operation of the four-way valve 13 to connect the refrigerant outlet side of the indoor condenser 12 to one of the inlet/outlet sides of the first expansion valve 14a, while simultaneously connecting one of the refrigerant inlet/outlet sides of the outdoor heat exchanger 16 to the suction side of the compressor 11.

Therefore, in the refrigeration cycle device 10 during the adsorption process, as shown by the black arrows in Figure 1, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: indoor condenser 12, four-way valve 13, first expansion valve 14a, indoor evaporator 15, second expansion valve 14b, outdoor heat exchanger 16, four-way valve 13, and the suction port of the compressor 11.

Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices. For example, with regard to the control signal to be output to the compressor 11, the control device 60 determines it so 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 blowing temperature TAO, with reference to a control map for the dehumidification heating mode that is pre-stored in the control device 60.

In addition, the control device 60 determines the control signal output to the inside/outside air switching device 33 to fully open the inside air inlet and fully close the outside air inlet. In other words, during the adsorption process, the inside/outside air switching device 33 increases the proportion of inside air in the blown air flowing into the indoor evaporator 15 more than the proportion of outside air.

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

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

The refrigerant that flows into the indoor evaporator 15 evaporates through heat exchange with the blown air (point c3 to point d3 in Figure 3). The refrigerant that flows out of the indoor evaporator 15 flows into the outdoor heat exchanger 16 through the second expansion valve 14b, which is fully open. Note that Figure 3 shows an example in which the second expansion valve 14b is fully open. The refrigerant that flows into the outdoor heat exchanger 16 evaporates through heat exchange with the outside air (point d3 to point e3 in Figure 3).

The refrigerant flowing out of the outdoor heat exchanger 16 is sucked into the compressor 11 and compressed again (from point f3 to point a3 in Figure 3). Note that the difference in pressure between point e3 and point f3 in Figure 3 is the suction pressure loss of the compressor 11. The suction pressure loss is also shown in the Mollier diagram below.

In other words, in the refrigeration cycle device 10 in the adsorption process, the indoor condenser 12 functions as a condenser, and the indoor evaporator 15 and the outdoor heat exchanger 16 function as evaporators to configure a vapor compression refrigeration cycle. In the refrigeration cycle device 10 in the adsorption process, the blown air is heated in the indoor condenser 12. The blown air is cooled and dehumidified in the indoor evaporator 15.

In the adsorption process of the indoor air conditioning unit 30, as shown by the dashed arrows in the Mollier diagram of FIG. 3, the indoor air introduced into the casing 31 via the indoor/outdoor 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 and dehumidified as it passes through the indoor evaporator 15. Furthermore, in the adsorption process, the blown air passing through the indoor evaporator 15 is dehumidified by the adsorption action of the desiccant material 15a.

The blown air that has been cooled and dehumidified by the interior evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b depending on the opening degree of the air mix door 34. The blown air that flows into the heating passage 35a is heated by the interior condenser 12. The blown air that flows 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 through the opening hole to an appropriate location in the vehicle cabin. This achieves dehumidification and heating in the vehicle cabin.

Next, in the desorption process of the dehumidification heating mode, the control device 60 opens the first expansion valve 14a fully and throttles the second expansion valve 14b. The control device 60 also controls the operation of the four-way valve 13 to connect the refrigerant outlet side of the indoor condenser 12 to one of the inlet/outlet sides of the first expansion valve 14a, while simultaneously connecting one of the refrigerant inlet/outlet sides of the outdoor heat exchanger 16 to the suction side of the compressor 11.

Therefore, in the desorption process of the refrigeration cycle device 10, the refrigerant circulates in the refrigerant circuit in the same order as in the adsorption process, as shown by the black arrows in Figure 1.

Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices. For example, for the control signal to be output to the inside/outside air switching device 33, the control device 60 determines the control signal so that the inside air inlet is fully closed and the outside air inlet is fully open. In other words, during the desorption process, the inside/outside air switching device 33 increases the proportion of outside air in the blown air flowing into the indoor evaporator 15 compared to the proportion of inside air.

In addition, for 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. In addition, for the control signal output to the exhaust device 38, the control device 60 determines to fully open the exhaust port 31b.

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

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

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

In other words, in the desorption process of the refrigeration cycle device 10, the indoor condenser 12 and the indoor evaporator 15 function as condensers, and the outdoor heat exchanger 16 functions as an evaporator, forming a vapor compression refrigeration cycle. In the desorption process of the refrigeration cycle device 10, the blown air is heated by the indoor condenser 12.

In the indoor air conditioning unit 30 during the desorption process, the outside air introduced into the casing 31 via the inside/outside air switching device 33 is sucked into the indoor blower 32, as shown by the dashed arrows in the Mollier diagram of FIG. 4. The outside air blown from the indoor blower 32 is heated as it passes through the indoor evaporator 15, and is humidified by the moisture desorbed from the desiccant material 15a. This regenerates the desiccant material 15a.

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

The outside air that flows into the heating passage 35a from the auxiliary outside air inlet 31a is heated as it passes through the interior condenser 12 as blown air, as shown by the dashed arrows in the Mollier diagram of FIG. 4. The blown air heated by the interior condenser 12 flows into the mixing space 36. The blown air that flows into the mixing space 36 is blown out to an appropriate location in the vehicle cabin through the opening hole. This allows the vehicle cabin to continue to be heated even during the desorption process.

(c) Defrosting Mode The defrosting mode is an operation mode for removing frost formed on the outdoor heat exchanger 16. The defrosting mode is executed when a predetermined frosting condition is met while the dehumidifying heating mode is being executed.

In the air conditioning control program of this embodiment, the frost formation time Tmf during which the outdoor unit temperature Tout detected by the outdoor unit temperature sensor 61h is continuously below a predetermined reference frost temperature KToutf while the dehumidification heating mode is being executed is measured. Then, when the frost formation time Tmf becomes equal to or greater than the reference frost formation time KTmf, it is determined that the frost formation condition is met.

In the defrost mode, the control device 60 fully opens the first expansion valve 14a and throttles the second expansion valve 14b. The control device 60 also controls the operation of the four-way valve 13 to connect the refrigerant outlet side of the indoor condenser 12 to one of the refrigerant inlet/outlet sides of the outdoor heat exchanger 16, while simultaneously connecting one of the inlet/outlet sides of the first expansion valve 14a to the suction side of the compressor 11.

Therefore, in the defrost mode, the refrigeration cycle device 10 switches to a refrigerant circuit in which the refrigerant circulates in the same order as in the cooling mode, as shown by the white arrows in Figure 1.

Furthermore, the control device 60 appropriately determines the control signals to be output to the various controlled devices. For example, the control device 60 determines the control signal to be output to the compressor 11 so that the rotation speed is lower than in the dehumidification heating mode. The control signal to be output to the compressor 11 is determined within a range that allows the refrigeration oil mixed in the refrigerant to be returned to the compressor 11.

In addition, for the control signal output to the inside/outside air switching device 33, the control device 60 determines that the inside air inlet is fully open and the outside air inlet is fully closed. In addition, for the control signal output to the indoor blower 32, the control device 60 determines that the rotation speed is lower than in the dehumidification heating mode.

In addition, the control device 60 determines the control signal output to the electric actuator 34a for the air mix door to reduce the opening area of the inlet of the heating passage 35a by a predetermined amount compared to the dehumidification heating mode. As a result, in the defrost mode, the amount of heating of the blown air in the indoor condenser 12 is reduced compared to the dehumidification heating mode.

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

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

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

In other words, in the defrost mode, the refrigeration cycle device 10 configures a vapor compression refrigeration cycle in which the indoor condenser 12 and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 15 functions as an evaporator.

In the defrost mode of the refrigeration cycle device 10, the blown air is heated in the indoor condenser 12. The blown air is cooled and dehumidified in the indoor evaporator 15. Furthermore, in the outdoor heat exchanger 16, the heat of the refrigerant flowing out from the indoor condenser 12 melts and removes the frost on the outdoor heat exchanger 16. In other words, the outdoor heat exchanger 16 is defrosted.

In addition, in the indoor air conditioning unit 30 in the defrost mode, as shown by the dashed arrows in the Mollier diagram of FIG. 5, the indoor air introduced into the casing 31 via the indoor/outdoor 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 and dehumidified as it passes through the indoor evaporator 15. Furthermore, in the defrost mode, the blown air passing through the indoor evaporator 15 is dehumidified by the adsorption action of the desiccant material 15a as well.

The blown air that has been cooled and dehumidified by the interior evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b depending on the opening degree of the air mix door 34. The blown air that flows into the heating passage 35a is heated by the interior condenser 12. The blown air that flows into the heating passage 35a and the blown air that flows into the cold air bypass passage 35b flow into the mixing space 36 and are mixed, as in the cooling mode. The blown air mixed in the mixing space 36 is blown out to an appropriate location in the vehicle cabin through the opening hole.

In the defrost mode, the rotation speed of the compressor 11 is reduced more than in the dehumidifying and heating mode. Furthermore, the air mix door 34 is displaced so that the opening area of the entrance to the heating passage 35a is smaller than in the dehumidifying and heating mode. Therefore, although the amount of heat applied to the blown air in the interior condenser 12 is reduced more than in the dehumidifying and heating mode, the dehumidifying and heating of the vehicle interior can be continued.

The defrost mode ends when a predetermined end condition is met. When the defrost mode ends, the dehumidifying heating mode is started. In the air conditioning control program of this embodiment, it is determined that the end condition is met when the execution time Tmdf of the defrost mode becomes equal to or greater than the reference defrosting time KTmdf and the outdoor unit temperature Tout becomes equal to or greater than the predetermined reference defrost temperature KToutdf.

As described above, the vehicle air conditioner 1 of this embodiment can achieve comfortable air conditioning in the vehicle cabin by switching the operating mode.

Furthermore, in the vehicle air conditioner 1 of this embodiment, a desiccant material 15a is applied to the interior evaporator 15. Therefore, during the adsorption process in the dehumidification heating mode, the adsorption action of the desiccant material 15a can be used to dehumidify the blown air. This reduces the power consumption of the compressor 11 consumed for dehumidification, and improves 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.

In addition, in the defrost mode, the blown air that has been cooled and dehumidified by the interior evaporator 15 can be reheated by the interior condenser 12. Therefore, even if the rotation speed of the compressor 11 is determined to an extent that allows the refrigeration oil to be appropriately returned to the compressor 11, the temperature drop in the passenger compartment can be suppressed.

In other words, according to the vehicle air conditioner 1 of this embodiment, the indoor evaporator 15 coated with the desiccant material 15a provides the effect of improving the operating efficiency, while allowing the refrigeration oil to be appropriately returned to the compressor 11 regardless of the operating mode.

In addition, in the vehicle air conditioner 1 of this embodiment, the adsorption process and the desorption process are switched during the dehumidification heating mode. During the adsorption process in the dehumidification heating mode, the inside/outside air switching device 33 increases the proportion of inside air in the blown air flowing into the interior evaporator 15 compared to the outside air.

As a result, during the adsorption process, the inside air, which is hotter and more humid than the outside air, can be introduced into the interior evaporator 15 in greater amounts than the outside air. This reduces the power consumption of the compressor 11 used to reheat the blown air, and further improves the coefficient of performance of the refrigeration cycle device 10. As a result, the operating efficiency of the vehicle air conditioner 1 can be further improved.

Furthermore, during the desorption process in the dehumidification heating mode, the inside/outside air switching device 33 increases the proportion of outside air in the blown air flowing into the indoor evaporator 15 compared to the inside air. As a result, during the desorption process, more outside air with 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 regenerated efficiently.

The vehicle air conditioner 1 of this embodiment is also equipped with an auxiliary outside air introduction device 37. With this, during the desorption process, outside air with a lower humidity than the inside air can be reheated in the interior condenser 12 and blown into the vehicle cabin. Therefore, when the dehumidification heating mode is being executed, even if the adsorption process is switched to the desorption process, the heating of the vehicle cabin can be continued. Furthermore, the occurrence of fogging of the vehicle window glass during the desorption process can also be suppressed.

In addition, in the vehicle air conditioner 1 of this embodiment, the amount of heat of the blown air in the interior condenser 12 is reduced in the defrost mode. This allows the heat of the refrigerant discharged from the compressor 11 in the defrost mode to be used for defrosting the exterior heat exchanger 16, with priority given to heating the blown air. Therefore, the defrosting of the exterior heat exchanger 16 can be completed quickly.

The vehicle air conditioner 1 of this embodiment is also equipped with an exhaust device 38, which exhausts the air that has passed through the interior evaporator 15 to the outside of the vehicle compartment during the desorption process in the dehumidification heating mode. This reliably prevents the humidity in the vehicle compartment from increasing due to the moisture desorbed from the desiccant material 15a. In other words, it effectively prevents the vehicle window glass from fogging up during the desorption process.

Second Embodiment
In this embodiment, a vehicle air conditioner 1a shown in the overall configuration diagrams of Figures 6 and 7 will be described. The vehicle air conditioner 1a not only conditions the air inside the vehicle cabin, but also has a function of 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 has a refrigeration cycle device 10a, an interior air conditioning 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 through which the high-pressure refrigerant discharged from the compressor 11 flows, and a water passage through which the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40 flows.

The water-refrigerant heat exchanger 12a is a heat exchanger for heating the heat medium that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage. In the water-refrigerant heat exchanger 12a, the heat of the high-pressure refrigerant is dissipated to the high-temperature heat medium, condensing the high-pressure refrigerant and heating the high-temperature heat medium.

The inlet 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 inlets and outlets that communicate with each other. The first three-way joint 17a can be a member formed by joining multiple pipes, or a member formed by providing multiple refrigerant passages in a metal block or resin block.

Furthermore, the refrigeration cycle device 10a is equipped with a second three-way joint 17b to a fourth three-way joint 17d, as described below. The basic configurations of the second three-way joint 17b to the fourth three-way joint 17d are the same as that of the first three-way joint 17a.

When one of the three inlet/outlet ports of the first three-way joint 17a to the fourth three-way joint 17d is used as an inlet and the other two are used as outlet ports, the flow of refrigerant flowing in from one inlet port can be branched. In this embodiment, the first three-way joint 17a is the branching part. Also, when two of the three inlet/outlet ports are used as inlet ports and the other one is used as outlet port, the flow of refrigerant flowing in from the two inlets can be merged.

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

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

Furthermore, the refrigeration cycle device 10a is equipped with a low-pressure on-off valve 13b, as described below. The basic configuration of the low-pressure on-off valve 13b is similar to 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 for each operating 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 unit of this embodiment.

The heating expansion valve 14c is an outdoor pressure reducing section that reduces the pressure of the refrigerant flowing into the outdoor heat exchanger 16 during the dehumidification heating mode described below. The heating expansion valve 14c is an outdoor refrigerant flow rate adjusting section that adjusts the flow rate of the refrigerant flowing downstream. 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.

Furthermore, the refrigeration cycle device 10a is equipped with a cooling expansion valve 14d and a cooling expansion valve 14e, as described below. The basic configurations of the cooling expansion valve 14d and the cooling expansion valve 14e are also similar to that of the first expansion valve 14a.

In addition to the fully open function described above, the heating expansion valve 14c, the cooling expansion valve 14d, and the cooling expansion valve 14e have a fully closed function that blocks the refrigerant passage by fully closing the valve opening. Therefore, the heating expansion valve 14c, the cooling expansion valve 14d, and the cooling expansion valve 14e also function as a refrigerant circuit switching unit that switches the refrigerant circuit by exerting the 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 that does not have a full closing function with an on-off valve. In this case, the on-off valve serves as the refrigerant circuit switching unit.

The outlet of the heating expansion valve 14c is connected to the refrigerant inlet side of the outdoor heat exchanger 16, which is the outdoor heat exchanger. The refrigerant outlet of the outdoor heat exchanger 16 is connected to the inlet side of the third three-way joint 17c. One outlet of the third three-way joint 17c is connected to one inlet side of the evaporation pressure control valve 20 via a heating passage 22b. A low pressure opening/closing valve 13b that opens and closes the heating passage 22b is arranged in the heating passage 22b.

The other outlet of the third three-way joint 17c is connected to the other inlet side of the second three-way joint 17b. 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 outlet of the second three-way joint 17b is connected to the inlet side of the fourth three-way joint 17d. The inlet side of the cooling expansion valve 14d is connected to one outlet 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 reduction units that reduce the pressure of the refrigerant.

More specifically, the cooling expansion valve 14d is an air cooling pressure reduction section that reduces the pressure of the refrigerant flowing into the indoor evaporator 15 during the single cooling mode described below. The cooling expansion valve 14d is an air refrigerant flow rate adjustment section that adjusts the flow rate of the refrigerant flowing downstream.

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

The cooling expansion valve 14e is a heat medium cooling pressure reducing section that reduces the pressure of the refrigerant flowing into the chiller 19 during the cooling/cooling mode described below. The cooling expansion valve 14e is an equipment cooling refrigerant flow rate adjusting section that adjusts the flow rate of the refrigerant flowing downstream.

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

The chiller 19 is a heat exchanger that exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage and the low-temperature heat medium flowing through the water passage. In the chiller 19, the low-pressure refrigerant is evaporated to exert a heat absorption effect, thereby cooling the low-temperature heat medium. The third inlet side of the evaporation pressure adjustment valve 20 is connected to the outlet of the refrigerant passage of the chiller 19.

The evaporation pressure adjustment valve 20 is a pressure adjustment 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. Furthermore, the evaporation pressure adjustment valve 20 merges at least two or more refrigerant flows from the outdoor heat exchanger 16, the indoor evaporator 15, and the chiller 19, and allows them to flow downstream.

Specifically, the evaporative pressure regulating valve 20 is an integrated unit of three electrically operated variable throttle mechanisms connected downstream of the outdoor heat exchanger 16, the indoor evaporator 15, and the chiller 19, and the junction 17g. The operation of the evaporative pressure regulating 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 junction 17g of the evaporation pressure adjustment valve 20. The accumulator 21 is a low-pressure gas-liquid separator that separates the low-pressure refrigerant flowing out from the heat exchanger that functions as an evaporator into gas and liquid. The accumulator 21 stores the separated liquid-phase refrigerant as surplus refrigerant for the cycle.

Therefore, the confluence section 17g of the evaporation pressure control valve 20 merges the refrigerant flow from the outdoor heat exchanger 16, the refrigerant flow from the indoor evaporator 15, and the refrigerant flow from the chiller 19, and causes the refrigerant to flow 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. The high-temperature side heat medium circuit 40 uses an aqueous ethylene glycol solution as the high-temperature side heat medium. The high-temperature side heat medium circuit 40 includes 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.

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 (i.e., pumping capacity) is controlled by the control voltage output from the control device 60.

The outlet of the water passage of the water-refrigerant heat exchanger 12a is connected to the heat medium inlet side of the heater core 42. The heater core 42 is disposed 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 exchanger that exchanges heat between the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a and the blown air. The heater core 42 heats the blown air by dissipating heat from the high-temperature side heat medium to 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 this embodiment, the water-refrigerant heat exchanger 12a and the components of the high-temperature side heat medium circuit 40 form a heating section that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source.

In addition, 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, thereby changing the amount of heat exchange between the high-temperature side heat medium in the heater core 42 and the blown air. Therefore, the high-temperature side heat medium pump 41 is a heat amount adjustment unit that adjusts the amount of heating 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, the same type of fluid as the high-temperature side heat medium can be used. In the low-temperature side heat medium circuit 50, the water passage of the chiller 19, the low-temperature side heat medium pump 51, the cooling water passage 80a of the battery 80, etc. are arranged.

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

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

The cooling water passage 80a is a heat medium device heat exchanger formed inside the battery case that houses the battery cells of the battery 80. The cooling water passage 80a is configured by connecting multiple passages in parallel inside the battery case. This allows the cooling water passage 80a to cool all the battery cells evenly. The outlet of the cooling water passage 80a is connected to the suction port side of the low-temperature side heat medium pump 51.

In this embodiment, therefore, the chiller 19 and each component of the low-temperature side heat medium circuit 50 form a cooling section for cooling the battery 80, which generates heat during operation. Furthermore, the chiller 19 is a cooling heat exchange section 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 section for cooling the heat medium to cool the battery 80.

Next, the electrical control unit of the vehicle air conditioner 1a will be outlined with reference to FIG. 8. The control device 60 of this 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.

As shown in FIG. 8, in addition to the various control sensors described in the first embodiment, a battery temperature sensor 61j, a high-temperature heat medium temperature sensor 61k, a low-temperature heat medium temperature sensor 61m, etc. are added to the input side of the control device 60.

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 multiple temperature detection units and detects the temperature of multiple locations on the battery 80. Therefore, the control device 60 can also detect the temperature difference between each part of the battery 80. Furthermore, the average value of the detection values of the multiple temperature sensors is used as the battery temperature TB.

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 detection 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.

In the present embodiment, the controller 60 is configured to control 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. The high temperature side pump controller 60d is configured to control the operation of the high temperature side heat medium pump 41. The low pressure side pump controller 60e is configured to control the operation of the low pressure side heat medium pump 61.

Next, the operation of the vehicle air conditioner 1a will be described. The vehicle air conditioner 1a not only conditions the air inside the vehicle cabin, but also switches between various operating modes to cool the battery 80. As in the first embodiment, the switching of operating modes is performed by executing an air conditioning control program that is pre-stored in the control device 60. The operation of each operating mode will be described below.

(a) Cooling Mode The cooling modes of the vehicle air conditioner 1a include a single cooling mode and a cool and cool mode. The single cooling mode is an operation mode in which the vehicle cabin is cooled without cooling the battery 80. The single cooling mode is executed when the same execution conditions for the cooling mode as those in the first embodiment are met and it is determined that cooling of the battery 80 is not necessary.

The cooling/air-conditioning mode is an operating mode that cools the battery 80 and also cools the vehicle interior. The cooling/air-conditioning mode is executed when the conditions for executing the cooling mode are met similar to those in the first embodiment, and it is determined that cooling of the battery 80 is necessary.

Whether or not cooling of the battery 80 is required is determined when the battery temperature TB detected by the battery temperature sensor 61j is equal to or higher than a predetermined reference cooling temperature KTB. Also, when the battery temperature TB is lower than the reference cooling temperature KTB, it is determined that cooling of the battery 80 is not required. The determination of whether or not cooling of the battery 80 is required is performed in the same manner in the following operating 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. The control device 60 also fully opens the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e.

Therefore, in the refrigeration cycle device 10a in the cooling only mode, as shown by the white arrow in Figure 6, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: water-refrigerant heat exchanger 12a, heating expansion valve 14c which is fully open, outdoor heat exchanger 16, check valve 18, cooling expansion valve 14d, indoor evaporator 15, evaporation pressure control valve 20, accumulator 21, and the intake port of compressor 11.

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

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

Therefore, in the refrigeration cycle device 10a in the sole cooling mode, the water-refrigerant heat exchanger 12a and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 15 functions as an evaporator, forming a vapor compression refrigeration cycle. In the refrigeration cycle device 10a in the sole cooling mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. The blown air is cooled in the indoor evaporator 15.

In addition, 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the indoor air conditioning unit 30 in the single cooling mode, 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 depending on the opening degree of the air mix door 34.

The blown air that flows into the heating passage 35a is heated as it passes through the heater core 42. The blown air heated by the heater core 42 flows into the mixing space 36, similar to the cooling mode of the first embodiment. The blown air that flows into the cold air bypass passage 35b flows into the mixing space 36, similar to the cooling mode of the first embodiment.

The air that has been mixed and temperature-adjusted in the mixing space 36 is then blown out through the opening to an appropriate location in the vehicle cabin. This provides cooling for the vehicle cabin.

(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. The control device 60 also sets the heating expansion valve 14c to a fully open state, the cooling expansion valve 14d to a throttled state, and the cooling expansion valve 14e to a throttled state.

Therefore, in the refrigeration cycle device 10a in the cooling/cooling mode, as shown by the black arrows in FIG. 6, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 12a, 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 control valve 20, the accumulator 21, and the intake port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12a, the heating expansion valve 14c which is fully open, the outdoor heat exchanger 16, the check valve 18, the cooling expansion valve 14e, the chiller 19, the evaporation pressure control valve 20, the accumulator 21, and the intake port of the compressor 11.

In other words, in the refrigeration 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, and the other refrigerant flows into the cooling expansion valve 14e and the chiller 19. Then, the refrigerant flowing out of the indoor evaporator 15 and the chiller 19 are switched to a refrigerant circuit in which they merge at the merging point 17g of the evaporation pressure adjustment valve 20.

In other words, in the refrigeration cycle device 10a in the cooling/air-conditioning mode, the indoor evaporator 15 and chiller 19 are switched to a refrigerant circuit in which they are connected in parallel to the refrigerant flow.

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

In addition, the control device 60 determines the control signal output to the evaporation pressure regulating valve 20 so that the refrigerant evaporation pressure in the indoor evaporator 15 and the refrigerant evaporation pressure in the chiller 19 are appropriate values.

The control signals, etc., to be output to the other controlled devices are determined in the same manner as for the single cooling mode. The control device 60 then outputs the control signals, etc., determined as described above, to the 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, forming a vapor compression refrigeration cycle. In the refrigeration cycle device 10a in the cooling/cooling mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. The blown air is cooled in the indoor evaporator 15. The low-temperature side heat medium is cooled in the chiller 19.

In addition, in the high-temperature side heat medium circuit 40 in the cooling/air-conditioning mode, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a flows into the heater core 42, just as in the single cooling mode.

In addition, in the low-temperature side heat medium circuit 50 in the cooling/air-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 in the chiller 19 flows through the cooling water passage 80a of the battery 80. This cools the battery 80.

In addition, in the interior air conditioning unit 30 in the air conditioning battery cooling mode, the temperature of the blown air is adjusted and blown out to an appropriate location in the vehicle cabin, just as in the single air conditioning mode. This achieves cooling of the vehicle cabin.

(b) Dehumidifying and heating mode The dehumidifying and heating mode of the vehicle air conditioner 1a includes an independent dehumidifying and heating mode and a cooling and dehumidifying and heating mode. The independent dehumidifying and heating mode is an operation mode that dehumidifies and heats the vehicle interior without cooling the battery 80. The independent dehumidifying and heating mode is executed when the execution conditions for the dehumidifying and heating mode similar to those of the first embodiment are met and it is determined that cooling of the battery 80 is not necessary.

The cooling, dehumidifying, and heating mode is an operating mode that cools the battery 80 and dehumidifies and cools the vehicle interior. The cooling, dehumidifying, and heating mode is executed when the conditions for executing the dehumidifying and heating mode are met, similar to those in the first embodiment, and it is determined that cooling of the battery 80 is necessary.

In addition, in the vehicle air conditioner 1a, the adsorption action of the desiccant material 15a is used to dehumidify the blown air in the dehumidifying heating mode. Therefore, in the dehumidifying heating mode, the adsorption process and the desorption process are switched at a predetermined cycle, as in the first embodiment.

(b-1) Single dehumidification and heating mode In the adsorption process of the single dehumidification and heating mode, the controller 60 opens the high pressure valve 13a and the low pressure valve 13b. The controller 60 also sets the heating expansion valve 14c in a throttled state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigeration cycle device 10a in the adsorption process of the single dehumidification heating mode, as shown by the white arrows in Figure 7, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 12a, the first three-way joint 17a, the heating expansion valve 14c, the outdoor heat exchanger 16, the heating passage 22b, the evaporation pressure control valve 20, the accumulator 21, and the intake 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 first three-way joint 17a, the bypass passage 22a, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure control valve 20, the accumulator 21, and the intake port of the compressor 11.

In other words, in the refrigeration cycle device 10a in the adsorption process of the single dehumidification 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, and the other refrigerant flows into the cooling expansion valve 14d and the indoor evaporator 15. Then, the refrigerant flowing out of the outdoor heat exchanger 16 and the refrigerant flowing out of the indoor evaporator 15 are switched to a refrigerant circuit where they merge at the merging point 17g of the evaporation pressure adjustment valve 20.

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

Furthermore, the control device 60 appropriately determines the control signals to be output to the various controlled devices. For example, the control device 60 determines the control voltage to be output to the high-temperature side heat medium pump 41 so that the high-temperature side heat medium pump 41 exerts a predetermined pumping capacity. Furthermore, the control device 60 determines the control voltage to be output to the low-temperature side heat medium pump 51 so that the low-temperature side heat medium pump 51 is stopped.

In addition, the control device 60 determines the control signal output to the evaporation pressure regulating valve 20 so 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 control signals to be output to the other controlled devices are determined in the same manner as in the adsorption process of the dehumidification heating mode in the first embodiment. The control device 60 then outputs the control signals determined as described above to the various controlled devices.

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

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

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

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

In other words, in the refrigeration cycle device 10a in the adsorption process of the single dehumidification 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 evaporators to configure a vapor compression refrigeration cycle. In the refrigeration cycle device 10a in the adsorption process of the single dehumidification heating mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. The blown air is cooled and dehumidified in the indoor evaporator 15.

In addition, in the high-temperature side heat medium circuit 40 during the adsorption process in the single dehumidification 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In the indoor air conditioning unit 30 during the adsorption process in the single dehumidification heating mode, the indoor air introduced into the casing 31 via the indoor/outdoor air switching device 33 is sucked into the indoor blower 32 as blown air, as shown by the dashed arrows in the Mollier diagram of FIG. 9. The blown air blown from the indoor blower 32 is cooled and dehumidified as it passes through the indoor evaporator 15.

In addition, during the adsorption process, the adsorption action of the desiccant material 15a also dehumidifies the blown air passing through the interior evaporator 15. The blown air that has been cooled and dehumidified by the interior evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b depending on the opening degree of the air mix door 34. The blown air that flows into the heating passage 35a is heated by heat exchange with the high-temperature heat medium as it passes through the heater core 42.

Note that in FIG. 9, the blown air that flows into the heating passage 35a is shown as if it were passing through the water-refrigerant heat exchanger 12a, but FIG. 9 shows the transfer of heat between the blown air and the refrigerant as a schematic. In other words, FIG. 9 shows that the blown air that flows into the heating passage 35a is heated using the heat dissipated by the refrigerant in the water-refrigerant heat exchanger 12a as a heat source. This is also true in the Mollier diagram using the water-refrigerant heat exchanger 12a and chiller 19 described below.

The blown air that flows 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 that has been mixed and temperature-adjusted in the mixing space 36 is blown out to an appropriate location in the vehicle cabin through the opening. This achieves dehumidification and heating in the vehicle cabin.

Next, in the desorption process of the single dehumidification heating mode, the control device 60 opens the high pressure on-off valve 13a and closes the low pressure on-off valve 13b. The control device 60 also fully closes the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e.

Therefore, in the refrigeration cycle device 10a during the desorption process in the single dehumidification heating mode, as shown by the hatched arrows in Figure 7, the refrigerant discharged from the compressor 11 circulates in the following order: water-refrigerant heat exchanger 12a, bypass passage 22a, cooling expansion valve 14d, indoor evaporator 15, evaporation pressure control valve 20, accumulator 21, and the intake port of the compressor 11.

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

The control signal output to the cooling expansion valve 14d is determined to be a predetermined standard throttle opening for the desorption process. The standard throttle opening for the desorption process is determined so that the temperature of the refrigerant flowing into the indoor evaporator 15 is a temperature at which moisture can be desorbed from the desiccant material 15a. Furthermore, the standard throttle opening for the desorption process 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, the cooling expansion valve 14 may be fully open during the desorption process.

In addition, the control device 60 determines the control signal output to the evaporation pressure regulating valve 20 so that the refrigerant evaporation pressure in the accumulator 21 is an appropriate value.

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 process.

The control signals etc. to be output to the other controlled devices are determined in the same manner as in the desorption process of the dehumidification heating mode in the first embodiment. Then, the control device 60 outputs the control signals etc. determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10a during the desorption process in the single dehumidification heating mode, as shown in the Mollier diagram of FIG. 10, the refrigerant discharged from the compressor 11 (point a10 in FIG. 10) flows into the water-refrigerant heat exchanger 12a. The refrigerant that flows into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and dissipates heat (point a10 → point b10 in FIG. 10).

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

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

In other words, in the refrigeration cycle device 10a in the desorption process of the single dehumidification heating mode, the water-refrigerant heat exchanger 12a and the indoor evaporator 15 function as radiators, forming a so-called hot gas cycle. In the refrigeration cycle device 10a in the desorption process, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a.

In addition, in the high-temperature side heat medium circuit 40 during the desorption process in the single dehumidification 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the indoor air conditioning unit 30 during the desorption process in the single dehumidification 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.

As shown by the dashed arrows in the Mollier diagram of FIG. 10, a portion of the outside air blown from the indoor blower 32 is humidified by moisture desorbed from the desiccant material as it passes through the indoor evaporator 15. This regenerates the desiccant material 15a. The outside air that has passed through the indoor evaporator 15 is exhausted to the outside of the vehicle cabin from the exhaust port 31b of the exhaust device 38, similar to the desorption process in the dehumidification heating mode of the first embodiment.

Another portion of the outside air blown from the interior blower 32 flows from the auxiliary outside air inlet 31a through the outside air bypass passage 35c into the heating passage 35a. As in the desorption process of the dehumidification heating mode of the first embodiment, the outside air that flows into the heating passage 35a is heated using the heat dissipated by the refrigerant in the water-refrigerant heat exchanger 12a as a heat source when passing through the heater core 42 as blown air, and is blown out into the passenger compartment. This allows the passenger compartment to be heated even during the desorption process of the single dehumidification heating mode.

(b-2) Cooling, dehumidifying and heating mode In the adsorption process of the cooling, dehumidifying and heating mode, the control device 60 opens the high pressure on-off valve 13a and the low pressure on-off valve 13b. The control device 60 also sets the heating expansion valve 14c to a throttled state, the cooling expansion valve 14d to a throttled state, and the cooling expansion valve 14e to a throttled state.

Therefore, in the refrigeration cycle device 10a in the adsorption stroke of the cooling/dehumidifying/heating mode, as shown by the black arrows in Figure 7, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 12a, the first three-way joint 17a, the heating expansion valve 14c, the outdoor heat exchanger 16, the heating passage 22b, the evaporation pressure control valve 20, the accumulator 21, and the intake 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 first three-way joint 17a, the bypass passage 22a, the fourth three-way joint 17d, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure control valve 20, the accumulator 21, and the intake port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 circulates through the water-refrigerant heat exchanger 12a, the first three-way joint 17a, the bypass passage 22a, the fourth three-way joint 17d, the cooling expansion valve 14e, the chiller 19, the evaporation pressure control valve 20, the accumulator 21, and the suction port of the compressor 11 in that order.

In other words, in the refrigeration cycle device 10a during the adsorption process in 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, and the other refrigerant flows into the fourth three-way joint 17d. Furthermore, 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.

Then, the refrigerant flowing out from the outdoor heat exchanger 16, the refrigerant flowing out from the indoor evaporator 15, and the refrigerant flowing out from the chiller 19 are switched to a refrigerant circuit in which they merge at the junction 17g of the evaporation pressure adjustment valve 20.

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

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

In addition, the control device 60 determines the control signal output to the evaporation pressure adjustment valve 20 so that 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 are appropriate values.

The control signals to be output to the other controlled devices are determined in the same manner as in the adsorption process of the dehumidification heating mode in the first embodiment. The control device 60 then outputs the control signals determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10a in the adsorption process of the cooling, dehumidifying and 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 evaporators to form a vapor compression refrigeration cycle.

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

In addition, in the high-temperature side heat medium circuit 40 during the adsorption process in the cooling/dehumidifying/heating mode, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a flows into the heater core 42, just as in the adsorption process in the single dehumidifying/heating mode.

In addition, in the low-temperature side heat medium circuit 50 during the adsorption process in the cooling, dehumidifying, and 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 in the chiller 19 flows through the cooling water passage 80a of the battery 80. This cools the battery 80.

In addition, in the interior air conditioning unit 30 during the adsorption process in the cooling, dehumidifying and heating mode, the blown air is dehumidified and temperature-adjusted, and then blown out to an appropriate location in the vehicle cabin, just as in the adsorption process in the single dehumidifying and heating mode. This achieves dehumidifying and heating the vehicle cabin.

Next, in the desorption process 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. The control device 60 also fully closes the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10a in the desorption process of the single dehumidifying/heating mode, a refrigerant circuit is formed in which the refrigerant circulates in the same order as in the desorption process of the single dehumidifying/heating mode.

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

The control signals etc. to be output to the other controlled devices are determined in the same manner as in the desorption process of the dehumidification heating mode in the first embodiment. Then, the control device 60 outputs the control signals etc. determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10a during the desorption process in the cooling/dehumidifying/heating mode, a hot gas cycle is formed in which the water-refrigerant heat exchanger 12a and the indoor evaporator 15 function as a radiator, just like in the desorption process in the single dehumidifying/heating mode. And, in the refrigeration cycle device 10a during the desorption process, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a.

In addition, in the high-temperature side heat medium circuit 40 during the desorption process in 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the low-temperature side heat medium circuit 50 during the desorption process in the cooling/dehumidifying/heating mode, the low-temperature side heat medium pumped from the low-temperature side heat medium pump 51 circulates. Therefore, while the desorption process is being performed, the battery 80 can continue to be cooled by the low-temperature side heat medium cooled during the adsorption process. In other words, the amount of low-temperature side heat medium sealed in is determined so that it has a heat capacity sufficient to continue the refrigerant of the battery 80 during the desorption process.

In addition, in the desorption process of the cooling, dehumidifying and heating mode, the desiccant material 15a of the interior evaporator 15 is regenerated in the interior air conditioning unit 30 in the same manner as in the desorption process of the single dehumidifying and heating mode. The outside air that is humidified while passing through the interior evaporator 15 is exhausted to the outside of the vehicle cabin through the exhaust port 31b of the exhaust device 38.

Furthermore, the outside air that flows into the heating passage 35a via the outside air bypass passage 35c is heated by heat exchange with the high-temperature heat medium heated in the water-refrigerant heat exchanger 12a as it passes through the heater core 42 as blown air, and is then blown into the passenger compartment. This allows the passenger compartment to be heated even during the desorption process in the cooling/dehumidifying/heating mode.

(c) Defrosting Mode The defrosting modes of the vehicle air conditioner 1a include an individual defrosting mode and a waste heat defrosting mode. The individual defrosting mode is an operation mode in which the exterior heat exchanger 16 is defrosted without cooling the battery 80. The individual defrosting mode is executed when a frosting condition is met while the individual dehumidification heating mode is being executed. The individual defrosting mode is terminated when a termination condition is met. When the defrosting mode is terminated, the operation transitions to the individual dehumidification heating mode.

The waste heat defrost mode is an operating mode that cools the battery 80 and defrosts the outdoor heat exchanger 16. The waste heat defrost mode is executed when the frosting conditions are met while the cooling, dehumidifying, and heating mode is being executed. The waste heat defrost mode ends when the termination conditions are met. When the defrost mode ends, the mode transitions to the cooling, dehumidifying, and 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. The control device 60 also fully opens the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10a in the single defrost mode, as shown by the white arrows in FIG. 6, the refrigeration cycle device 10a is switched to a refrigerant circuit in which the refrigerant circulates in the same order as in the single cooling mode.

Furthermore, the control device 60 appropriately determines the control signals to be output to the various controlled devices. For example, the control voltage to be output to the high-temperature side heat medium pump 41 is determined so as to provide a lower pumping capacity than in the single dehumidification heating mode. In addition, the control device 60 determines the control voltage to be output to the low-temperature side heat medium pump 51 so as to stop the low-temperature side heat medium pump 51.

In addition, for the compressor 11, the control device 60 determines the control signal to be output to the compressor 11 so that the rotation speed is lower than in the single dehumidification heating mode. The control signal to be output to the compressor 11 is determined within a range that allows the refrigeration oil mixed in the refrigerant to be returned to the compressor 11.

In addition, the control device 60 determines the control signal output to the electric actuator 34a for the air mix door to reduce the opening area of the inlet of the heating passage 35a by a predetermined amount compared to the dehumidification heating mode. As a result, in the defrost mode, the amount of heating of the blown air in the indoor condenser 12 is reduced compared to the dehumidification heating mode.

The control signals, etc. output to the other controlled devices are determined in the same manner as in the defrost mode of the first embodiment. The control device 60 then outputs the control signals, etc. determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10a in the single defrost mode, as shown in the Mollier 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 that flows into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and condenses (point a11 → point b11 in FIG. 11). The refrigerant that flows out of the water-refrigerant heat exchanger 12a flows into the outdoor heat exchanger 16 via the heating expansion valve 14c, which is fully open.

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

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

In other words, 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 condensers, and the indoor evaporator 15 functions as an evaporator, forming a vapor compression refrigeration cycle.

In the refrigeration cycle device 10a in the single defrost mode, the high-temperature heat medium is heated in the water-refrigerant heat exchanger 12a. The air to be blown is cooled and dehumidified in the indoor evaporator 15. Furthermore, in the outdoor heat exchanger 16, the heat of the refrigerant flowing out from the indoor condenser 12 melts and removes the frost on the outdoor heat exchanger 16. In other words, the outdoor heat exchanger 16 is defrosted.

In addition, in the high-temperature side heat medium circuit 40 in the single defrost 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the indoor air conditioning unit 30 in the single defrost mode, as shown by the dashed arrows in the Mollier diagram of FIG. 11, the blown air that has been cooled and dehumidified in the indoor evaporator 15 is reheated using the heat dissipated by the refrigerant in the water-refrigerant heat exchanger 12a as a heat source as it passes through the heater core 42.

In the single defrost mode, the rotation speed of the compressor 11 is reduced more than in the single dehumidification heating mode. The air mix door 34 is displaced so that the opening area of the entrance to the heating passage 35a is reduced more than in the single dehumidification heating mode. Furthermore, the pumping capacity of the high temperature side heat medium pump 41 is reduced more than in the single dehumidification heating mode. Therefore, although the amount of heating of the blown air in the heater core 42 is reduced more than in the single dehumidification heating mode, the dehumidification 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. The control device 60 also opens the heating expansion valve 14c fully, throttles the cooling expansion valve 14d, and throttles the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10a in the waste heat defrosting mode, as shown by the black arrows in FIG. 6, the refrigeration cycle device 10a is switched to a refrigerant circuit in which the refrigerant circulates in the same order as in the cooling/cooling mode.

Furthermore, the control device 60 appropriately determines the control signals to be output to the various controlled devices. For example, the control voltage to be output to the high-temperature side heat medium pump 41 is determined so that it exerts a lower pumping capacity than in the single dehumidification heating mode. In addition, the control device 60 determines the control voltage to be output to the low-temperature side heat medium pump 51 so that the low-temperature side heat medium pump 51 exerts a predetermined pumping capacity.

In addition, the control device 60 determines the control signal output to the evaporation pressure regulating valve 20 so that the refrigerant evaporation pressure in the indoor evaporator 15 and the refrigerant evaporation pressure in the chiller 19 are appropriate values.

The control signals to be output to the other controlled devices are determined in the same manner as in the defrost mode of the first embodiment. The control device 60 then outputs the control signals determined as described above to the 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 chiller 19 function as evaporators, forming a vapor compression refrigeration cycle.

In the refrigeration cycle device 10a in the waste heat defrost mode, the high-temperature heat medium is heated in the water-refrigerant heat exchanger 12a. The air being blown is cooled and dehumidified in the indoor evaporator 15. The low-temperature heat medium is cooled in the chiller 19. Furthermore, in the outdoor heat exchanger 16, the heat of the refrigerant flowing out from the indoor condenser 12 melts and removes the frost on the outdoor heat exchanger 16. In other words, the outdoor heat exchanger 16 is defrosted.

In addition, in the high-temperature side heat medium circuit 40 in the waste heat defrost 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the low-temperature side heat medium circuit 50 in the waste heat defrost 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 in the chiller 19 flows through the cooling water passage 80a of the battery 80. This cools the battery 80.

In addition, in the waste heat defrost mode, the interior air conditioning unit 30 achieves dehumidification and heating of the vehicle cabin, similar to the single defrost mode. In the waste heat defrost mode, the amount of heat applied to the blown air in the heater core 42 is reduced compared to the cooling, dehumidification and heating mode, but dehumidification and heating of the vehicle cabin can be continued, similar to the single defrost mode, etc.

As described above, the vehicle air conditioner 1a of this embodiment can achieve comfortable air conditioning in the vehicle cabin and proper cooling of heat-generating equipment by switching the operating mode.

Furthermore, in the vehicle air conditioner 1a of this embodiment, the desiccant material 15a is applied to the interior evaporator 15, so the same effect as in the first embodiment can be obtained. That is, according to the vehicle air conditioner 1a of this embodiment, the refrigeration oil can be appropriately returned to the compressor 11 regardless of which operating mode is switched to, while obtaining the effect of improving the operating efficiency by having the interior evaporator 15 to which the desiccant material 15a is applied.

The vehicle air conditioner 1a of this embodiment is also equipped with a cooling expansion valve 14e as a cooling pressure reducing section, and a chiller 19 as a cooling heat exchange section. This allows the battery 80 to be cooled. Furthermore, in the waste heat dehumidification mode, the refrigerant circuit is switched to one in which the refrigerant flowing out of the exterior heat exchanger 16 flows into the cooling expansion valve 14e. This allows the waste heat of the battery 80 to be used as a heat source for defrosting the exterior heat exchanger 16.

Third Embodiment
In this embodiment, a vehicle air conditioner 1b shown in the overall configuration diagrams of Figures 12 and 13 will be described. Like the vehicle air conditioner 1a described in the second embodiment, the vehicle air conditioner 1b not only conditions the air inside the vehicle cabin, but also has a function of 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 has a refrigeration cycle device 10b, an interior air conditioning unit 30, a high-temperature side heat medium circuit 40, and a low-temperature side heat medium circuit 50.

In addition, in Fig. 12 and Fig. 13, the indoor air conditioning unit 30 is omitted for clarity. Therefore, the indoor evaporator 15 of the refrigeration cycle device 10b is disposed 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 disposed in the casing 31 of the indoor air conditioning unit 30.

In the refrigeration cycle device 10b, the accumulator 21 has been eliminated and a receiver 23 has been adopted. The receiver 23 is a high-pressure side gas-liquid separator that separates the high-pressure refrigerant that flows out of the heat exchanger that functions as a condenser into gas and liquid. The receiver 23 allows a portion of the separated liquid-phase refrigerant to flow downstream and stores the remaining liquid-phase refrigerant as surplus refrigerant for 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. The second high-pressure on-off valve 13d and the 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 the refrigerant passage from one outlet of the first three-way joint 17a to one inlet of the fifth three-way joint 17e. The other inlet of the fifth three-way joint 17e is connected to the outlet side of the receiver 23 via the outlet side passage 22d. The sixth three-way joint 17f and the second check valve 18b are arranged in the outlet side passage 22d. The remaining outlet of the sixth three-way joint 17f is connected to the inlet side of the fourth three-way joint 17d.

The second check valve 18b allows the refrigerant to flow from the sixth three-way joint 17f to the fifth three-way joint 17e, and prohibits the refrigerant from flowing from the fifth three-way joint 17e to the sixth three-way joint 17f. 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 prohibits the refrigerant from flowing from the inlet side of the heating expansion valve 14c to the outlet side of the receiver 23.

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, etc. The basic configuration of the first high pressure on-off valve 13c and the second high pressure on-off valve 13d is the same as that of the high pressure on-off valve 13a, etc. 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, for the sake of clarity, the check valve 18 described in the first embodiment will be referred to as the first check valve 18a. The rest of the configuration of the 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 modes 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. The control device 60 also fully opens the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e.

Therefore, in the refrigeration cycle device 10b in the cooling only mode, as shown by the white arrow in Figure 12, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: water-refrigerant heat exchanger 12a, heating expansion valve 14c which is fully open, outdoor heat exchanger 16, first check valve 18a, receiver 23, cooling expansion valve 14d, indoor evaporator 15, evaporation pressure control valve 20, and the suction port of compressor 11.

Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices. For example, the control signal to be output to the cooling expansion valve 14d is determined by the control device 60 so that the refrigerant on the outlet side of the indoor evaporator 15 approaches a predetermined target degree of superheat.

The control signals etc. to be output to other controlled devices are determined in the same manner as in the single cooling mode of the second embodiment. The control device 60 then outputs the control signals etc. determined as described above to the various controlled devices. Therefore, the vehicle air conditioner 1b in the single cooling mode can cool the vehicle interior in the same manner as in the second embodiment.

Furthermore, in the refrigeration cycle device 10b in the single cooling mode, the excess refrigerant in the cycle is stored in the receiver 23, so the refrigerant on the outlet side of the indoor evaporator 15 can be made to have a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the indoor evaporator 15 can be increased, and the cooling capacity of the blown air can be improved, compared to a cycle in which the excess refrigerant in the cycle is stored in an 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. The control device 60 also fully opens the heating expansion valve 14c, throttles the cooling expansion valve 14d, and throttles the cooling expansion valve 14e.

Therefore, in the refrigeration cycle device 10b in the cooling/cooling mode, as shown by the black arrows in FIG. 12, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 12a, 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 adjustment valve 20, and the intake port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12a, 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 14e, the chiller 19, the evaporation pressure adjustment valve 20, and the intake port of the compressor 11.

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

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

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

Furthermore, in the refrigeration cycle device 10b in the cooling/air-conditioning mode, the refrigerant on the outlet side of the indoor evaporator 15 and the refrigerant on the outlet side of the chiller 19 can be made to have a degree of superheat. Therefore, similar to the single cooling mode, the amount of heat absorbed by the refrigerant in the indoor evaporator 15 can be increased, improving the cooling capacity of the blown air. Furthermore, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased, improving the cooling capacity of the battery 80.

(b-1) Single dehumidification and heating mode In the adsorption process of the single dehumidification and 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. The control device 60 also sets the heating expansion valve 14c in a throttled state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a fully closed state.

Therefore, in the refrigeration cycle device 10b in the adsorption process of the single dehumidification heating mode, as shown by the white arrow in Figure 13, the refrigerant discharged from the compressor 11 circulates in the order of 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 heating expansion valve 14c, the outdoor heat exchanger 16, the heating passage 22b, the evaporation pressure adjustment valve 20, and the intake 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 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, the evaporation pressure adjustment valve 20, and the intake port of the compressor 11.

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

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

The control signals etc. output to other controlled devices are determined in the same manner as in the adsorption process of the single dehumidification heating mode of the second embodiment. The control device 60 then outputs the control signals etc. determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b during the adsorption process of the single dehumidification heating mode, the adsorption action of the desiccant material 15a can be used to dehumidify and heat the vehicle interior, as in the second embodiment.

Furthermore, in the refrigeration cycle device 10b in the adsorption process in the single dehumidification heating mode, the refrigerant on the outlet side of the outdoor heat exchanger 16 and the refrigerant on the outlet side of the indoor evaporator 15 can be made to have a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, improving the heating capacity of the blown air. Furthermore, the amount of heat absorbed by the refrigerant in the indoor evaporator 15 can be increased, improving the cooling capacity of the blown air.

Next, in the desorption process of the single dehumidification 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. The control device 60 also fully closes the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e.

Therefore, in the refrigeration cycle device 10b during the desorption process in the single dehumidification heating mode, as shown by the hatched arrows in Figure 13, the refrigerant discharged from the compressor 11 circulates in the following order: water-refrigerant heat exchanger 12a, inlet side passage 22c, receiver 23, cooling expansion valve 14d, indoor evaporator 15, evaporation pressure control valve 20, and the suction port of compressor 11.

Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices, similar to the desorption process in the single dehumidification heating mode of the second embodiment.

Therefore, in the refrigeration cycle device 10b during the desorption process in the single dehumidification heating mode, a hot gas cycle is formed in which the water-refrigerant heat exchanger 12a and the indoor evaporator 15 function as a radiator. Furthermore, in the refrigeration cycle device 10b during the desorption process, high-temperature gas-phase refrigerant flows into the receiver 23, so that the receiver 23 functions as a refrigerant passage.

Therefore, in the vehicle air conditioner 1b during the desorption process in the single dehumidification heating mode, the desiccant material 15a can be regenerated and the vehicle interior can be heated, similar to the desorption process in the single dehumidification heating mode of the second embodiment.

(b-2) Cooling, dehumidifying and heating mode In the adsorption process of the cooling, dehumidifying and 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. The control device 60 also sets the heating expansion valve 14c in a throttled state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a throttled state.

Therefore, in the refrigeration cycle device 10b in the adsorption stroke of the cooling/dehumidifying/heating mode, as shown by the black arrows in Figure 13, the refrigerant discharged from the compressor 11 circulates in the order of 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 heating expansion valve 14c, the outdoor heat exchanger 16, the heating passage 22b, the evaporation pressure control 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 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, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure control valve 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 circulates through the water-refrigerant heat exchanger 12a, the inlet passage 22c, the receiver 23, the sixth three-way joint 17f of the outlet passage 22d, the fourth three-way joint 17d, the cooling expansion valve 14e, the chiller 19, the evaporation pressure control valve 20, and the suction port of the compressor 11 in that order.

That is, in the refrigeration cycle device 10b during the adsorption process in the cooling/dehumidifying/heating mode, the refrigerant circuit is switched to one in which 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.

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

The control signal output to the cooling expansion valve 14d is determined by the control device 60 so that the degree of superheat of the refrigerant on the outlet side of the indoor evaporator 15 approaches the target degree of superheat. The control signal output to the cooling expansion valve 14e is determined by the control device 60 so that the degree of superheat of the refrigerant on the outlet side of the chiller 19 approaches the target degree of superheat.

The control signals etc. output to the other controlled devices are determined in the same manner as in the adsorption process of the cooling, dehumidifying and heating mode of the second embodiment. The control device 60 then outputs the control signals etc. determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b during the adsorption process of the cooling, dehumidifying and heating mode, the battery 80 can be cooled and the interior of the vehicle can be dehumidified and heated, similar to the second embodiment.

Furthermore, in the adsorption process refrigeration cycle device 10b in the cooling, dehumidifying and heating mode, the refrigerant on the outlet side of the outdoor heat exchanger 16, the refrigerant on the outlet side of the indoor evaporator 15, and the refrigerant on the outlet side of the chiller 19 can be made to have 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. 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. Furthermore, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased to improve the cooling capacity of the battery 80.

Next, in the desorption process 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. The control device 60 also fully closes the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e.

Therefore, in the refrigeration cycle device 10b during the desorption process in the cooling, dehumidifying and heating mode, the refrigerant circulates in the refrigerant circuit in the same order as during the desorption process in the single dehumidifying and heating mode, as shown by the hatched arrows in Figure 13.

Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices, similar to the desorption process of the single dehumidification and heating mode in the second embodiment. Therefore, in the vehicle air conditioner 1b during the desorption process of the cooling, dehumidification and heating mode, it is possible to regenerate the desiccant material 15a, continue cooling the battery 80, and heat the vehicle interior, similar to 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. The control device 60 also fully opens the heating expansion valve 14c, throttles the cooling expansion valve 14d, and fully closes the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10b in the single defrost mode, as shown by the white arrows in FIG. 12, the refrigeration cycle device 10b is switched to a refrigerant circuit in which the refrigerant circulates in the same order as in the single cooling mode.

Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices. For example, the control signal to be output to the cooling expansion valve 14d is determined by the control device 60 so that the refrigerant on the outlet side of the indoor evaporator 15 approaches a predetermined target degree of superheat.

The control signals to be output to the other controlled devices are determined in the same manner as in the single defrost mode of the second embodiment. The control device 60 then outputs the control signals determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b in the single defrost mode, defrosting of the exterior heat exchanger 16 and dehumidifying and heating the vehicle interior can be continued in the same manner 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. The control device 60 also opens the heating expansion valve 14c fully, throttles the cooling expansion valve 14d, and throttles the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10b in the single defrosting mode, as shown by the black arrows in FIG. 12, the refrigeration cycle device 10b is switched to a refrigerant circuit in which the refrigerant circulates in the same order as in the single cooling mode.

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

The control signals etc. output to the other controlled devices are determined in the same manner as in the waste heat defrost mode of the second embodiment. The control device 60 then outputs the control signals etc. determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b in the waste heat defrost mode, cooling of the battery 80, defrosting of the exterior heat exchanger 16, and dehumidification and heating of the vehicle interior can be continued in the same manner as in the second embodiment.

As described above, the vehicle air conditioner 1b of this embodiment can achieve comfortable air conditioning in the vehicle cabin and proper cooling of heat-generating equipment by switching the operating mode.

Furthermore, the vehicle air conditioner 1b of this embodiment can also achieve the same effects as the vehicle air conditioner 1a described in the second embodiment. That is, the indoor evaporator 15 to which the desiccant material 15a is applied can improve the operating efficiency, and the refrigeration oil can be appropriately returned to the compressor 11 regardless of the operating mode.

In addition, in the refrigeration cycle device 10b of this embodiment, the refrigerant on the outlet side of the heat exchanger functioning as an evaporator can be made to have a degree of superheat, so the amount of heat absorbed by the refrigerant in the heat exchanger functioning as an evaporator can be increased. This improves the coefficient of performance of the refrigeration cycle device 10b, and further improves the operating efficiency of the vehicle air conditioning device 1b.

Fourth Embodiment
In this embodiment, a vehicle air conditioner 1c shown in the overall configuration diagrams of Figures 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 has a refrigeration cycle device 10c, an interior air conditioning unit 30, a high-temperature side heat medium circuit 40a, and a low-temperature side heat medium circuit 50a.

As in the third embodiment, in Figs. 14 to 19, the indoor air conditioning unit 30 is omitted from the illustration for clarity. Therefore, the indoor evaporator 15 of the refrigeration cycle device 10c is disposed within the casing 31 of the indoor air conditioning unit 30. The heater core 42 of the high-temperature side heat medium circuit 40a is disposed within 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, etc. are eliminated compared 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 branching part.

One of the outlets of the fourth three-way joint 17d is connected to the inlet side of the cooling expansion valve 14d, which is the same as in the second embodiment. The cooling expansion valve 14d in this embodiment is an air cooling pressure reduction section that reduces the pressure of one of the refrigerants branched off at the fourth three-way joint 17d.

The outlet of the cooling expansion valve 14d is connected to the refrigerant inlet side of the indoor evaporator 15, which is the same as in the first embodiment. The indoor evaporator 15 in this embodiment is an air cooling heat exchanger that evaporates the refrigerant decompressed by the cooling expansion valve 14d to cool the blown air.

The other outlet of the fourth three-way joint 17d is connected to the inlet side of the cooling expansion valve 14e, which is the same as in the second embodiment. The cooling expansion valve 14e in this embodiment is a cooling pressure reduction section that reduces the pressure of the other refrigerant branched off at the fourth three-way joint 17d.

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

The inlet side of the evaporation pressure regulating 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 regulating valve 20 of this embodiment individually regulates the refrigerant pressure in the indoor evaporator 15 and the refrigerant pressure in the chiller 19. The rest of the basic configuration of the refrigeration cycle device 10c is the same as that of the refrigeration 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 junction 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 inlet 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 is a three-way flow control valve that can continuously adjust the flow rate of the high-temperature side heat medium flowing out of the water-refrigerant heat exchanger 12a to the high-temperature side radiator 44 side and the flow rate of the heat medium flowing out to the heater core 42 side.

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 outdoor air heat exchanger that exchanges heat between the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a and outdoor air blown by an outdoor air fan (not shown). The high-temperature side radiator 44 is disposed at the front side of the drive unit room, similar to the outdoor heat exchanger 16 described in the second embodiment. One inlet side of the high-temperature side junction 45 is connected to the heat medium outlet of the high-temperature side radiator 44.

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

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

In the low-temperature heat medium circuit 50a, the inlet side of the low-temperature three-way valve 53 is connected to the outlet of the water passage of the chiller 19. The low-temperature three-way valve 53 is a three-way flow control valve that can continuously adjust the flow rate of the low-temperature heat medium flowing out of the chiller 19 to the low-temperature radiator 54 side and the flow rate of the heat medium flowing out to the cooling water passage 80a side of the battery 80, which is the heat medium equipment heat exchanger.

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 outdoor air heat exchanger that exchanges heat between the low-temperature side heat medium cooled by the chiller 19 and outdoor air blown by an outdoor air fan (not shown). The low-temperature side radiator 54 is located at the front side of the drive unit room, downstream of the outdoor air flow of the high-temperature side radiator 44.

Therefore, the low-temperature side radiator 54 exchanges heat between the outside air that has passed through the high-temperature side radiator 44 and the low-temperature side heat medium. Furthermore, in this embodiment, the high-temperature side radiator 44 and the low-temperature side radiator 54 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 this embodiment, some of the components (heat exchange fins in this embodiment) of the high-temperature side radiator 44 and the low-temperature side radiator 54 are formed from common materials. Then, the heat of the high-temperature side heat medium and the heat of the low-temperature side heat medium can be transferred between them via the common components. This allows, for example, the heat of the high-temperature side heat medium flowing through the high-temperature side radiator 44 to 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 can adjust the flow rate of the heat medium supplied to the heater core 42 and the flow rate of the heat medium supplied to the high-temperature side radiator 44, among the high-temperature side heat medium heated by the heat of the refrigerant discharged from the compressor 11.

In other words, 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 in 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 serves as a heat distribution section that distributes the amount of heat supplied to the heating section and the amount of heat supplied to the low-temperature side outside air heat exchange section via the high-temperature side outside air heat exchange section.

Next, an overview of the electrical control unit of the vehicle air conditioner 1c will be described using FIG. 20. The control device 60 of this 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. In this embodiment, the component that controls the operation of the high-temperature side three-way valve 43 in the control device 60 is the high-temperature side circuit control unit 60f. The component that controls 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 rest of the configuration of the 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 modes 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 controller 60 controls the cooling expansion valve 14d to be in a throttled state and the cooling expansion valve 14e to be in a fully closed state.

Therefore, in the refrigeration cycle device 10c in the cooling only mode, as shown by the white arrow in Figure 14, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: water-refrigerant heat exchanger 12a, receiver 23, cooling expansion valve 14d, indoor evaporator 15, evaporation pressure control valve 20, and suction port of compressor 11.

Furthermore, the control device 60 appropriately determines the control signals to be output to the various controlled devices. For example, the control device 60 determines the control voltage to be output to the high-temperature side heat medium pump 41 so that the high-temperature side heat medium pump 41 exerts a predetermined pumping capacity. Furthermore, the control device 60 determines the control voltage to be output to the low-temperature side heat medium pump 51 so that the low-temperature side heat medium pump 51 is stopped.

As for the high-temperature side three-way valve 43, the control device 60 determines that the high-temperature side heat medium flowing out of the water-refrigerant heat exchanger 12a will flow into both the high-temperature side radiator 44 and the heater core 42 as shown by the solid arrows in FIG. 14. Furthermore, in the independent cooling mode, the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the heat medium flow rate flowing into the high-temperature side radiator 44 is greater than the heat medium flow rate flowing into the heater core 42.

The control signals, etc. to be output to the other controlled devices are determined in the same manner as in the independent cooling mode of the third embodiment. Then, the control device 60 outputs the control signals, etc. determined as described above to the various controlled devices.

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

In addition, 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 in 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 that flows into the high-temperature side radiator 44 exchanges heat with the outside air and releases heat to the outside air. The high-temperature side heat medium that flows into the heater core 42 exchanges heat with the blown air and releases heat depending on the opening degree of the air mix door 34.

In addition, 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 location in the vehicle cabin, as in the single cooling mode of the third embodiment. This achieves cooling of the vehicle cabin.

(a-2) Cooling/Cooling Mode In the cooling/cooling mode, the controller 60 controls the cooling expansion valve 14d to be in a throttled state, and the cooling expansion valve 14e to be in a throttled state.

Therefore, in the refrigeration cycle device 10c in the cooling/cooling mode, as shown by the black arrows in Figure 15, 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 14d, the indoor evaporator 15, the evaporation pressure adjustment valve 20, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant 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 adjustment valve 20, and the suction port of the compressor 11.

That is, in the refrigeration cycle device 10c in the cooling/air-conditioning mode, the indoor evaporator 15 and chiller 19 are switched to a refrigerant circuit connected in parallel to the refrigerant flow.

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

As for the high-temperature side three-way valve 43, the control device 60 determines that the high-temperature side heat medium flowing out of the water-refrigerant heat exchanger 12a will flow into both the high-temperature side radiator 44 and the heater core 42 as shown by the solid arrows in FIG. 15. Furthermore, in the cooling/cooling mode, the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the heat medium flow rate flowing into the high-temperature side radiator 44 is greater than the heat medium flow rate flowing into the heater core 42.

In addition, the control device 60 determines the control voltage output to the low-temperature side heat medium pump 51 so that the low-temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Furthermore, for the low-temperature side three-way valve 53, the control device 60 determines that the low-temperature side heat medium flowing out of the chiller 19 will form a heat medium circuit that flows into the cooling water passage 80a of the battery 80, as shown by the dashed arrow in Figure 15.

The control signals etc. to be output to the other controlled devices are determined in the same manner as in the cooling/air-conditioning mode of the third embodiment. Then, the control device 60 outputs the control signals etc. determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10c in the cooling/cooling mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and chiller 19 function as evaporators to configure a vapor compression refrigeration cycle. In the refrigeration cycle device 10c in the single cooling mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. The blown air is cooled in the indoor evaporator 15. The low-temperature side heat medium is cooled in the chiller 19.

In addition, 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 in 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 that flows into the high-temperature side radiator 44 exchanges heat with the outside air and dissipates heat to the outside air.

In addition, in the low-temperature side heat medium circuit 50a in the cooling/air-conditioning 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 in the chiller 19 flows into the cooling water passage 80a of the battery 80. The low-temperature side heat medium that flows into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. This cools the battery 80.

In addition, in the interior air conditioning unit 30 in the cooling/cooling mode, the temperature of the blown air is adjusted and blown out to an appropriate location in the vehicle cabin, as in the cooling/cooling mode of the third embodiment. This achieves cooling of the vehicle cabin.

(b-1) Single dehumidifying and heating mode In the adsorption stroke of the single dehumidifying and heating mode, the control device 60 throttles the cooling expansion valve 14d and the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10c in the adsorption stroke of the single dehumidifying and heating mode, as shown by the black arrows in Fig. 16, the refrigeration cycle device 10c is switched to a refrigerant circuit in which the refrigerant circulates, similar to the cooling and cooling mode.

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

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

In addition, the control device 60 determines the control voltage output to the low-temperature side heat medium pump 51 so that the low-temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Furthermore, with regard to the low-temperature side three-way valve 53, the control device 60 controls the operation of 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, as shown by the dashed arrow in FIG. 16.

The control signals etc. to be output to the other controlled devices are determined in the same manner as in the adsorption process of the single dehumidification and heating mode of the third embodiment. Then, the control device 60 outputs the control signals etc. determined as described above to the various controlled devices.

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

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

The other refrigerant branched off at the fourth three-way joint 17d is depressurized by the cooling expansion valve 14e (point b21 to point c21 in FIG. 21) and flows into the chiller 19. The refrigerant that flows into the chiller 19 exchanges heat with the low-temperature heat medium and evaporates (point c21 to 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 adjustment valve 20 and merge at the merging point 17g. The refrigerant flowing out of the merging point 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 Figure 21).

In other words, in the refrigeration cycle device 10c in the adsorption process of the single dehumidification heating mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and chiller 19 function as evaporators to configure a vapor compression refrigeration cycle. Note that, although FIG. 21 illustrates 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 may be lower than the refrigerant pressure in the chiller 19.

In the refrigeration cycle device 10c in the adsorption process of the single dehumidification heating mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. The blown air is cooled in the indoor evaporator 15. The low-temperature side heat medium is cooled in 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.

In addition, in the high-temperature side heat medium circuit 40a during the adsorption process in the single dehumidification 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the low-temperature side heat medium circuit 50a during the adsorption process in the single dehumidification 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 in the chiller 19 flows into the low-temperature side radiator 54. The low-temperature side heat medium that flows into the low-temperature side radiator 54 exchanges heat with the outside air and absorbs heat from the outside air.

In addition, in the interior air conditioning unit 30 during the adsorption process in the single dehumidification heating mode, the temperature of the blown air is adjusted and blown out to an appropriate location in the passenger compartment, as in the adsorption process in the single dehumidification heating mode of the second embodiment, as shown diagrammatically by the dashed arrow in the Mollier diagram of FIG. 21. Therefore, in the vehicle air conditioning device 1c during the adsorption process in the single dehumidification heating mode, the adsorption action of the desiccant material 15a can be used to dehumidify and heat the passenger compartment, as in the second embodiment.

Next, in the desorption process of the single dehumidification and heating mode, the control device 60 throttles the cooling expansion valve 14d and fully closes the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10c in the desorption process of the single dehumidification and heating mode, the refrigeration cycle device 10c is switched to a refrigerant circuit in which the refrigerant circulates, as shown by the white arrow in Figure 17.

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

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

In addition, 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 control signals etc. to be output to the other controlled devices are determined in the same manner as in the desorption process of the single dehumidification and heating mode of the second embodiment. The control device 60 then outputs the control signals etc. determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10c in the desorption process of the single dehumidification heating mode, as shown in the Mollier diagram of FIG. 22, the refrigerant discharged from the compressor 11 (point a22 in FIG. 22) flows into the water-refrigerant heat exchanger 12a. The refrigerant that flows into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and releases heat (point a22 → point b22 in FIG. 22).

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

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

In other words, in the refrigeration cycle device 10c in the desorption process of the single dehumidification 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 refrigeration cycle device 10c in the desorption process, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. Furthermore, in the refrigeration cycle device 10c in the desorption process, the high-temperature gas-phase refrigerant flows into the receiver 23, so that the receiver 23 functions as a refrigerant passage.

In addition, in the high-temperature side heat medium circuit 40a during the desorption process in the single dehumidification 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In the indoor air conditioning unit 30 during the desorption process in the single dehumidification heating mode, as shown by the dashed arrows in the Mollier diagram of FIG. 22, part of the outside air blown from the indoor blower 32 passes through the indoor evaporator 15 and is humidified, as in the second embodiment. This regenerates the desiccant material 15a. The outside air that has passed through the indoor evaporator 15 and been humidified is exhausted to the outside of the vehicle cabin from the exhaust port 31b of the exhaust device 38.

Another portion of the outside air blown from the interior blower 32 flows through the outside air bypass passage 35c and from the auxiliary outside air inlet 31a into the heating passage 35a. The outside air that flows into the heating passage 35a is heated by the heater core 42 as blown air and blown out into the passenger compartment. This allows the passenger compartment to be heated even during the desorption process in the single dehumidification heating mode.

(b-2) Cooling, dehumidifying and heating mode In the adsorption process of the cooling, dehumidifying and heating mode, the control device 60 throttles the cooling expansion valve 14d and the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10c in the adsorption process of the cooling, dehumidifying and heating mode, as shown by the black arrows in FIG. 18, the refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the cooling and air-conditioning mode.

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

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

In addition, the control device 60 determines the control voltage output to the low-temperature side heat medium pump 51 so that the low-temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Furthermore, with regard to the low-temperature side three-way valve 53, the control device 60 controls the operation of the low-temperature side three-way valve 53 so that the low-temperature side heat medium flowing out of the chiller 19 flows into both the low-temperature side radiator 54 and the cooling water passage 80a of the battery 80, as shown by the dashed arrows in FIG. 18.

If the heat of the battery 80 can be used to sufficiently reheat the blown air, the operation of the low-temperature side three-way valve 53 may be controlled so that the entire flow rate of the low-temperature side heat medium flowing out of the chiller 19 flows into the cooling water passage 80a of the battery 80.

The control signals etc. to be output to the other controlled devices are determined in the same manner as in the adsorption process of the cooling, dehumidifying and heating mode of the third embodiment. Then, the control device 60 outputs the control signals etc. determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10c in the adsorption process of the cooling, dehumidifying and heating mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and chiller 19 function as evaporators to form a vapor compression refrigeration cycle.

In the refrigeration cycle device 10c in the adsorption process of the cooling/dehumidifying/heating mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a, as in the adsorption process of the single dehumidifying/heating mode. The blown air is cooled in the indoor evaporator 15. The low-temperature side heat medium is cooled in 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.

In addition, in the high-temperature side heat medium circuit 40a during the adsorption process in 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the low-temperature side heat medium circuit 50a during the adsorption process in the cooling, dehumidifying, and 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 in the chiller 19 flows into the low-temperature side radiator 54 and the cooling water passage 80a of the battery 80.

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

In addition, in the interior air conditioning unit 30 during the adsorption process in the cooling, dehumidifying and heating mode, the temperature of the blown air is adjusted and blown out to an appropriate location in the vehicle cabin, just as in the adsorption process in the single dehumidifying and heating mode. Therefore, in the vehicle air conditioning device 1c during the adsorption process in the single dehumidifying and heating mode, the adsorption action of the desiccant material 15a can be used to dehumidify and heat the vehicle cabin.

Next, in the desorption process of the cooling, dehumidifying and heating mode, the control device 60 throttles the cooling expansion valve 14d and fully closes the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10c in the desorption process of the cooling, dehumidifying and heating mode, as shown by the white arrows in Figure 19, the refrigeration cycle device 10c switches to a refrigerant circuit in which the refrigerant circulates in the same order as in the single dehumidifying and heating mode.

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

In addition, with regard to the high-temperature side three-way valve 43, the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the water-refrigerant heat exchanger 12a flows into the heater core 42, as shown by the solid arrow in Figure 19.

In addition, the control device 60 determines the control voltage output to the low-temperature side heat medium pump 51 so that the low-temperature side heat medium pump 51 exerts a predetermined pumping capacity.

Furthermore, for the low-temperature side three-way valve 53, the control device 60 determines that the low-temperature side heat medium flowing out of the chiller 19 will form a heat medium circuit that flows into the cooling water passage 80a of the battery 80, as shown by the dashed arrow in FIG. 19.

Therefore, in the refrigeration cycle device 10c during the desorption process in the cooling/dehumidifying/heating mode, a hot gas cycle is formed in which the water-refrigerant heat exchanger 12a and the indoor evaporator 15 function as a radiator, just like in the desorption process in the single dehumidifying/heating mode. And, in the refrigeration cycle device 10a during the desorption process, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12c.

In addition, in the high-temperature side heat medium circuit 40a during the desorption process in 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 in the water-refrigerant heat exchanger 12a flows into the heater core 42.

In addition, in the low-temperature side heat medium circuit 50a during the desorption process in 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. Therefore, during the desorption process, the battery 80 can continue to be cooled by the low-temperature side heat medium cooled during the adsorption process, as in the second embodiment.

In addition, in the desorption process of the cooling, dehumidifying and heating mode, the desiccant material 15a of the interior evaporator 15 is regenerated in the interior air conditioning unit 30 in the same manner as in the desorption process of the single dehumidifying and heating mode. The outside air that is humidified while passing through the interior evaporator 15 is exhausted to the outside of the vehicle cabin through the exhaust port 31b of the exhaust device 38.

Furthermore, the outside air that flows into the heating passage 35a via the outside air bypass passage 35c is heated by heat exchange with the high-temperature heat medium heated in the water-refrigerant heat exchanger 12a as it passes through the heater core 42 as blown air, and is then blown into the passenger compartment. This allows the passenger compartment to be heated even during the desorption process in the cooling/dehumidifying/heating mode.

(c) Defrosting Mode In the vehicle air conditioner 1c, in the dehumidifying and heating mode, the low-temperature side radiator 54 heats the blown air using heat absorbed from the outside air by the low-temperature side heat medium as a heat source. For this reason, in the dehumidifying and heating mode, frost may form on the low-temperature side radiator 54. Therefore, in the defrosting mode of this embodiment, the low-temperature side radiator 54 is defrosted.

(c-1) Single defrost mode In the single defrost mode, the control device 60 throttles the cooling expansion valve 14d and fully closes the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10c in the single cooling mode, as shown by the white arrows in FIG. 14, the refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the single cooling mode.

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

As for the high-temperature side three-way valve 43, the control device 60 determines, as in the single cooling mode, that the high-temperature side heat medium flowing out of the water-refrigerant heat exchanger 12a forms a heat medium circuit in which it flows into both the high-temperature side radiator 44 and the heater core 42, as shown by the solid arrows in FIG. 14. Therefore, in the single defrost mode, the high-temperature side three-way valve 43, which is the heat distribution unit, increases the flow rate of the high-temperature side heat medium flowing into the high-temperature side radiator 44 more than in the single dehumidification heating mode.

As described above, in this embodiment, the high-temperature side radiator 44 and the low-temperature side radiator 54 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 defrost mode compared to the single dehumidification heating mode.

The control signals, etc. to be output to the other controlled devices are determined in the same manner as in the single defrost mode of the third embodiment. Then, the control device 60 outputs the control signals, etc. determined as described above to the various controlled devices.

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

The refrigerant flowing out of the water-refrigerant heat exchanger 12a is decompressed by the cooling expansion valve 14d (point b23 → point c23 in FIG. 23) and flows into the indoor evaporator 15. The refrigerant that flows into the indoor evaporator 15 exchanges heat with the blown air and evaporates (point d23 → point e23 in FIG. 23). The refrigerant that flows 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).

In other words, 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 vapor compression type refrigeration cycle. In the refrigeration cycle device 10c in the single cooling mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. The blown air is cooled in the indoor evaporator 15.

In addition, in the high-temperature side heat medium circuit 40a in the single defrost 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 in 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 flows into the high-temperature side radiator 44 is transferred to the integrated low-temperature side radiator 54. This causes the frost on the low-temperature side radiator 54 to melt and be removed. In other words, the low-temperature side radiator 54 is defrosted.

In addition, in the interior air conditioning unit 30 in the single defrost mode, as shown by the dashed arrows in the Mollier diagram in FIG. 23, the ventilation air that has been cooled and dehumidified in the interior evaporator 15 is reheated using the heat dissipated by the refrigerant in the water-refrigerant heat exchanger 12a as a heat source as it passes through the heater core 42. Therefore, dehumidification 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 throttles the cooling expansion valve 14d and throttles the cooling expansion valve 14e. Therefore, in the refrigeration cycle device 10c in the waste heat defrosting mode, as shown by the black arrows in FIG. 15, the refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the cooling/cooling mode.

Furthermore, the control device 60 appropriately determines the control signals to be output to the various controlled devices. For example, the control voltages to be output to the high-temperature side heat medium pump 41 and the low-temperature side heat medium pump 51 are determined in the same manner as in the cooling/air-conditioning mode.

As for the high-temperature side three-way valve 43, the control device 60 determines, as in the cooling/air-conditioning mode, that the high-temperature side heat medium flowing out of the water-refrigerant heat exchanger 12a forms a heat medium circuit in which it flows into both the high-temperature side radiator 44 and the heater core 42, as shown by the solid arrows in FIG. 15. Therefore, in the waste heat defrost mode, 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 more than in the cooling/dehumidification/heating mode.

Furthermore, for the low-temperature side three-way valve 53, the control device 60 determines that, as in the cooling/air-conditioning mode, the low-temperature side heat medium flowing out of the chiller 19 forms a heat medium circuit that flows into the cooling water passage 80a of the battery 80, as shown by the dashed arrow in FIG. 15.

The control signals, etc. to be output to the other controlled devices are determined in the same manner as in the waste heat defrosting mode of the third embodiment. Then, the control device 60 outputs the control signals, etc. determined as described above to the various controlled devices.

Therefore, in the refrigeration cycle device 10c in the waste heat defrost mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and chiller 19 function as evaporators to configure a vapor compression refrigeration cycle. In the refrigeration cycle device 10c in the single cooling mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a. The blown air is cooled in the indoor evaporator 15. The low-temperature side heat medium is cooled in the chiller 19.

In addition, in the high-temperature side heat medium circuit 40a in the waste heat defrost 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 in 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 flows into the high-temperature side radiator 44 is transferred to the integrated low-temperature side radiator 54. This causes the frost on the low-temperature side radiator 54 to melt and be removed. In other words, the low-temperature side radiator 54 is defrosted.

In addition, in the low-temperature side heat medium circuit 50a in the waste heat defrost 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 in the chiller 19 flows into the cooling water passage 80a of the battery 80. The low-temperature side heat medium that flows into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. This cools the battery 80.

In addition, in the interior air conditioning unit 30 in the single defrost mode, the dehumidification and heating of the vehicle interior can be continued by reheating the blown air that has been cooled and dehumidified by the interior evaporator 15 in the heater core 42, as in the waste heat defrost mode of the third embodiment.

As described above, the vehicle air conditioner 1c of this embodiment can achieve comfortable air conditioning in the vehicle cabin and proper cooling of heat-generating equipment by switching the operating mode.

Furthermore, in the vehicle air conditioner 1c of this embodiment, a desiccant material 15a is applied to the interior evaporator 15. Therefore, the operating efficiency can be improved to the same extent as in the vehicle air conditioner 1 of the first embodiment.

In addition, in the defrost mode, the flow rate of the high-temperature side heat medium that the high-temperature side three-way valve 43 causes to flow into the high-temperature side radiator 44 is increased compared to the dehumidification heating mode. In other words, in the defrost mode, the amount of heat supplied to the low-temperature side radiator 54 via the high-temperature side radiator 44 is increased compared to the dehumidification heating mode. Therefore, the frost on the low-temperature side radiator 54 can be melted and removed.

Furthermore, in the defrost 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 defrost mode, it can be reheated by the heater core 42. As a result, even if the rotation speed of the compressor 11 is determined so that the refrigeration oil can be appropriately returned to the compressor 11, the temperature drop in the air-conditioned space can be suppressed.

Therefore, the vehicle air conditioner 1c of this embodiment can provide the same effects as the vehicle air conditioner 1 described in the first embodiment. That is, the indoor evaporator 15 to which the desiccant material 15a is applied provides the effect of improving the operating efficiency, while allowing the refrigeration oil to be appropriately returned to the compressor 11 regardless of the operating mode.

In addition, the vehicle air conditioner 1c of this embodiment is equipped with a coolant passage 80a of the battery 80 as a heat medium device heat exchanger. This allows the battery 80 to be cooled.

Furthermore, in the waste heat dehumidification mode, the low-temperature side three-way valve 53 switches the low-temperature side heat medium circuit 50a so as to circulate the low-temperature side heat medium between the chiller 19 and the cooling water passage 80a of the battery 80. This makes it possible to use the waste heat of the battery 80 as a heat source for defrosting the exterior heat exchanger 16. (Other embodiments)
The present invention is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit of the present invention.

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

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

(2) The operating modes that the vehicle air conditioners 1 to 1c can execute are not limited to those described in the above embodiments. In the vehicle air conditioners 1 to 1c, the above-mentioned effects can be obtained as long as they can switch between at least the dehumidification heating mode and the defrosting mode described in each embodiment. In other words, the refrigeration oil can be appropriately returned to the compressor 11 while obtaining the effect of improving the operating efficiency by providing a heat exchanger having an adsorption section.

Therefore, the vehicle air conditioners 1 to 1c may be capable of executing a different operating mode. For example, the vehicle air conditioner 1a described in the second embodiment may execute a serial dehumidification heating mode as a different 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 throttled, and the cooling expansion valve 14d and the cooling expansion valve 14e are fully closed. The other components are controlled in the same way as in the dehumidifying and heating mode. Therefore, in the serial dehumidifying and heating mode, the refrigerant circuit is switched to one in which the outdoor heat exchanger 16 and the indoor evaporator 15 are connected in series to the refrigerant flow.

For example, the vehicle air conditioner 1a described in the second embodiment may further execute a heating mode. In the heating mode, heated air is blown into the vehicle cabin without cooling and dehumidifying the air in the interior 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. Furthermore, the heating expansion valve 14c is throttled, and the cooling expansion valve 14d and the cooling expansion valve 14e are fully closed. The other components can be controlled in the same way as in the cooling mode. In this way, the vehicle interior can be heated by blowing the blown air heated by the heater core 42 into the vehicle interior.

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. Furthermore, the heating expansion valve 14c is throttled, and the cooling expansion valve 14d and the cooling expansion valve 14e are fully closed. The other components may be controlled in the same way as in the cooling mode. In this way, the vehicle interior can be heated by blowing the blown air heated by the heater core 42 into the vehicle interior.

For example, the heating mode may be executed in the vehicle air conditioning device 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 throttled. The high-temperature side heat medium pump 41 and the low-temperature side heat medium pump 51 are operated to exert a predetermined pumping capacity. The high-temperature side three-way valve 43 is operated so that the high-temperature side heat medium flows into the heater core 42. 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.

This allows the interior of the vehicle to be heated by blowing the air heated by the heater core 42 into the vehicle cabin.

In addition, in the vehicle air conditioners 1a to 1c described in the second to fourth embodiments, defrosting may be performed using only waste heat from heat-generating equipment as a heat source. Specifically, the cooling expansion valve 14d may be fully closed during the waste heat defrosting mode.

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

For example, when the dehumidifying heating mode is being executed, it may be determined that the frosting condition is met when the time Tmf2 during which the outdoor air temperature Tam is continuously below the reference frosting outdoor air temperature Ktamf becomes equal to or greater than the reference frosting time KTmf. For example, when the defrosting mode is being executed, it may be determined that the termination condition is met when the outdoor unit temperature Tout becomes equal to or greater than a predetermined reference defrosting temperature KToutdf.

For example, when the low-temperature side heat medium temperature TWL detected by the low-temperature side heat medium temperature sensor 61m is equal to or higher than a predetermined reference heat medium temperature KTWL during execution of each operating mode, it may be determined that cooling of the battery 80 is necessary. Also, when the low-temperature side heat medium temperature TWL is lower than the reference heat medium temperature KTWL, it may be determined that cooling of the battery 80 is not necessary.

For example, in the dehumidification heating mode, the control signal output to the compressor 11 may be 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.

(4) The configurations of the refrigeration cycle devices 10, 10a to 10c are not limited to those disclosed in the above embodiments.

In the refrigeration cycle device 10, an example has been described in which a four-way valve 13 is used as the refrigerant circuit switching unit, but this is not limiting. For example, the refrigerant circuit switching unit may be formed by combining multiple (e.g., four) on-off valves.

In the refrigeration cycle devices 10a to 10c, an example has been described in which the evaporation pressure adjustment valve 20 is used as the pressure adjustment unit, but this is not limiting. For example, a mechanical evaporation pressure adjustment valve that maintains the refrigerant at or above the evaporation pressure of the refrigerant in the indoor evaporator 15 may be disposed in the refrigerant flow path from the refrigerant outlet of the indoor evaporator 15 to the junction 17g. As the mechanical evaporation pressure adjustment valve, a variable throttle mechanism that increases the valve opening as the refrigerant pressure on the refrigerant outlet side of the indoor evaporator 15 increases can be used.

In the above embodiment, an example in which R1234yf is used as the refrigerant has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be used. Alternatively, a mixed refrigerant in which a plurality of these refrigerants are mixed may be used.
(5) The configuration of the indoor air conditioning unit 30 is not limited to that disclosed in the above embodiment. For example, an inside air dedicated passage through which only inside air flows and an outside air dedicated passage through which only outside air flows may be formed in the casing 31. A heating passage and a cold air bypass passage may be formed in both the inside air dedicated passage and the outside air dedicated passage.

In the above embodiment, the adsorption process in the dehumidifying heating mode is described as an example in which the operation of the inside/outside air switching device 33 is controlled so that the inside air inlet is fully open and the outside air inlet is fully closed, but the present invention is not limited to this. In the adsorption process, the operation of the inside/outside air switching device 33 may be controlled so that the proportion of inside air in the blown air flowing into the indoor evaporator 15 is greater than the proportion of outside air.

Similarly, in the desorption process of the dehumidifying heating mode, an example has been described in which the operation of the inside/outside air switching device 33 is controlled so that the inside air inlet is fully closed and the outside air inlet is fully open, but this is not limiting. In the desorption process, the operation of the inside/outside air switching device 33 may be controlled so that the proportion of outside air in the blown air flowing into the indoor evaporator 15 is greater than the proportion of inside air.

In addition, in the cooling mode and defrost mode, an example has been described in which the operation of the inside/outside air switching device 33 is controlled so that the inside air inlet is fully closed and the outside air inlet is fully open, but this is not limiting. In the cooling mode and defrost mode, the operation of the inside/outside air switching device 33 may be controlled so that the proportion of outside air in the blown air flowing into the indoor evaporator 15 is greater than the proportion of inside air.

In the above embodiment, an example in which the outside air bypass passage 35c is provided has been described, but the outside air bypass passage 35c may be eliminated and outside air may be introduced directly from the auxiliary outside air inlet 31a. In this case, it is desirable to provide a dedicated auxiliary outside air blower for directing outside air into the auxiliary outside air inlet 31a. Then, when the control device 60 opens the auxiliary outside air inlet 31a, it is sufficient to operate the auxiliary outside air blower.

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

In addition, a bypass passage may be provided in the high-temperature side heat medium circuit 40 to allow the high-temperature side heat medium to flow around the heater core 42, and a three-way valve may be disposed to adjust the flow rate ratio between 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. The three-way valve may then be used as a heat amount adjustment unit.

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

(7) Furthermore, the means disclosed in each of the above embodiments may be combined as appropriate to the extent feasible.

For example, the water-refrigerant heat exchanger 12a and the components of the high-temperature side heat medium circuit 40 may be used as the heating section of the vehicle air conditioner 1 described in the first embodiment. Similarly, the interior condenser 12 may be used as the heating section of the vehicle air conditioners 1a and 1b described in the second and third embodiments.

1 to 1c...vehicle air conditioning device, 10 to 10c...refrigeration cycle device, 11...compressor,
12: Indoor condenser (heating unit), 12a: Water-refrigerant heat exchanger (heating unit),
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 unit),
14a...first expansion valve (first pressure reducing section), 14b...second expansion valve (second pressure reducing section),
14c...Heating expansion valve (outdoor pressure reduction section), 14d...Cooling expansion valve (cooling pressure reduction section),
14e...cooling expansion valve (cooling pressure reducing section),
15: indoor evaporator (cooling heat exchange section), 15a: desiccant material (adsorption section),
16...Outdoor heat exchanger (outdoor heat exchange part),
17a, 17d... first and fourth three-way joints (branching parts), 17g... junction part 19... chiller (cooling heat exchange part), 20... evaporation pressure regulating valve (pressure regulating part),
40, 40a...High temperature side heat medium circuit (heating part), 50, 50a...Low temperature side heat medium circuit

Claims (7)

An air conditioning device applied to a vehicle,
A compressor (11) that compresses and discharges a refrigerant mixed with refrigeration oil;
A heating unit (12, 12a, 40) that heats air to be blown to a space to be air-conditioned using the refrigerant discharged from the compressor as a heat source;
a first pressure reducing section (14a) and a second pressure reducing section (14b) for reducing the pressure of the refrigerant;
an air cooling heat exchange section (15) that evaporates the refrigerant and cools the blown air before it is heated by the heating section;
an outdoor heat exchange section (16) for exchanging heat between the refrigerant and outside air;
a refrigerant circuit switching unit (13) that switches a refrigerant circuit through which the refrigerant circulates;
an inside/outside air ratio adjustment unit (33) for adjusting the ratio of outside air and inside air in the blown air flowing into the air cooling heat exchange unit;
an exhaust section (38) that exhausts the blown air that has passed through the air-cooling heat exchange section to the outside of the space to be air-conditioned;
An auxiliary outside air introduction section (37) that introduces outside air into the heating section,
The air-cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air,
the inside/outside air ratio adjustment unit is disposed on the upstream side of the blown air flow of a heating passage (35a) through which the blown air that has passed through the air-cooling heat exchange unit passes through the heating unit, a cold air bypass passage (35b) through which the blown air that has passed through the air-cooling heat exchange unit flows, bypassing the heating unit, and an outside air bypass passage (35c) through which the blown air that has flowed in from the inside/outside air ratio adjustment unit flows, bypassing the air-cooling heat exchange unit;
The exhaust unit is configured to exhaust the entire amount of the blown air that has flowed through the cold air bypass passage to outside the target space to be air-conditioned,
the refrigerant circuit switching unit switches to a refrigerant circuit that circulates the refrigerant discharged from the compressor through the heating unit, the first decompression unit, the air-cooling heat exchange unit, the outdoor heat exchange unit, and the suction side of the compressor in this order during a dehumidification heating mode in which the air-conditioned space is dehumidified and heated;
the refrigerant circuit switching unit switches to a refrigerant circuit that circulates the refrigerant discharged from the compressor in the order of the heating unit, the outdoor heat exchange unit, the second pressure reducing unit, the air cooling heat exchange unit, and the suction side of the compressor during a defrosting mode in which frost on the outdoor heat exchange unit is removed;
In the adsorption process in which the adsorption unit adsorbs the moisture in the dehumidifying and heating mode, the inside/outside air ratio adjustment unit causes the inside air to flow into the air-cooling heat exchange unit,
In the adsorption process, the blown air that has passed through the air-cooling heat exchange section is blown to the space to be air-conditioned via the heating passage and the cold air bypass passage;
In the desorption process in which the moisture is desorbed from the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes outside air to flow into the air-cooling heat exchange section,
In the desorption process, the exhaust section exhausts the entire amount of the blown air that has passed through the air-cooling heat exchange section to the outside of the air-conditioned space via the cold air bypass passage without flowing the entire amount of the blown air into the air-conditioned space,
In the desorption process, the auxiliary outside air introduction section introduces outside air into the heating section via the outside air bypass passage , and the blown air heated by the heating section is blown into the space to be air-conditioned. An air conditioning device applied to a vehicle,
A compressor (11) that compresses and discharges a refrigerant mixed with refrigeration oil;
A heating unit (12, 12a, 40) that heats air to be blown to a space to be air-conditioned using the refrigerant discharged from the compressor as a heat source;
a branching section (17a) for branching the flow of the refrigerant flowing out from the heating section;
an outdoor pressure reduction section (14c) and a cooling pressure reduction section (14d, 14e) for reducing the pressure of the refrigerant;
an outdoor heat exchange section (16) for exchanging heat between the refrigerant decompressed in the outdoor pressure reduction section and outside air;
a cooling heat exchange section (15, 19, 50) for evaporating the refrigerant decompressed in the cooling decompression section in order to cool an object to be cooled;
a confluence section (17g) for confluence of the refrigerant flowing out from the cooling heat exchange section and the refrigerant flowing out from the outdoor heat exchange section and for discharging the refrigerant to the suction side of the compressor;
a refrigerant circuit switching unit (13a...13d) that switches a refrigerant circuit through which the refrigerant circulates,
The cooling heat exchange unit has an air cooling heat exchange unit (15) for cooling the blown air before it is 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 pressure reducing section has an air cooling pressure reducing section (14d) that reduces the pressure of the refrigerant flowing into the air cooling heat exchange section,
Furthermore, an inside/outside air ratio adjustment unit (33) that adjusts the ratio of outside air and inside air in the blown air flowing into the air cooling heat exchange unit;
an exhaust section (38) that exhausts the blown air that has passed through the air-cooling heat exchange section to the outside of the space to be air-conditioned;
An auxiliary outside air introduction section (37) that introduces outside air into the heating section,
the inside/outside air ratio adjustment unit is disposed on the upstream side of the blown air flow of a heating passage (35a) through which the blown air that has passed through the air-cooling heat exchange unit passes through the heating unit, a cold air bypass passage (35b) through which the blown air that has passed through the air-cooling heat exchange unit flows, bypassing the heating unit, and an outside air bypass passage (35c) through which the blown air that has flowed in from the inside/outside air ratio adjustment unit flows, bypassing the air-cooling heat exchange unit;
The exhaust unit is configured to exhaust the entire amount of the blown air that has flowed through the cold air bypass passage to outside the target space to be air-conditioned,
the refrigerant circuit switching unit, during a dehumidification heating mode in which the air-conditioned space is dehumidified and heated, circulates the refrigerant discharged from the compressor in the order of the heating unit, the branching unit, the outdoor pressure reduction unit, the outdoor heat exchange unit, the junction unit, and the suction side of the compressor, and switches to a refrigerant circuit in which the refrigerant discharged from the compressor is circulated in the order of the heating unit, the branching unit, the air-cooling pressure reduction unit, the air-cooling heat exchange unit, the junction unit, and the suction side of the compressor;
the refrigerant circuit switching unit switches to a refrigerant circuit that circulates the refrigerant discharged from the compressor in the order of the heating unit, the outdoor heat exchange unit, the cooling decompression unit, the cooling heat exchange unit, and the suction side of the compressor during a defrosting mode in which frost on the outdoor heat exchange unit is removed;
In the adsorption process in which the adsorption unit adsorbs the moisture in the dehumidifying and heating mode, the inside/outside air ratio adjustment unit causes the inside air to flow into the air-cooling heat exchange unit,
In the adsorption process, the blown air that has passed through the air-cooling heat exchange section is blown to the space to be air-conditioned via the heating passage and the cold air bypass passage;
In the desorption process in which the moisture is desorbed from the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes outside air to flow into the air-cooling heat exchange section,
In the desorption process, the exhaust section exhausts the entire amount of the blown air that has passed through the air-cooling heat exchange section to the outside of the air-conditioned space via the cold air bypass passage without flowing the entire amount of the blown air into the air-conditioned space,
In the desorption process, the auxiliary outside air introduction section introduces outside air into the heating section via the outside air bypass passage , and the blown air heated by the heating section is blown into the space to be air-conditioned. The cooling heat exchanger has a heat medium cooling heat exchanger (19) for cooling a heat generating device (80) that generates heat during operation,
The cooling pressure reducing section has a heat medium cooling pressure reducing section (14e) that reduces the pressure of the refrigerant flowing into the heat medium cooling heat exchange section,
The refrigerant circuit switching unit is
The air conditioner according to claim 2 , wherein, in the defrosting mode, the refrigerant circuit is switched to one in which the refrigerant flowing out of the outdoor heat exchange section flows into the heat medium cooling pressure reducing section. An air conditioning device applied to a vehicle,
A compressor (11) that compresses and discharges a refrigerant mixed with refrigeration oil;
A heating unit (12a, 40a) that heats air to be blown to a space to be air-conditioned using the refrigerant discharged from the compressor as a heat source;
A branching portion (17d) for branching the flow of the refrigerant flowing out from the heating portion;
an air cooling pressure reducing section (14d) for reducing the pressure of one of the refrigerants branched at the branch section;
an air-cooling heat exchange section (15) that evaporates the refrigerant decompressed in the air-cooling decompression section to cool the blown air before it is heated in the heating section;
a low-temperature side heat medium circuit (50a) for circulating a low-temperature side heat medium;
a heat medium cooling pressure reducing section (14e) for reducing the pressure of the other of the refrigerants branched off at the branch section;
a heat exchange section for cooling a heat medium for exchanging heat between the refrigerant decompressed in the heat medium cooling decompression section and the low-temperature side heat medium;
a confluence section (17g) for confluence of the refrigerant flowing out of the air-cooling heat exchange section and the refrigerant flowing out of the heat medium-cooling heat exchange section and allowing the refrigerant to flow out to a suction side of the compressor;
a low-temperature side outside air heat exchange section (54) disposed in the low-temperature side heat medium circuit for exchanging heat between the low-temperature side heat medium and outside air;
a heat quantity distribution section (43) that distributes a heat quantity of the refrigerant discharged from the compressor between the heating section and the low-temperature side outside air heat exchange section;
an inside/outside air ratio adjustment unit (33) for adjusting the ratio of outside air and inside air in the blown air flowing into the air cooling heat exchange unit;
an exhaust section (38) that exhausts the blown air that has passed through the air-cooling heat exchange section to the outside of the space to be air-conditioned;
An auxiliary outside air introduction section (37) that introduces outside air into the heating section,
The air-cooling heat exchange unit has an adsorption unit (15a) that adsorbs moisture contained in the blown air,
the inside/outside air ratio adjustment unit is disposed on the upstream side of the blown air flow of a heating passage (35a) through which the blown air that has passed through the air-cooling heat exchange unit passes through the heating unit, a cold air bypass passage (35b) through which the blown air that has passed through the air-cooling heat exchange unit flows, bypassing the heating unit, and an outside air bypass passage (35c) through which the blown air that has flowed in from the inside/outside air ratio adjustment unit flows, bypassing the air-cooling heat exchange unit;
The exhaust unit is configured to exhaust the entire amount of the blown air that has flowed through the cold air bypass passage to outside the target space to be air-conditioned,
The heat distribution unit supplies heat of the refrigerant discharged from the compressor to the heating unit during a dehumidification heating mode in which the air-conditioned space is dehumidified and heated,
the heat quantity distribution unit increases the amount of heat supplied to the low-temperature side outdoor air heat exchange unit in a defrosting mode for removing frost on the low-temperature side outdoor air heat exchange unit compared to the dehumidification heating mode,
In the adsorption process in which the adsorption unit adsorbs the moisture in the dehumidifying and heating mode, the inside/outside air ratio adjustment unit causes the inside air to flow into the air-cooling heat exchange unit,
In the adsorption process, the blown air that has passed through the air-cooling heat exchange section is blown to the space to be air-conditioned via the heating passage and the cold air bypass passage;
In the desorption process in which the moisture is desorbed from the adsorption section in the dehumidifying and heating mode, the inside/outside air ratio adjustment section causes outside air to flow into the air-cooling heat exchange section,
In the desorption process, the exhaust section exhausts the entire amount of the blown air that has passed through the air-cooling heat exchange section to the outside of the air-conditioned space via the cold air bypass passage without flowing the entire amount of the blown air into the air-conditioned space,
In the desorption process, the auxiliary outside air introduction section introduces outside air into the heating section via the outside air bypass passage , and the blown air heated by the heating section is blown into the space to be air-conditioned. a heat medium equipment heat exchanger (80a) disposed in the low-temperature side heat medium circuit and exchanging heat between the low-temperature side heat medium and a heat generating equipment (80) that generates heat during operation;
a low-temperature side circuit switching unit (53) that switches the circuit configuration of the low-temperature side heat medium circuit,
The air conditioning apparatus according to claim 4 , wherein the low-temperature side circuit switching unit switches the 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 during the defrosting mode. the heating section includes a high-temperature side heat medium circuit (40a) for circulating a high-temperature side heat medium, a heat medium heating heat exchange section (12a) for exchanging heat between the high-temperature side heat medium and a refrigerant discharged from the compressor, and an air heating heat exchange section (42) for exchanging heat between the high-temperature side heat medium and the blown air,
6. The air conditioning apparatus according to claim 4, wherein the heat distribution section adjusts 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 outdoor air heat exchange section. A heating amount adjustment unit (34, 41) is provided to adjust the heating amount of the blown air in the heating unit,
7. The air conditioner according to claim 1, wherein the heat amount adjustment unit reduces the heat amount in the defrosting mode compared to the dehumidifying and heating mode.

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