Air conditioning device

Abstract

To provide an air conditioner which can return refrigerator oil to a compressor adequately while obtaining improvement effect of actuation efficiency by being provided with a heat exchange part including a suction part.SOLUTION: A refrigerant circuit of a refrigeration cycle device 10 is switched so as to circulate coolant discharged from a compressor 11 in order of indoor evaporator 12, a first expansion valve 14a, an indoor evaporator 15 including a desiccant material 15a, an outdoor heat exchanger 16 and a suction side of the compressor in a dehumidification heating mode of an air conditioner 1 for a vehicle. Blowing air is dehumidified by utilizing adsorptive action of the desiccant material 15a in the dehumidification heating mode. The refrigerant circuit of the refrigeration cycle device 10 is switched so as to circulate the coolant discharged from the compressor 11 in order of indoor evaporator 12, the outdoor heat exchanger 16, a second expansion valve 14b, the indoor evaporator 15 and the suction side of the compressor in a defrost mode. The blowing air is reheated at the indoor condenser 12 in the defrost mode.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to an air conditioner equipped with a heat exchanger having an adsorption portion. [Background technology]

[0002] Conventionally, a vehicle air conditioner applied to an electric vehicle is disclosed in Patent Document 1. The vehicle air conditioner of 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.

[0003] The refrigeration cycle device of Patent Document 1 includes a plurality of heat exchangers and is configured to be able to switch the refrigerant circuit according to the operation mode. For example, in a dehumidification and heating mode for dehumidifying and heating 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.

[0004] As a result, in the vehicle air conditioning system of Patent Document 1, the blown 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 achieving dehumidification and heating of the vehicle cabin.

[0005] Furthermore, the vehicle air conditioner of Patent Document 1 employs a heat exchanger (specifically, a heat exchanger with an outer surface coated with a desiccant material) having an adsorption section that adsorbs moisture contained in the blown air as a heat exchanger for adjusting humidity. 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 adjusting humidity, and the moisture contained in the blown air is adsorbed by the adsorption section.

[0006] As a result, in the vehicle air conditioner of Patent Document 1, in the dehumidification heating mode, the energy consumed for dehumidifying the blown air is reduced, improving the operating efficiency.

[0007] Patent Document 2 discloses an air conditioning system having a refrigeration cycle device. The refrigeration cycle device of Patent Document 2 includes an indoor heat exchanger and an outdoor heat exchanger, and is configured to be able to switch a refrigerant circuit depending on an operation mode. Furthermore, the air conditioning system of Patent Document 2 employs a heat exchanger having an adsorption unit similar to that of Patent Document 1 as the indoor heat exchanger.

[0008] 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 for heating the room, and switches to a refrigerant circuit in which the outdoor heat exchanger functions as a condenser and the indoor heat exchanger functions as an evaporator during a defrost mode for removing frost on the outdoor heat exchanger.

[0009] Furthermore, in the air conditioning system of Patent Document 2, during 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.

[0010] In this way, the air conditioning system of Patent Document 2 is intended to suppress a drop in temperature in the space to be air conditioned when switching from the heating mode to the defrosting mode. [Prior art documents] [Patent documents]

[0011] [Patent Document 1] JP 2018-176936 A [Patent Document 2] JP 2019-66090 A Summary of the Invention [Problem to be solved by the invention]

[0012] Incidentally, in the vehicle air conditioner of Patent Document 1, frost may occur on the exterior heat exchanger that functions as an evaporator in the dehumidification heating mode. Therefore, in the vehicle air conditioner of Patent Document 1, it is considered to operate in a defrosting mode similar to the air conditioning system of Patent Document 2.

[0013] 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 temperature drop 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 part of the indoor heat exchanger as a heat source.

[0014] In order to suppress the temperature drop in the air-conditioned space after switching from the dehumidifying and heating mode to the defrosting 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 rotation speed of the compressor after switching from the dehumidifying and heating mode to the defrosting mode.

[0015] However, the required refrigerant flow rate required to circulate the cycle in the defrost mode is smaller than that in the dehumidification heating mode. Therefore, if the rotation speed of the compressor of the refrigeration cycle device is reduced in the defrost mode in order to suppress the drop in temperature of the blown air after switching from the dehumidification heating mode to the defrost mode, there is a possibility that the refrigeration oil mixed in the refrigerant cannot be returned to the compressor.

[0016] In other words, in the vehicle air conditioner of Patent Document 1, in the dehumidification heating mode, the operating efficiency can be improved by the adsorption action of the adsorption unit, but when the vehicle air conditioner is operated in the defrost mode, the refrigeration oil cannot be appropriately returned to the compressor, which may adversely affect the durability and life of the compressor.

[0017] In view of the above, an object of the present invention is to provide an air conditioner that can appropriately return refrigeration oil to the compressor while obtaining the effect of improving operating efficiency by being provided with a heat exchange section having an adsorption section. [Means for solving the problem]

[0018] In order to achieve the above object, the air conditioner according to claim 1 comprises: An air conditioning device applied to a vehicle, The refrigerant coolant system 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).

[0019] The compressor compresses and discharges a refrigerant mixed with refrigeration oil. The heating unit uses the refrigerant discharged from the compressor as a heat source to heat the air to be blown into the space to be air-conditioned. The first and second pressure reduction units reduce the pressure of the refrigerant. The air cooling heat exchange unit evaporates the refrigerant to cool the air to be blown before it is heated by the heating unit. The outdoor heat exchange unit exchanges heat between the refrigerant and outside air. The refrigerant circuit switching unit switches the refrigerant circuit that circulates the refrigerant. The inside / outside air ratio adjustment section (33) adjusts the ratio of outside air to 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.

[0020] The air-cooling heat exchange section 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 flow of blown air in 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 exchange section and passes through the heating section. The cold air bypass passage is an air passage that passes through the air-cooling heat exchange section and bypasses 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 bypasses the air-cooling heat exchange section. The exhaust section is configured to be able to exhaust the entire volume of blown air that has flowed through the cold air bypass passage to outside the space to be air-conditioned.

[0021] 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 reducing 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 refrigerant is dehumidified and heated in the air-conditioned space. The refrigerant circuit switching unit includes: During defrost mode, which removes frost that has built up on the outdoor heat exchange section, the refrigerant discharged from the compressor is switched to a refrigerant circuit that circulates the refrigerant discharged from the compressor in the following order: heating section, outdoor heat exchange section, second pressure reduction section, air-cooling heat exchange section, and the suction side of the compressor. In the adsorption process in which moisture is adsorbed into the adsorption section in the dehumidifying heating mode, the inside / outside air ratio adjustment section Allowing internal air to flow inIn the desorption process in which moisture is desorbed from the adsorption section in the dehumidifying heating mode, the inside / outside air ratio adjustment section transfers the moisture to the air cooling heat exchange section. Let outside air in In the desorption process, the exhaust gas passes through an air-cooling heat exchanger. Total airflow Blow air , through the cold air bypass passage without flowing into the space to be air-conditioned The air is exhausted outside the space to be air-conditioned. In the desorption process, the auxiliary outside air intake section: Through the outside air bypass passage Outside air is introduced into the heating section, and the air heated by the heating section is sent to the space to be air-conditioned.

[0022] According to this, 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.

[0023] The blown air cooled and dehumidified in the air-cooling heat exchange section (15) is reheated in the heating section (12, 12a, 40) and blown into the space to be air-conditioned, thereby dehumidifying and heating the space to be air-conditioned.

[0024] 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 utilized 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 conditioner as a whole can be improved.

[0025] 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) function as a condenser, and the air-cooling heat exchange unit (15) functions as an evaporator. Thus, the frost on the outdoor heat exchange unit (16) can be melted and removed.

[0026] Furthermore, in the defrost mode, 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) in 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 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.

[0027] In other words, according to the air conditioner of claim 1, it is possible to obtain the effect of improving the operating efficiency by providing the air-cooling heat exchange section (15) having the adsorption section (15a), while appropriately returning refrigeration oil to the compressor (11).

[0028] The air conditioner according to claim 2 is An air conditioning device applied to a vehicle, The refrigerant coolant ...

[0029] The compressor compresses and discharges a refrigerant mixed with refrigeration oil. The heating section uses the refrigerant discharged from the compressor as a heat source to heat the air to be blown into the space to be air-conditioned. The branching section branches the flow of the refrigerant flowing out from the heating section. The outdoor pressure reduction section and the cooling pressure reduction section reduce the pressure of the refrigerant. The outdoor heat exchange section exchanges heat between the refrigerant reduced in pressure by the outdoor pressure reduction section and outside air. The cooling heat exchange section evaporates the refrigerant reduced in pressure by the cooling pressure reduction section in order to cool the object to be cooled. . If The flow section merges the refrigerant flowing out from the cooling heat exchange section and the refrigerant flowing out from the outdoor heat exchange section, and causes the refrigerant to flow to the suction side of the compressor. The refrigerant circuit switching section switches the refrigerant circuit that circulates the refrigerant.

[0030] 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 includes an inside / outside air ratio adjustment section (33), an exhaust section (38), and an auxiliary outside air introduction section (37). The inside / outside air ratio adjustment section (33) adjusts the ratio of outside air to 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 adjustment section is disposed upstream of the flow of blown air in 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 exchange section and passes through the heating section. The cold air bypass passage is an air passage that passes through the air-cooling heat exchange section and bypasses 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 bypasses the air-cooling heat exchange section. The exhaust section is configured to be able to exhaust the entire volume of blown air that has flowed through the cold air bypass passage to outside the space to be air-conditioned.

[0031] In a dehumidification heating mode in which the air-conditioned space is dehumidified and heated, the refrigerant circuit switching unit circulates the refrigerant discharged from the compressor through the heating unit, branching unit, air cooling pressure reduction unit, air cooling heat exchange unit, junction unit, and the suction side of the compressor in that order. At the same time, the refrigerant circuit switching unit switches the refrigerant discharged from the compressor to the heating unit, branching unit, outdoor pressure reduction unit, outdoor heat exchange unit, junction unit, and the suction side of the compressor in that order. The refrigerant circuit switching unit includes: During a defrosting mode for removing frost on the outdoor heat exchanger, the refrigerant discharged from the compressor is switched to a refrigerant circuit that circulates the refrigerant through the heating section, the outdoor heat exchanger, the cooling pressure reduction section, the cooling heat exchanger, and the suction side of the compressor in that order. In the adsorption process in which moisture is adsorbed into the adsorption section in the dehumidifying heating mode, the inside / outside air ratio adjustment section Allowing internal air to flow in In the desorption process in which moisture is desorbed from the adsorption section in the dehumidifying heating mode, the inside / outside air ratio adjustment section transfers the moisture to the air cooling heat exchange section. Let outside air in In the desorption process, the exhaust gas passes through an air-cooling heat exchanger. Total airflow Blow air , through the cold air bypass passage without flowing into the space to be air-conditioned The air is exhausted outside the space to be air-conditioned. In the desorption process, the auxiliary outside air intake section: Through the outside air bypass passage Outside air is introduced into the heating section, and the air heated by the heating section is sent to the space to be air-conditioned.

[0032] According to this, when the refrigerant circuit switching unit (13a...13d) switches to the refrigerant circuit of 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.

[0033] The blown air cooled and dehumidified in the air-cooling heat exchange section (15) is reheated in the heating section (12, 12a, 40) and blown into the space to be air-conditioned, thereby dehumidifying and heating the space to be air-conditioned.

[0034] 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 utilized 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 conditioner as a whole can be improved.

[0035] When the refrigerant circuit switching units (13a...13d) switch to the defrost mode refrigerant circuit, the heating units (12, 12a, 40) and the outdoor heat exchange unit (16) function as condensers, and the cooling heat exchange unit (15, 19) function as an evaporator. Thus, the frost on the outdoor heat exchange unit (16) can be melted and removed.

[0036] Furthermore, in the defrost mode, 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) in 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 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.

[0037] In other words, according to the air conditioner of claim 2, it is possible to obtain the effect of improving the operating efficiency by providing the air-cooling heat exchange section (15) having the adsorption section (15a), while appropriately returning refrigeration oil to the compressor (11).

[0038] The air conditioner according to claim 4 further comprises: An air conditioning device applied to a vehicle, The refrigerant coolant system 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 distribution section (43), an inside / outside air ratio adjustment section (33), an exhaust section (38), and an auxiliary outside air introduction section (37).

[0039] 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 air cooling decompression unit is a unit that divides one of the refrigerant branches at the branching unit. The air cooling heat exchange section evaporates the refrigerant depressurized in the air cooling depressurization section to cool the blown air before it is heated in the heating section. The low-temperature side heat medium circuit circulates the low-temperature side heat medium. The heat medium cooling depressurization section depressurizes the other refrigerant branched in the branch section. The heat medium cooling heat exchange section exchanges heat between the refrigerant depressurized in the heat medium cooling depressurization section and the low-temperature side heat medium. The pressure adjustment section adjusts at least one of the refrigerant pressure in the air cooling heat exchange section and the refrigerant pressure in the heat medium cooling heat exchange section. The confluence section merges the flow of the refrigerant flowing out of the air cooling heat exchange section and the flow of the refrigerant flowing out of the heat medium cooling heat exchange section, and causes the refrigerant to flow out to the suction side of the compressor. The low-temperature side outside air heat exchange section 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 distribution section distributes the amount of heat contained in the refrigerant discharged from the compressor between 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. 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 the outside of the space to be air-conditioned. The auxiliary outside air introduction unit introduces outside air into the heating unit.

[0040] The air-cooling heat exchange section 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 flow of blown air in 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 exchange section and passes through the heating section. The cold air bypass passage is an air passage that passes through the air-cooling heat exchange section and bypasses 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 bypasses the air-cooling heat exchange section. The exhaust section is configured to be able to exhaust the entire volume of blown air that has flowed through the cold air bypass passage to outside the space to be air-conditioned.

[0041] The heat distribution unit supplies heat contained in the refrigerant discharged from the compressor to the heating unit during a dehumidification heating mode in which the space to be air-conditioned is dehumidified and heated. The heat distribution section is In a defrosting mode for removing frost formed on the low-temperature side outdoor air heat exchange section, the amount of heat supplied to the low-temperature side outdoor air heat exchange section is increased more than in a dehumidification heating mode. In the adsorption process in which moisture is adsorbed into the adsorption section in the dehumidifying heating mode, the inside / outside air ratio adjustment section Allowing internal air to flow in In the desorption process in which moisture is desorbed from the adsorption section in the dehumidifying heating mode, the inside / outside air ratio adjustment section transfers the moisture to the air cooling heat exchange section. Let outside air in In the desorption process, the exhaust gas passes through an air-cooling heat exchanger. Total airflow The ventilation air, Without entering the space to be air-conditioned, the cold air is passed through a bypass passage. The air is exhausted outside the space to be air-conditioned. In the desorption process, the auxiliary outside air intake section: Through the outside air bypass passage Outside air is introduced into the heating section, and the air heated by the heating section is sent to the space to be air-conditioned.

[0042] According to this, in the dehumidifying and heating mode, the heat distribution section (43) supplies heat contained in the refrigerant discharged from the compressor to the heating section. Therefore, in the dehumidifying and heating mode, the blown air 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.

[0043] 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 utilized 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 conditioner as a whole can be improved.

[0044] In the defrosting mode, the heat distributor (43) supplies a larger amount of heat to the low-temperature side outdoor air heat exchanger (54) than in the dehumidification heating mode, so that the frost on the low-temperature side outdoor air heat exchanger (54) can be melted and removed.

[0045] Furthermore, in the defrost mode, the heat distribution section (43) can also supply heat to the heating sections (12a, 40a). Therefore, even if the blown air is cooled by the air-cooling heat exchange section (15) in the defrost mode, the blown air can be reheated by the heating sections (12a, 40a). As a result, even if the rotation speed of the compressor (11) is determined so that 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.

[0046] In other words, according to the air conditioner of claim 4, it is possible to obtain the effect of improving the operating efficiency by providing the air-cooling heat exchange section (15) having the adsorption section (15a), while appropriately returning refrigeration oil to the compressor (11).

[0047] 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 later. [Brief description of the drawings]

[0048] [Figure 1] 1 is an overall configuration diagram of a vehicle air conditioner according to a first embodiment. [Diagram 2] 2 is a block diagram showing an electric control unit of the vehicle air conditioner of the first embodiment. FIG. [Diagram 3] FIG. 3 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. [Figure 4] FIG. 3 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. [Diagram 5] FIG. 3 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. [Figure 6] 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. [Figure 7] FIG. 11 is an overall configuration diagram showing the flow of refrigerant in a dehumidifying and heating mode of a vehicle air conditioner according to a second embodiment. [Figure 8]FIG. 11 is a block diagram showing an electric control unit of a vehicle air conditioner according to a second embodiment. [Figure 9] 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 a refrigeration cycle device of a second embodiment. [Figure 10] 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. [Figure 11] 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. [Figure 12] 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. [Figure 13] FIG. 11 is an overall configuration diagram showing the flow of refrigerant in a dehumidifying and heating mode of a vehicle air conditioner according to a third embodiment. [Figure 14] FIG. 11 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. [Figure 15] FIG. 11 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. [Figure 16] FIG. 11 is an overall configuration diagram showing the flows of refrigerant and heat medium during an adsorption process in a single dehumidification and heating mode of a vehicle air conditioner according to a fourth embodiment. [Figure 17] FIG. 11 is an overall configuration diagram showing the flows of refrigerant and heat medium during a desorption process in a single dehumidification and heating mode of a vehicle air conditioner according to a fourth embodiment. [Figure 18] FIG. 11 is an overall configuration diagram showing the flows of refrigerant and heat medium during an adsorption process in a cooling, dehumidifying and heating mode of a vehicle air conditioner according to a fourth embodiment. [Figure 19] FIG. 11 is an overall configuration diagram showing the flows of the refrigerant and the heat medium during a desorption process in a cooling, dehumidifying and heating mode of a vehicle air conditioner according to a fourth embodiment. [Figure 20] FIG. 13 is a block diagram showing an electric control unit of a vehicle air conditioner according to a fourth embodiment. [Figure 21]FIG. 13 is a Mollier diagram showing a change in state of a refrigerant during an adsorption process in a single dehumidification and heating mode in a refrigeration cycle device of a fourth embodiment. [Figure 22] 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 fourth embodiment. [Diagram 23] FIG. 11 is a Mollier diagram showing a change in state of a refrigerant in a single defrost mode in a refrigeration cycle device of a fourth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0049] Hereinafter, a number of embodiments for carrying out the present invention will be described with reference to the drawings. In each embodiment, the same reference numerals may be used to designate parts corresponding to matters described in the preceding embodiment, and duplicated descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other embodiments described previously may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically indicated as being possible in each embodiment, it is also possible to partially combine embodiments even if not indicated, as long as there is no particular problem with the combination.

[0050] (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 power 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.

[0051] As shown in the overall configuration diagram of FIG. 1, the vehicle air conditioner 1 includes a refrigeration cycle device 10 and an interior air conditioning unit 30.

[0052] First, a description will be given of the refrigeration cycle device 10. The refrigeration cycle device 10 adjusts the temperature of air blown into the vehicle cabin in the vehicle air conditioner 1. The refrigeration cycle device 10 is configured to be capable of switching a refrigerant circuit that circulates the refrigerant depending on the operation mode.

[0053] The refrigeration cycle device 10 employs an HFO refrigerant (specifically, R1234yf) as a refrigerant. The refrigeration cycle device 10 configures 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. Refrigeration oil for lubricating the compressor 11 is mixed into the refrigerant. 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.

[0054] The compressor 11 draws in, compresses, and discharges refrigerant in the refrigeration cycle device 10. The compressor 11 is disposed in a drive unit compartment at the front side of the vehicle cabin. The drive unit compartment is a space outside the vehicle cabin in which at least a part of a drive unit (e.g., an electric motor) for outputting drive force for traveling is disposed.

[0055] The compressor 11 is an electric compressor that uses an electric motor to rotate a fixed-capacity compression mechanism having a fixed discharge capacity. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60, which will be described later.

[0056] A discharge port of the compressor 11 is connected to a refrigerant inlet side of an indoor condenser 12. The indoor condenser 12 is disposed in a casing 31 of an indoor air conditioning unit 30, which will be described later.

[0057] 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. The indoor condenser 12 dissipates heat contained in the high-pressure refrigerant 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.

[0058] One inlet / outlet side of a four-way valve 13 is connected to a refrigerant outlet of the indoor condenser 12. The four-way valve 13 is a refrigerant circuit switching unit that switches the refrigerant circuit that circulates the refrigerant in the refrigeration cycle device 10. The four-way valve 13 is an electric switching valve whose operation is controlled by a control voltage output from the control device 60.

[0059] 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 inlet / outlet side of the first expansion valve 14a, and at the same time connects one refrigerant inlet / outlet side of an outdoor heat exchanger 16 (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 inlet / outlet side 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 refrigerant inlet / outlet side of the outdoor heat exchanger 16 (described later).

[0060] One of the inlet / outlet sides of a 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 that flows out to the downstream side.

[0061] 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 reducing action or flow rate regulating action.

[0062] The other inlet / outlet of the first expansion valve 14a is connected to one refrigerant inlet / outlet side of the indoor evaporator 15. The indoor evaporator 15 is disposed inside the casing 31 of the indoor air-conditioning unit 30, and upstream of the indoor condenser 12 in the flow of blown air.

[0063] 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 an 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.

[0064] Furthermore, in this embodiment, a so-called tank-and-tube type heat exchanger is adopted as the indoor evaporator 15. The tank-and-tube type heat exchanger has a plurality of refrigerant tubes and a pair of refrigerant tanks.

[0065] The refrigerant tubes are metal tubes through which a refrigerant flows. A plurality of the refrigerant tubes are stacked and arranged in a predetermined direction with gaps between them. 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 metal sheet into a corrugated shape.

[0066] The refrigerant tank is a bottomed cylindrical member made of metal and extending in the stacking direction of the refrigerant tubes. The pair of refrigerant tanks are connected to both ends of the refrigerant tubes, respectively. Inside the refrigerant tank, a distribution space that distributes the refrigerant to the refrigerant tubes and a collection space that collects the refrigerant flowing out from the refrigerant tubes are formed. Therefore, in the 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.

[0067] In the indoor evaporator 15, a desiccant material 15a is applied to the outer surface of the heat exchange core part. 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.

[0068] One of the inlet / outlet sides of the second expansion valve 14b is connected to the other refrigerant inlet / outlet of the indoor evaporator 15. The second expansion valve 14b is a second pressure reducing section that reduces the pressure of the refrigerant. The second expansion valve 14b is a second refrigerant flow rate adjusting section that adjusts the flow rate of the refrigerant that flows out to the downstream side. The basic configuration of the second expansion valve 14b is the same as that of the first expansion valve 14a.

[0069] The other refrigerant inlet / outlet side of the exterior heat exchanger 16 is connected to the other refrigerant inlet / outlet side of the exterior heat exchanger 16. 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 on 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.

[0070] 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. A suction port side of the compressor 11 is connected to yet another inlet / outlet of the four-way valve 13.

[0071] Next, the interior air conditioning unit 30 will be described. The interior air conditioning unit 30 is a unit for blowing out air adjusted to an appropriate temperature toward an appropriate location in the vehicle cabin in the vehicle air conditioner 1. The interior air conditioning unit 30 is disposed inside the instrument panel (i.e., the instrument panel) disposed at the frontmost part of the vehicle cabin.

[0072] The indoor air conditioning unit 30 has a casing 31 that forms an air passage therein for the blown air. 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.

[0073] An inside / outside air switching device 33 is disposed on the most upstream side of the blown air flow of the casing 31. The inside / outside air switching device 33 adjusts the introduction 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.

[0074] 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. In this way, the inside / outside air door 33a adjusts the area ratio between the opening area of ​​an inside air inlet that introduces inside air into the air passage in the casing 31 and the opening area of ​​an 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.

[0075] An interior blower 32 is disposed downstream of the inside / outside air switching device 33 in the flow of blown air. The interior blower 32 blows air drawn in through the inside / outside air switching device 33 toward the vehicle cabin. 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.

[0076] The downstream side of the blown air flow of the indoor blower 32 is divided into a plurality of air passages. Furthermore, in the air passage downstream of the blown air flow of the indoor blower 32, the indoor evaporator 15 and the indoor condenser 12 are arranged in this order with respect to the blown air flow. In other words, the indoor evaporator 15 is arranged upstream of the indoor condenser 12 in the blown air flow.

[0077] 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 causes 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 causes the blown air that has passed through the indoor evaporator 15 to bypass the indoor condenser 12 and flow downstream.

[0078] Further, an outside air bypass passage 35c is formed on the downstream side of the air flow of the indoor blower 32, which allows the air to flow while bypassing the indoor evaporator 15. The most downstream part of the air flow of the outside air bypass passage 35c is connected to an auxiliary outside air inlet 31a, which will be described later.

[0079] An air mix door 34 is disposed in an air passage downstream of the indoor evaporator 15 in the flow of blown air and upstream of the heating passage 35a and the cold air bypass passage 35b. The air mix door 34 adjusts the ratio of the amount of air that flows into the heating passage 35a and the cold air bypass passage 35b, among the amount of air that has passed through the indoor evaporator 15.

[0080] 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.

[0081] When the air mix door 34 changes the opening area of ​​the entrance of the heating passage 35a, the amount of blown air passing through the heating passage 35a changes. When the amount of blown air passing through the heating passage 35a changes, the amount of heat exchanged between the refrigerant and the blown air in the interior 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 interior condenser 12.

[0082] 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.

[0083] Furthermore, at the most downstream portion of the casing 31 in the flow of the blown air, a plurality of openings (not shown) are formed for blowing out the blown air (conditioned air) mixed in the mixing space 36 into the vehicle compartment.

[0084] 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. That is, by displacing the air mix door 34, the temperature of the blown air blown into the vehicle compartment from each opening can be adjusted.

[0085] 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.

[0086] An air outlet mode switching door (not shown) is disposed upstream of these openings. The air outlet 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 air outlet mode switching door is controlled by a control signal output from the control device 60.

[0087] In addition, an auxiliary outside air introduction device 37 is disposed at a portion of the casing 31 that forms the heating passage 35a. The auxiliary outside air introduction device 37 is an auxiliary outside air introduction section that introduces outside air from the downstream side of the air mix door 34 to the indoor condenser 12 during a desorption process that will be described later.

[0088] 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.

[0089] 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.

[0090] An exhaust device 38 is disposed on the most downstream side of the cold air bypass passage 35b of the casing 31. The exhaust device 38 is an exhaust unit that exhausts the blown air that has flowed through the cold air bypass passage 35b to the outside of the vehicle compartment during a desorption process in a dehumidification heating mode, which will be described later.

[0091] 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.

[0092] When the electric actuator for the exhaust door displaces the exhaust door 38a so as to fully open the exhaust port 31b, not only the exhaust port 31b is opened but also the communication portion between the cold air bypass passage 35b and the mixing space 36 is closed. As a result, the entire volume of the 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.

[0093] In addition, when the electric actuator for the exhaust door displaces the exhaust door 38a to fully close the exhaust port 31b, the communication part between the cold air bypass passage 35b and the mixing space 36 opens. As a result, the entire volume of the blown air that has flowed through the cold air bypass passage 35b flows into the mixing space 36 without being exhausted to the outside.

[0094] 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 control target devices 11, 13, 14a, 14b, 32, 33, 34a, 37, 38, etc. connected to the output side.

[0095] 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 amount 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.

[0096] The inside air temperature sensor 61a is an inside air temperature detector that detects the inside air temperature Tr, which is the temperature inside the vehicle cabin. The outside air temperature sensor 61b is an outside air temperature detector that detects the outside air temperature Tam, which is the temperature outside the vehicle cabin. The solar radiation sensor 61c is an solar radiation amount detector that detects the amount of solar radiation As irradiated into the vehicle cabin. The detection values ​​of these detectors are used when calculating a target blown air temperature TAO, which will be described later, and the like.

[0097] The high-pressure pressure sensor 61d is a high-pressure pressure detection unit that detects a 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 air conditioning air temperature detection unit that detects the temperature TAV of air blown from the mixing space 36 into the vehicle cabin.

[0098] 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.

[0099] The evaporator pressure sensor 61g is an evaporator pressure detection unit that detects the refrigerant evaporation pressure Pe in the indoor evaporator 15. Specifically, the evaporator pressure sensor 61g in this embodiment detects the pressure of the refrigerant on one refrigerant inlet / outlet side of the indoor evaporator 15 (the refrigerant inlet / outlet side to which the first expansion valve 14a is connected).

[0100] 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. Specifically, the outdoor unit temperature sensor 61h in this embodiment 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).

[0101] The outdoor unit pressure sensor 61i is an outdoor unit temperature detection unit that detects an outdoor unit refrigerant pressure Pout, which is the pressure of the refrigerant flowing through the outdoor heat exchanger 16. Specifically, the outdoor unit pressure sensor 61i in this embodiment detects the pressure 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).

[0102] Furthermore, an operation panel 62 arranged 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.

[0103] The various operation switches provided on the operation panel 62 specifically include an air conditioner switch, an auto switch, an air volume setting switch, a temperature setting switch, and the like.

[0104] The air conditioner switch is an operational switch for requesting cooling of the blown air by the interior evaporator 15. The auto switch is an operational switch for setting or canceling the automatic control operation of the refrigeration cycle device 10. The air volume setting switch is an operational switch for manually setting the air volume of the interior blower 32. The temperature setting switch is an operational switch for setting a target temperature Tset in the vehicle cabin.

[0105] In addition, the control device 60 of this embodiment is configured as an integrated unit that controls various control target devices connected to the output side. That is, 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.

[0106] For example, in the control device 60, a component that controls the operation of the four-way valve 13, which is a refrigerant circuit switching unit, is a refrigerant circuit control unit 60a. A component that controls the operation of the inside / outside air switching device 33, which is an inside / outside air ratio adjustment unit, is an inside / outside air switching control unit 60b. A component that controls the operation of the electric actuator 34a for the air mix door is a heating amount control unit 60c.

[0107] Next, the operation of the vehicle air conditioner 1 will be described. In the vehicle air conditioner 1, various operation modes are switched to condition the air inside the vehicle cabin. The operation modes are switched by executing an air conditioning control program stored in advance in the control device 60. The air conditioning control program is executed when the auto switch on the operation panel 62 is turned on.

[0108] The air conditioning control program calculates a target blowing temperature TAO of the air to be blown into the vehicle cabin based on the detection signals of the above-mentioned 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 blowing temperature TAO, the detection signals of the control sensors, and the operation signals of the operation panel 62. The operation of each operation mode will be described in detail below.

[0109] (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.

[0110] 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.

[0111] The reference outside air temperature KTam is set to a value at which it is generally determined that the inner surface of the vehicle window glass is unlikely to fog up when the outside air temperature Tam is equal to or higher than the reference outside air temperature KTam. The cooling reference temperature KTao is set to a temperature at which it is generally 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.

[0112] In the cooling mode, the control device 60 fully opens the first expansion valve 14a 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, and to connect one of the inlet / outlet sides of the first expansion valve 14a to the suction side of the compressor 11.

[0113] 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: the indoor condenser 12, the four-way valve 13, the outdoor heat exchanger 16, the second expansion valve 14b, the indoor evaporator 15, the first expansion valve 14a which is in a fully open state, the four-way valve 13, and the suction port of the compressor 11.

[0114] Furthermore, the control device 60 appropriately determines control signals to be output to various controlled devices. For example, the control device 60 determines the control signal to be output to the compressor 11 so that the evaporator temperature Tefin detected by the evaporator temperature sensor 61f approaches the target evaporator temperature TEO.

[0115] The target evaporator temperature TEO is determined based on the target air outlet temperature TAO with reference to a control map for the cooling mode 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.

[0116] Regarding the control signal to be output to the inside / outside air switching device 33, the control device 60 determines to fully close the inside air inlet and fully open the outside air inlet. 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 to fully open the inside air inlet and fully close the outside air inlet.

[0117] 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.

[0118] Regarding the control signal output to the auxiliary outside air introduction device 37, the control device 60 determines to close the auxiliary outside air introduction port 31a. Regarding the control signal output to the exhaust device 38, the control device 60 determines to close the exhaust port 31b.

[0119] Then, the control device 60 outputs the control signals and the like determined as described above to various devices to be controlled.

[0120] In the air conditioning control program, until a request to stop the air conditioning in the vehicle cabin is received, at each predetermined control period, control routines such as reading the detection signals and operation signals, calculating the target blown air temperature TAO, determining the operation mode, determining the control signals etc. to be output to various controlled devices according to the operation mode, and outputting the determined control signals etc. are repeated. Such repetition of the control routines is similarly performed in other operation modes.

[0121] 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.

[0122] In the refrigeration cycle device 10 in the cooling mode, 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.

[0123] In addition, in the indoor air-conditioning unit 30 in the 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 when passing through the indoor evaporator 15. The blown air cooled by the indoor evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b according to the opening degree of the air mix door 34.

[0124] The blown air that flows into the heating passage 35a is heated when passing through the indoor condenser 12. The blown air heated in 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.

[0125] 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 blown air that flows through the cold air bypass passage 35b flows into the mixing space 36.

[0126] 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 together to become blown air (conditioned air) at an appropriate temperature. The blown air mixed and temperature-adjusted in the mixing space 36 is blown out through the opening to an appropriate location in the vehicle cabin. This achieves cooling of the vehicle cabin.

[0127] Here, the desiccant material 15a, which is an adsorption portion, is applied to the indoor evaporator 15. Therefore, when the air passes through the indoor evaporator 15, moisture contained in the air is adsorbed by the desiccant material 15a until the adsorption amount of the desiccant material 15a reaches a saturated amount.

[0128] However, in the cooling mode, since the outside air temperature Tam is equal to or higher than the reference outside air temperature KTam, the vehicle window glass is unlikely to fog up. Therefore, in the cooling mode, even if the adsorption amount of the desiccant material 15a reaches the saturation amount, the desorption process in which the moisture is desorbed from the desiccant material 15a to be regenerated is not performed. Therefore, in the cooling mode, the vehicle interior can be continuously cooled.

[0129] (b) Dehumidification heating mode The dehumidifying and heating mode is an operation mode in which the cooled and dehumidified ventilation 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 outlet temperature TAO is higher than the cooling reference temperature KTao.

[0130] 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. Therefore, 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 a saturated amount.

[0131] Therefore, in the dehumidifying heating mode, 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 are switched at a predetermined cycle.

[0132] First, in the adsorption process of the dehumidifying 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, and to connect one of the refrigerant inlet / outlet sides of the outdoor heat exchanger 16 to the suction side of the compressor 11.

[0133] 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.

[0134] Furthermore, the control device 60 appropriately determines control signals to be output to various controlled devices. For example, the control device 60 determines the control signal to be output to the compressor 11 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 by referring to a control map for the dehumidification heating mode stored in advance in the control device 60.

[0135] Regarding the control signal output to the inside / outside air switching device 33, the control device 60 determines to fully open the inside air inlet and fully close the outside air inlet. That is, in the adsorption stroke, the inside / outside air switching device 33 increases the ratio of inside air in the blown air flowing into the indoor evaporator 15 more than the ratio of outside air.

[0136] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the cooling mode. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0137] Therefore, in the refrigeration cycle device 10 in the adsorption process, as shown in the Mollier diagram of Fig. 3, the refrigerant discharged from the compressor 11 (point a3 in Fig. 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 to point b3 in Fig. 3). The refrigerant that flows out of the indoor condenser 12 is decompressed by the first expansion valve 14a (point b3 to point c3 in Fig. 3) and flows into the indoor evaporator 15.

[0138] The refrigerant that flows into the indoor evaporator 15 evaporates by exchanging heat with the blown air (point c3 to point d3 in FIG. 3). The refrigerant that flows out of the indoor evaporator 15 flows into the outdoor heat exchanger 16 via the second expansion valve 14b, which is fully open. Note that FIG. 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 by exchanging heat with the outside air (point d3 to point e3 in FIG. 3).

[0139] The refrigerant flowing out from the outdoor heat exchanger 16 is drawn into the compressor 11 and compressed again (from point f3 to point a3 in FIG. 3). The difference in pressure between point e3 and point f3 in FIG. 3 is the suction pressure loss of the compressor 11. The suction pressure loss is also shown in the following Mollier diagram.

[0140] That is, 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 type 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.

[0141] In the adsorption process of the indoor air-conditioning unit 30, 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. 3. 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.

[0142] The blown air 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 to an appropriate location in the vehicle cabin through the opening hole. This achieves dehumidification and heating of the vehicle cabin.

[0143] Next, in the desorption process of the dehumidifying and heating 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 inlet / outlet sides of the first expansion valve 14a, and to connect one of the refrigerant inlet / outlet sides of the outdoor heat exchanger 16 to the suction side of the compressor 11.

[0144] Therefore, in the refrigeration cycle device 10 in the desorption process, as shown by the solid arrows in FIG. 1, the refrigerant circulates in the refrigerant circuit in the same order as in the adsorption process.

[0145] Furthermore, the control device 60 appropriately determines control signals to be output to various controlled devices. For example, with regard to the control signal to be output to the inside / outside air switching device 33, the control device 60 determines the control signal so as to fully close the inside air inlet and fully open the outside air inlet. In other words, in 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 more than the proportion of inside air.

[0146] Regarding the control signal output to the auxiliary outside air introduction device 37, the control device 60 determines to open the auxiliary outside air introduction port 31a. Regarding the control signal output to the exhaust device 38, the control device 60 determines to fully open the exhaust port 31b.

[0147] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the adsorption process. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0148] Therefore, in the desorption process of the refrigeration cycle apparatus 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 to 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.

[0149] The refrigerant that flows into the indoor evaporator 15 releases heat to the outside air and the desiccant material 15a and condenses (point b4 to point c4 in FIG. 4). The refrigerant that flows out of the indoor evaporator 15a is depressurized by the second expansion valve 14b (point c4 to point d4 in FIG. 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 to point e4 in FIG. 4). The refrigerant that flows out of the outdoor heat exchanger 16 is drawn into the compressor 11 and compressed again (point f4 to point a4 in FIG. 4).

[0150] That is, in the refrigeration cycle device 10 in the desorption process, 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 refrigeration cycle device 10 in the desorption process, the blown air is heated in the indoor condenser 12.

[0151] In the desorption process of the indoor air conditioning unit 30, 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.

[0152] The outside air that has passed through the interior evaporator 15 flows into the cold air bypass passage 35b because the air mix door 34 fully closes the inlet of the heating passage 35a. The outside air that has flowed into the cold air bypass passage 35b is exhausted to the outside of the vehicle compartment through the exhaust port 31b because the exhaust device 38 fully opens the exhaust port 31b.

[0153] The outside air that flows into the heating passage 35a from the auxiliary outside air inlet 31a is heated when passing 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.

[0154] (c) Defrost 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.

[0155] 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 equal to or lower than a predetermined reference frost formation temperature KToutf is measured during execution of the dehumidification heating mode. When the frost formation time Tmf becomes equal to or higher than the reference frost formation time KTmf, it is determined that the frost formation condition is met.

[0156] 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, and to connect one of the inlet / outlet sides of the first expansion valve 14a to the suction port side of the compressor 11.

[0157] Therefore, in the defrosting mode, the refrigeration cycle apparatus 10 is switched 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 FIG.

[0158] 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 signal to be output to the compressor 11 so as to set the rotation speed lower than that in the dehumidification heating mode. The control signal to be output to the compressor 11 is determined within a range in which the refrigerating machine oil mixed in the refrigerant can be returned to the compressor 11.

[0159] As for the control signal output to the inside / outside air switching device 33, the control device 60 determines to fully open the inside air inlet and fully close the outside air inlet. As for the control signal output to the indoor blower 32, the control device 60 determines to have a lower rotation speed than in the dehumidifying heating mode.

[0160] In addition, the control device 60 determines the control signal output to the electric actuator 34a for the air mix door so as 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.

[0161] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the dehumidifying and heating mode. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0162] Therefore, in the refrigeration cycle apparatus 10 in the defrost mode, as shown in the Mollier diagram of 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 to point b5 in Fig. 5). The refrigerant that flows out of the indoor condenser 12 flows into the outdoor heat exchanger 16.

[0163] The refrigerant that flows into the outdoor heat exchanger 16 releases heat to the outside air and the outdoor heat exchanger 16 and condenses (point b5 to 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 to 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 to 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 to point a5 in FIG. 5).

[0164] That is, in the refrigeration cycle device 10 in the defrost mode, the indoor condenser 12 and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 15 functions as an evaporator, forming a vapor compression refrigeration cycle.

[0165] In the defrosting mode of the refrigeration cycle apparatus 10, the blown air is heated by the indoor condenser 12. The blown air is cooled and dehumidified by the indoor evaporator 15. Furthermore, in the outdoor heat exchanger 16, the frost on the outdoor heat exchanger 16 is melted and removed by the heat of the refrigerant flowing out from the indoor condenser 12. That is, the outdoor heat exchanger 16 is defrosted.

[0166] In the indoor air-conditioning unit 30 in the defrost mode, the inside air introduced into the casing 31 via the inside / outside 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. 5. 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 also by the adsorption action of the desiccant material 15a.

[0167] The blown air cooled and dehumidified in 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, similar to 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.

[0168] In the defrosting 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 inlet of the heating passage 35a is smaller than in the dehumidifying and heating mode. Therefore, although the amount of heat of 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.

[0169] The defrost mode ends when a predetermined end condition is satisfied. When the defrost mode ends, the mode transitions to a dehumidifying and heating mode. In the air conditioning control program of this embodiment, it is determined that the end condition is satisfied when the execution time Tmdf of the defrost mode becomes equal to or longer than the reference defrost time KTmdf and the outdoor unit temperature Tout becomes equal to or longer than the predetermined reference defrost temperature KToutdf.

[0170] As described above, according to the vehicle air conditioner 1 of this embodiment, comfortable air conditioning for the vehicle interior can be achieved by switching the operation mode.

[0171] Furthermore, in the vehicle air conditioner 1 of this embodiment, the 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.

[0172] 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 the refrigerating machine oil can be appropriately returned to the compressor 11, a decrease in the temperature inside the vehicle cabin can be suppressed.

[0173] In other words, according to the vehicle air conditioning system 1 of this embodiment, it is possible to obtain the effect of improving the operating efficiency by providing the indoor evaporator 15 to which the desiccant material 15a is applied, while appropriately returning refrigeration oil to the compressor 11 regardless of which operating mode is switched to.

[0174] In the vehicle air conditioner 1 of this embodiment, the adsorption process and the desorption process are switched in the dehumidification heating mode. In the adsorption process in the dehumidification heating mode, the inside / outside air switching device 33 increases the ratio of inside air to the blown air flowing into the interior evaporator 15 compared to the outside air.

[0175] According to this, 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 a larger amount than the outside air. Therefore, the power consumption of the compressor 11 consumed to reheat the blown air can be reduced, and the coefficient of performance of the refrigeration cycle device 10 can be further improved. As a result, the operating efficiency of the vehicle air conditioner 1 can be further improved.

[0176] Furthermore, in the desorption process of the dehumidifying heating mode, the inside / outside air switching device 33 increases the ratio of outside air to the inside air in the blown air flowing into the indoor evaporator 15. As a result, it is possible to introduce more outside air, which has a lower humidity than the inside air, into the indoor evaporator 15 during the desorption process. Therefore, it is possible to efficiently regenerate the desiccant material 15a.

[0177] The vehicle air conditioner 1 of this embodiment is also provided 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 by the interior condenser 12 and blown into the vehicle cabin. Therefore, when the dehumidification heating mode is performed, 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 be suppressed.

[0178] Furthermore, 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.

[0179] In addition, the vehicle air conditioner 1 of this embodiment is provided with an exhaust device 38, and exhausts the air that has passed through the interior evaporator 15 to the outside of the vehicle compartment during the desorption process in the dehumidifying 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 is possible to effectively prevent the vehicle window glass from fogging up during the desorption process.

[0180] 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.

[0181] The vehicle air conditioner 1a includes 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.

[0182] 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 apparatus 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.

[0183] The water-refrigerant heat exchanger 12a is a heat exchanger for heating a heat medium, which 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, so that the high-pressure refrigerant is condensed and the high-temperature heat medium is heated.

[0184] The inlet side of a 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 inlet and outlet ports that communicate with each other. The first three-way joint 17a may be a member formed by joining multiple pipes, or a member formed by providing multiple refrigerant passages in a metal block or a resin block.

[0185] Furthermore, the refrigeration cycle apparatus 10a includes a second three-way joint 17b to a fourth three-way joint 17d, as described below. The second three-way joint 17b to the fourth three-way joint 17d have the same basic configuration as the first three-way joint 17a.

[0186] 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 the refrigerant flowing in from one inlet port can be branched. In this embodiment, the first three-way joint 17a serves as a branching section. When two of the three inlet / outlet ports are used as inlet ports and the other one is used as an outlet port, the flows of the refrigerant flowing in from the two inlets can be joined together.

[0187] An inlet side of the heating expansion valve 14c is connected to one outlet side of the first three-way joint 17a. An inlet side of the second three-way joint 17b is connected to the other outlet side of the first three-way joint 17a via a bypass passage 22a.

[0188] 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.

[0189] Furthermore, the refrigeration cycle device 10a includes 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 operation mode by opening and closing the refrigerant passage. Therefore, the high-pressure on-off valve 13a and the low-pressure on-off valve 13b are the refrigerant circuit switching unit of this embodiment.

[0190] 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 a dehumidification heating mode, which will be described later. The heating expansion valve 14c is an outdoor refrigerant flow rate adjusting section that adjusts the flow rate of the refrigerant that flows out to the downstream side. The basic configuration of the heating expansion valve 14c is the same as that of the first expansion valve 14a described in the first embodiment.

[0191] Furthermore, the refrigeration cycle apparatus 10a includes 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.

[0192] 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.

[0193] 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.

[0194] The outlet of the heating expansion valve 14c is connected to the refrigerant inlet side of the outdoor heat exchanger 16, which is an outdoor heat exchange section. The inlet side of a third three-way joint 17c is connected to the refrigerant outlet of the outdoor heat exchanger 16. One outlet of the third three-way joint 17c is connected to one inlet side of an evaporation pressure regulating valve 20 via a heating passage 22b. A low pressure on-off valve 13b that opens and closes the heating passage 22b is arranged in the heating passage 22b.

[0195] 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 disposed in a 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.

[0196] The outlet of the second three-way joint 17b is connected to the inlet side of a fourth three-way joint 17d. The inlet side of a cooling expansion valve 14d is connected to one outlet of the fourth three-way joint 17d. The inlet side of a cooling expansion valve 14e is connected to the other outlet of the fourth three-way joint 17d. The cooling expansion valve 14d and the cooling expansion valve 14e are both cooling pressure reducing parts that reduce the pressure of the refrigerant.

[0197] More specifically, the cooling expansion valve 14d is an air cooling pressure reducing section that reduces the pressure of the refrigerant flowing into the indoor evaporator 15 during a single cooling mode, which will be described later, etc. The cooling expansion valve 14d is an air refrigerant flow rate adjusting section that adjusts the flow rate of the refrigerant flowing downstream.

[0198] 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 in order to cool an object to be cooled. More specifically, the indoor evaporator 15 is an air-cooling heat exchanger that cools the blown air.

[0199] The cooling expansion valve 14e is a heat medium cooling pressure reducing unit that reduces the pressure of the refrigerant flowing into the chiller 19 during a cooling / air-cooling mode, which will be described later. The cooling expansion valve 14e is an equipment cooling refrigerant flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing downstream.

[0200] The outlet of the cooling expansion valve 14e is connected to the inlet side of a 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 side heat medium circulating in the low-temperature side heat medium circuit 50 flows.

[0201] 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. The chiller 19 cools the low-temperature heat medium by evaporating the low-pressure refrigerant to exert a heat absorption effect. The third inlet side of the evaporation pressure regulating valve 20 is connected to the outlet of the refrigerant passage of the chiller 19.

[0202] The evaporating pressure regulating valve 20 is a pressure regulating unit that individually regulates 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 evaporating pressure regulating valve 20 merges at least two or more refrigerant flows among 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, and causes the refrigerant to flow downstream.

[0203] Specifically, the evaporating pressure regulating valve 20 is an integral unit of three electrically-driven variable throttle mechanisms connected downstream of the outdoor heat exchanger 16, the indoor evaporator 15, and the chiller 19, and a junction 17g. The operation of the evaporating pressure regulating valve 20 is controlled by a control signal output from the control device 60.

[0204] The inlet side of the accumulator 21 is connected to the refrigerant outlet of the junction 17g of the evaporation pressure regulating valve 20. The accumulator 21 is a low-pressure side gas-liquid separator that separates the low-pressure refrigerant flowing out from the heat exchanger functioning as an evaporator into gas and liquid. The accumulator 21 stores the separated liquid-phase refrigerant as surplus refrigerant for the cycle.

[0205] Therefore, the confluence section 17g of the evaporation pressure control valve 20 merges the flow of refrigerant flowing out of the outdoor heat exchanger 16, the flow of refrigerant flowing out of the indoor evaporator 15, and the flow of refrigerant flowing out of the chiller 19, and causes the refrigerant to flow out to the suction side of the compressor 11.

[0206] 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 ethylene glycol aqueous 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.

[0207] 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 a control voltage output from the control device 60.

[0208] 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.

[0209] 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.

[0210] 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.

[0211] 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 exchanged between the high-temperature side heat medium and the blown air in the heater core 42. 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.

[0212] 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, a water passage of the chiller 19, a low-temperature side heat medium pump 51, a cooling water passage 80a of the battery 80, etc. are arranged.

[0213] The low-temperature side heat medium pump 51 is a water pump that pumps the low-temperature side heat medium to the inlet side of the water passage of the chiller 19. The basic configuration of the low-temperature side heat medium pump 51 is similar to that of the high-temperature side heat medium pump 41. The inlet side of the cooling water passage 80a of the battery 80 is connected to the outlet of the water passage of the chiller 19.

[0214] The battery 80 is a secondary battery (a lithium ion battery in this embodiment) 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 (15° C. or higher and 55° C. or lower in this embodiment) in order to fully utilize the charging and discharging capacity of the battery 80.

[0215] The cooling water passage 80a is a heat medium device heat exchanger formed inside a 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.

[0216] Therefore, in this embodiment, the chiller 19 and each component of the low-temperature side heat medium circuit 50 form a cooling section for cooling the battery 80 that 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.

[0217] Next, an overview of the electrical control unit of the vehicle air conditioner 1a will be described with reference to Fig. 8. A control device 60 of this embodiment controls the operation of various control target devices 11, 13a, 13b, 14c to 14e, 20, 32, 33, 34a, 37, 38, 41, 61, etc. connected to the output side.

[0218] 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 side heat medium temperature sensor 61k, a low-temperature side heat medium temperature sensor 61m, etc. are added to the input side of the control device 60.

[0219] 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 temperatures of multiple locations of the battery 80. Therefore, the control device 60 can also detect the temperature difference between the various locations of the battery 80. Furthermore, the average value of the detection values ​​of the multiple temperature sensors is used as the battery temperature TB.

[0220] The high-temperature side heat medium temperature sensor 61k is a high-temperature side heat medium temperature detector that detects a 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 detector that detects a 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.

[0221] In this embodiment, the controller 60 includes a refrigerant circuit control unit 60a that controls the operation of the high pressure on-off valve 13a and the low pressure on-off valve 13b, which are refrigerant circuit switching units. A high temperature side pump control unit 60d controls the operation of the high temperature side heat medium pump 41. A low pressure side pump control unit 60e controls the operation of the low pressure side heat medium pump 61.

[0222] 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 operation modes to cool the battery 80. As in the first embodiment, the operation modes are switched by executing an air conditioning control program stored in advance in the control device 60. The operation of each operation mode will be described below.

[0223] (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.

[0224] The cooling / air-cooling mode is an operation mode that cools the battery 80 and also cools the interior of the vehicle. The cooling / air-cooling mode is executed when the execution conditions for the cooling mode similar to those in the first embodiment are met and it is determined that cooling of the battery 80 is necessary.

[0225] The determination as to whether or not cooling of the battery 80 is necessary is made 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 necessary. The determination as to whether or not cooling of the battery 80 is necessary is made in the same manner in the following operation modes.

[0226] (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.

[0227] Therefore, in the refrigeration cycle apparatus 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 suction port of the compressor 11.

[0228] 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. 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 0V.

[0229] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the cooling mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0230] Therefore, in the refrigeration cycle apparatus 10a in the single 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 apparatus 10a 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.

[0231] 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.

[0232] In the indoor air-conditioning unit 30 in the single cooling mode, the outside air introduced into the casing 31 via the inside / outside air switching device 33 is sucked into the indoor blower 32 as blown air. The blown air blown from the indoor blower 32 is cooled when passing through the indoor evaporator 15. The blown air cooled by the indoor evaporator 15 flows into the heating passage 35a and the cold air bypass passage 35b according to the opening degree of the air mix door 34.

[0233] The blown air that flows into the heating passage 35a is heated when passing through the heater core 42. The blown air heated by the heater core 42 flows into the mixing space 36, 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.

[0234] 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, thereby cooling the vehicle cabin.

[0235] (a-2) 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 in a fully open state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a throttled state.

[0236] 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 opened, 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 opened, 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.

[0237] That is, in the refrigeration cycle apparatus 10a in the cooling / cooling mode, one of the refrigerant branches 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, a refrigerant circuit is switched to one in which the refrigerant flowing out from the indoor evaporator 15 and the refrigerant flowing out from the chiller 19 join at the joining point 17g of the evaporation pressure regulating valve 20.

[0238] That is, in the refrigeration cycle apparatus 10a in the cooling / air-cooling mode, the refrigerant circuit is switched to one in which the indoor evaporator 15 and the chiller 19 are connected in parallel with respect to the refrigerant flow.

[0239] 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.

[0240] Furthermore, with regard to the control signal output to the evaporation pressure regulating valve 20, the control device 60 determines it so that the refrigerant evaporation pressure in the indoor evaporator 15 and the refrigerant evaporation pressure in the chiller 19 become appropriate values.

[0241] The control signals to be output to the other controlled devices are determined in the same manner as in the single cooling mode. Then, the control device 60 outputs the control signals determined as described above to the various controlled devices.

[0242] Therefore, in the refrigeration cycle apparatus 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 apparatus 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.

[0243] In the high-temperature side heat medium circuit 40 in the cooling / air-cooling mode, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a flows into the heater core 42, as in the single cooling mode.

[0244] 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 coolant passage 80a of the battery 80. As a result, the battery 80 is cooled.

[0245] In the interior air conditioning unit 30 in the cooling / battery cooling mode, the temperature of the blown air is adjusted and the air is blown out to an appropriate location in the vehicle cabin, in the same manner as in the single cooling mode, thereby realizing cooling of the vehicle cabin.

[0246] (b) Dehumidification heating mode The dehumidification and heating mode of the vehicle air conditioner 1a includes an independent dehumidification and heating mode and a cooling and dehumidification and heating mode. The independent dehumidification and heating mode is an operation mode that dehumidifies and heats the vehicle interior without cooling the battery 80. The independent dehumidification and heating mode is executed when the execution conditions for the dehumidification 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.

[0247] The cooling, dehumidifying and heating mode is an operation mode that cools the battery 80 and dehumidifies and cools the vehicle interior. The cooling, 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 necessary.

[0248] In the vehicle air conditioner 1a, the dehumidifying and heating mode utilizes the adsorption action of the desiccant material 15a to dehumidify the air. Therefore, in the dehumidifying and heating mode, the adsorption process and the desorption process are switched at a predetermined cycle, as in the first embodiment.

[0249] (b-1) Single dehumidification and heating mode In the adsorption process of the single dehumidification heating mode, the controller 60 opens the high pressure on-off valve 13a and the low pressure on-off valve 13b. The controller 60 also sets the heating expansion valve 14c in a throttling state, the cooling expansion valve 14d in a throttling state, and the cooling expansion valve 14e in a fully closed state.

[0250] 7, the refrigerant discharged from the compressor 11 circulates through 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 suction port of the compressor 11 in that order. 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 cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure control valve 20, the accumulator 21, and the suction port of the compressor 11 in that order.

[0251] That is, in the refrigeration cycle apparatus 10a in the adsorption stroke of the single dehumidification heating mode, one of the refrigerant branches 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 in which they are joined at the joining point 17g of the evaporation pressure regulating valve 20.

[0252] That is, in the refrigeration cycle apparatus 10a in the adsorption process in the single dehumidification 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 parallel with respect to the refrigerant flow.

[0253] 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. Moreover, 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.

[0254] Furthermore, the control signal output to the evaporation pressure regulating valve 20 is determined by the control device 60 so that the refrigerant evaporation pressure in the exterior heat exchanger 16 and the refrigerant evaporation pressure in the interior evaporator 15 become appropriate values.

[0255] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the adsorption process in the dehumidifying and heating mode in the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0256] Therefore, in the refrigeration cycle apparatus 10a in the adsorption stroke in the single dehumidification and 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.

[0257] One of the refrigerant branches off at the first three-way joint 17a is decompressed by the heating expansion valve 14c (from point b9 to point c9 in FIG. 9) and flows into the outdoor heat exchanger 16. The refrigerant that has flowed into the outdoor heat exchanger 16 exchanges heat with outside air and evaporates (from point c9 to point d9 in FIG. 9).

[0258] 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 by 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 regulating 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).

[0259] The refrigerant flowing out from the indoor evaporator 15 and the refrigerant flowing out from the outdoor heat exchanger 16 are joined at a joining portion 17g. The refrigerant flowing out from the joining portion 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 to point a9 in FIG. 9).

[0260] That is, in the refrigeration cycle device 10a in the adsorption process in 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 in 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.

[0261] In the high-temperature side heat medium circuit 40 during the adsorption stroke in the single dehumidification and 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.

[0262] In the indoor air-conditioning unit 30 in the adsorption stroke of 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.

[0263] Furthermore, in 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 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.

[0264] In addition, in Fig. 9, the blown air flowing into the heating passage 35a is illustrated 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 diagram. In other words, Fig. 9 shows that the blown air flowing into the heating passage 35a is heated by using the heat dissipated by the refrigerant in the water-refrigerant heat exchanger 12a as a heat source. This is also true for the following Mollier diagrams using the water-refrigerant heat exchanger 12a and the chiller 19.

[0265] The blown air that has flowed 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 hole. This realizes dehumidification and heating in the vehicle cabin.

[0266] 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.

[0267] Therefore, in the refrigeration cycle apparatus 10a during the desorption stroke in the single dehumidification and heating mode, as shown by the hatched arrows in FIG. 7, the refrigerant discharged from the compressor 11 circulates through the water-refrigerant heat exchanger 12a, the bypass passage 22a, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure control valve 20, the accumulator 21, and the suction port of the compressor 11, in that order.

[0268] 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 exhibit a predetermined refrigerant discharge capacity for the desorption process.

[0269] Moreover, the control signal output to the cooling expansion valve 14d is determined so as to be a predetermined reference throttle opening for the desorption process. The reference 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 reference 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, during the desorption process, the cooling expansion valve 14 may be fully open.

[0270] Furthermore, the control signal output to the evaporation pressure regulating valve 20 is determined by the control device 60 so that the refrigerant evaporation pressure in the accumulator 21 becomes an appropriate value.

[0271] Moreover, the control voltage output to the high temperature side heat medium pump 41 and the control voltage output to the low temperature side heat medium pump 51 are determined in the same manner as in the adsorption stroke.

[0272] The control signals and the like 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 and the like determined as described above to the various controlled devices.

[0273] Therefore, in the refrigeration cycle apparatus 10a in the desorption process in the single dehumidification and heating mode, the refrigerant discharged from the compressor 11 (point a10 in FIG. 10) flows into the water-refrigerant heat exchanger 12a as shown in the Mollier diagram of FIG. 10. The refrigerant that flows into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and releases heat (point a10 to point b10 in FIG. 10).

[0274] 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 to point c10 in FIG. 10). The refrigerant depressurized by the cooling expansion valve 14d flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 dissipates heat to the outside air and the desiccant material 15a (point c10 to point d10 in FIG. 10).

[0275] 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).

[0276] That is, in the refrigeration cycle apparatus 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 to configure a so-called hot gas cycle. In the refrigeration cycle apparatus 10a in the desorption process, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a.

[0277] In the desorption process in the single dehumidification and 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 in the high-temperature side heat medium circuit 40. The high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a flows into the heater core 42.

[0278] 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.

[0279] As shown by the dashed arrows in the Mollier diagram of Fig. 10, a portion of the outside air blown from the interior blower 32 is humidified by moisture desorbed from the desiccant material as it passes through the interior evaporator 15. This regenerates the desiccant material 15a. The outside air that has passed through the interior 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.

[0280] Another part 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 in the dehumidification heating mode of the first embodiment, the outside air that has flowed into the heating passage 35a is heated using 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 then blown into the vehicle cabin. This allows the vehicle cabin to be heated even during the desorption process in the single dehumidification heating mode.

[0281] (b-2) Cooling, dehumidifying and heating mode In the adsorption process of the cooling / dehumidifying / heating mode, the control device 60 opens the high pressure on-off valve 13a and the low pressure on-off valve 13b. 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.

[0282] 7, the refrigerant discharged from the compressor 11 circulates through 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 suction port of the compressor 11 in this order. 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 14d, the indoor evaporator 15, the evaporation pressure control valve 20, the accumulator 21, and the suction port of the compressor 11 in this order. 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.

[0283] That is, in the refrigeration cycle apparatus 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.

[0284] 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 join at the joining point 17g of the evaporation pressure regulating valve 20.

[0285] That is, in the refrigeration cycle apparatus 10a in the adsorption process of 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 with respect to the refrigerant flow.

[0286] 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. Also, 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.

[0287] In addition, with regard to the control signal output to the evaporation pressure regulating valve 20, the control device 60 determines it 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.

[0288] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the adsorption process in the dehumidifying and heating mode in the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0289] 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, forming a vapor compression refrigeration cycle.

[0290] In the refrigeration cycle device 10a in the adsorption process of the cooling, dehumidifying and 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. The low-temperature side heat medium is cooled in the chiller 19.

[0291] In the high-temperature side heat medium circuit 40 in 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, as in the adsorption process in the single dehumidifying / heating mode.

[0292] In the low-temperature side heat medium circuit 50 during the adsorption process in the cooling / dehumidifying / heating mode, the low-temperature side heat medium pumped from the low-temperature side heat medium pump 51 flows into the chiller 19. The low-temperature side heat medium cooled in the chiller 19 flows through the cooling water passage 80a of the battery 80. As a result, the battery 80 is cooled.

[0293] 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 is blown out to an appropriate location in the vehicle cabin, in the same manner as during the adsorption process in the single dehumidifying and heating mode. This realizes dehumidifying and heating the vehicle cabin.

[0294] 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.

[0295] Furthermore, the control device 60 appropriately determines the control signals to be output to 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.

[0296] The control signals and the like 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 and the like determined as described above to the various controlled devices.

[0297] Therefore, in the refrigeration cycle apparatus 10a in the desorption process of 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, as in the desorption process of the single dehumidifying / heating mode. In the refrigeration cycle apparatus 10a in the desorption process, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12a.

[0298] In the desorption process of the cooling, dehumidifying and 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 in the high-temperature side heat medium circuit 40. The high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a flows into the heater core 42.

[0299] 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, during the desorption process, the low-temperature side heat medium cooled during the adsorption process can continue to cool the battery 80. In other words, the amount of the 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.

[0300] In the desorption process of the cooling, dehumidifying and heating mode, the interior air conditioning unit 30 regenerates the desiccant material 15a of the interior evaporator 15 in the same manner as in the desorption process of the single dehumidifying and heating mode. The outside air that has been humidified while passing through the interior evaporator 15 is exhausted from the exhaust port 31b of the exhaust device 38 to the outside of the vehicle compartment.

[0301] Furthermore, the outside air that has flowed into the heating passage 35a via the outside air bypass passage 35c is heated by heat exchange with the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a when passing through the heater core 42 as blown air, and is then blown into the vehicle cabin. This allows the vehicle cabin to be heated even during the desorption process in the cooling / dehumidifying / heating mode.

[0302] (c) Defrost 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.

[0303] The waste heat defrost mode is an operation mode that cools the battery 80 and defrosts the outdoor heat exchanger 16. The waste heat defrost mode is executed when a frost condition is met during execution of the cooling, dehumidifying, and heating mode. The waste heat defrost mode ends when a termination condition is met. When the defrost mode ends, the operation transitions to the cooling, dehumidifying, and heating mode.

[0304] (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 refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the single cooling mode.

[0305] Furthermore, the control device 60 appropriately determines the control signals to be output to 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. Moreover, 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.

[0306] Regarding the compressor 11, the control device 60 determines a control signal to be output to the compressor 11 so that the rotation speed is lower than that in the single dehumidification heating mode. The control signal to be output to the compressor 11 is determined within a range in which the refrigerating machine oil mixed in the refrigerant can be returned to the compressor 11.

[0307] In addition, the control device 60 determines the control signal output to the electric actuator 34a for the air mix door so as 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.

[0308] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the defrosting mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0309] Therefore, in the refrigeration cycle apparatus 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 to 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.

[0310] The refrigerant that flows into the outdoor heat exchanger 16 releases heat to the outside air and the outdoor heat exchanger 16 and condenses (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).

[0311] 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 FIG. 11).

[0312] That is, in the refrigeration cycle apparatus 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.

[0313] In the refrigeration cycle apparatus 10a in the single defrost mode, the high temperature side 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 frost on the outdoor heat exchanger 16 is melted and removed by the heat of the refrigerant flowing out from the indoor condenser 12. That is, the outdoor heat exchanger 16 is defrosted.

[0314] 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.

[0315] 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 as it passes through the heater core 42 using the heat radiated by the refrigerant in the water-refrigerant heat exchanger 12a as a heat source.

[0316] 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 inlet of 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.

[0317] (c-2) Waste heat defrost 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 refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the cooling / cooling mode.

[0318] 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 the pumping capacity is lower than that in the single dehumidification heating mode. Moreover, 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.

[0319] Furthermore, with regard to the control signal output to the evaporation pressure regulating valve 20, the control device 60 determines it so that the refrigerant evaporation pressure in the indoor evaporator 15 and the refrigerant evaporation pressure in the chiller 19 become appropriate values.

[0320] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the defrosting mode of the first embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0321] Therefore, in the refrigeration cycle apparatus 10a in the waste heat defrost mode, the water-refrigerant heat exchanger 12a and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 15 and the chiller 19 function as evaporators, forming a vapor compression refrigeration cycle.

[0322] In the refrigeration cycle apparatus 10a in the waste heat defrosting 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. The low-temperature side heat medium is cooled in the chiller 19. Furthermore, in the outdoor heat exchanger 16, the frost on the outdoor heat exchanger 16 is melted and removed by the heat of the refrigerant flowing out from the indoor condenser 12. That is, the outdoor heat exchanger 16 is defrosted.

[0323] 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.

[0324] 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 coolant passage 80a of the battery 80. As a result, the battery 80 is cooled.

[0325] In addition, the interior air conditioning unit 30 in the waste heat defrost mode realizes dehumidification and heating of the vehicle cabin, similar to the single defrost mode. In the waste heat defrost mode, the amount of heat of the blown air in the heater core 42 is reduced compared to the cooling, dehumidification and heating mode, but the dehumidification and heating of the vehicle cabin can be continued, similar to the single defrost mode, etc.

[0326] As described above, according to the vehicle air conditioner 1a of this embodiment, by switching the operation mode, it is possible to realize comfortable air conditioning in the vehicle cabin and appropriate cooling of heat-generating devices.

[0327] Furthermore, in the vehicle air conditioner 1a of this embodiment, the desiccant material 15a is applied to the interior evaporator 15, so that the same effect as in the first embodiment can be obtained. That is, according to the vehicle air conditioner 1a of this embodiment, the refrigerating machine oil can be appropriately returned to the compressor 11 regardless of the operation mode switched to, while obtaining the effect of improving the operation efficiency by including the interior evaporator 15 to which the desiccant material 15a is applied.

[0328] The vehicle air conditioner 1a of this embodiment is also provided 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.

[0329] 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 etc. 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.

[0330] The vehicle air conditioner 1b includes 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.

[0331] 12 and 13, for clarity of illustration, the indoor air conditioning unit 30 is omitted. Therefore, the indoor evaporator 15 of the refrigeration cycle apparatus 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.

[0332] In the refrigeration cycle apparatus 10b, the accumulator 21 is eliminated and a receiver 23 is adopted. The receiver 23 is a high-pressure side gas-liquid separator that separates the high-pressure refrigerant flowing out from the heat exchanger functioning as a condenser into gas and liquid. The receiver 23 allows a part of the separated liquid-phase refrigerant to flow downstream and stores the remaining liquid-phase refrigerant as surplus refrigerant for the cycle.

[0333] One outlet of the first three-way joint 17a of the refrigeration cycle device 10b is connected to the inlet side of the heating expansion valve 14c via the first high pressure on-off valve 13c and the fifth three-way joint 17e. The other outlet of the first three-way joint 17a is connected to the inlet side of the receiver 23 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.

[0334] 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 an outlet side passage 22d. A sixth three-way joint 17f and a second check valve 18b are disposed 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.

[0335] 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.

[0336] The basic configurations of the fifth three-way joint 17e and the sixth three-way joint 17f are similar to those of the first three-way joint 17a, etc. The basic configurations of the first high pressure on-off valve 13c and the second high pressure on-off valve 13d are similar to those 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 similar to that of the check valve 18 described in the first embodiment.

[0337] In this embodiment, for the sake of clarity, the check valve 18 described in the first embodiment will be referred to as a first check valve 18a. The rest of the configuration of the vehicle air conditioner 1b is similar to that of the vehicle air conditioner 1a described in the second embodiment.

[0338] 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.

[0339] (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.

[0340] Therefore, in the refrigeration cycle apparatus 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.

[0341] 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.

[0342] The control signals to be output to the other controlled devices are determined in the same manner as in the single cooling mode of the second embodiment. Then, the control device 60 outputs the control signals 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.

[0343] Furthermore, in the refrigeration cycle device 10b in the single cooling mode, the surplus refrigerant of the cycle is stored in the receiver 23, so that the refrigerant on the outlet side of the indoor evaporator 15 can 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 surplus refrigerant of the cycle is stored in an accumulator.

[0344] (a-2) 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 sets the heating expansion valve 14c in a fully open state, the cooling expansion valve 14d in a throttled state, and the cooling expansion valve 14e in a throttled state.

[0345] 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 opened, 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 control 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 opened, 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 control valve 20, and the intake port of the compressor 11.

[0346] That is, in the refrigeration cycle apparatus 10b in the cooling / air-cooling mode, the refrigerant circuit is switched to one in which the indoor evaporator 15 and the chiller 19 are connected in parallel with respect to the refrigerant flow, similarly to the second embodiment.

[0347] 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 superheat degree of the refrigerant on the outlet side of the indoor evaporator 15 approaches a target superheat degree. Also, the control signal to be output to the cooling expansion valve 14e is determined by the control device 60 so that the superheat degree of the refrigerant on the outlet side of the chiller 19 approaches a target superheat degree.

[0348] The control signals to be output to the other controlled devices are determined in the same manner as in the cooling / air-cooling mode of the second embodiment. Then, the control device 60 outputs the control signals determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b in the cooling / air-cooling mode, the battery 80 can be cooled and the interior of the vehicle can be cooled, in the same manner as in the second embodiment.

[0349] Furthermore, in the refrigeration cycle apparatus 10b in the cooling / air-cooling 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, similarly to the single cooling mode, the amount of heat absorbed by the refrigerant in the indoor evaporator 15 can be increased to improve the cooling capacity of the blown air. 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.

[0350] (b-1) Single dehumidification and heating mode In the adsorption 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 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.

[0351] 13, the refrigerant discharged from the compressor 11 circulates in the order of 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 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 passage 22c, the receiver 23, the sixth three-way joint 17f of the outlet passage 22d, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure control valve 20, and the suction port of the compressor 11.

[0352] That is, in the refrigeration cycle device 10b in the adsorption process in 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 with respect to the refrigerant flow, as in the second embodiment.

[0353] Furthermore, the control device 60 appropriately determines 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 superheat degree of the refrigerant on the outlet side of the outdoor heat exchanger 16 approaches a target superheat degree. Also, the control signal to be output to the cooling expansion valve 14d is determined by the control device 60 so that the superheat degree of the refrigerant on the outlet side of the indoor evaporator 15 approaches a target superheat degree.

[0354] The control signals to be output to the other controlled devices are determined in the same manner as in the adsorption process of the single dehumidification heating mode of the second embodiment. Then, the control device 60 outputs the control signals determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b in 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.

[0355] Furthermore, in the refrigeration cycle device 10b in the adsorption stroke in the single dehumidification and 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, thereby 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, thereby improving the cooling capacity of the blown air.

[0356] Next, in the desorption 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 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.

[0357] Therefore, in the refrigeration cycle apparatus 10b during the desorption stroke in the single dehumidification and 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 suction port of compressor 11.

[0358] Furthermore, the control device 60 appropriately determines the control signals to be output to various controlled devices, similarly to the desorption process in the single dehumidification and heating mode in the second embodiment.

[0359] Therefore, in the refrigeration cycle device 10b in the desorption process in the single dehumidification heating mode, the water-refrigerant heat exchanger 12a and the indoor evaporator 15 function as a radiator to configure a hot gas cycle. Furthermore, in the refrigeration cycle device 10b 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.

[0360] Therefore, in the vehicle air conditioner 1b in the desorption process of the single dehumidification and heating mode, the desiccant material 15a can be regenerated and the vehicle interior can be heated, similarly to the desorption process of the single dehumidification and heating mode in the second embodiment.

[0361] (b-2) Cooling, dehumidifying and heating mode In the adsorption 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 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.

[0362] 13, the refrigerant discharged from the compressor 11 circulates in the order of 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 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 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 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 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 14e, the chiller 19, the evaporation pressure control valve 20, and the suction port of the compressor 11, in that order.

[0363] That is, in the refrigeration cycle device 10b in the adsorption process of the cooling, dehumidifying and 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 with respect to the refrigerant flow, as in the second embodiment.

[0364] 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 a target degree of superheat.

[0365] In addition, the control signal output to the cooling expansion valve 14d is determined by the control device 60 so that the superheat degree of the refrigerant on the outlet side of the indoor evaporator 15 approaches the target superheat degree. In addition, the control signal output to the cooling expansion valve 14e is determined by the control device 60 so that the superheat degree of the refrigerant on the outlet side of the chiller 19 approaches the target superheat degree.

[0366] The control signals 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 second embodiment. Then, the control device 60 outputs the control signals determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b in the adsorption process of the cooling, dehumidifying and heating mode, the battery 80 can be cooled and the vehicle interior can be dehumidified and heated in the same manner as in the second embodiment.

[0367] 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.

[0368] 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.

[0369] 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.

[0370] Therefore, in the refrigeration cycle device 10b in the desorption process in the cooling, dehumidifying and heating mode, as shown by the hatched arrows in FIG. 13, the refrigerant circulates in the refrigerant circuit in the same order as in the desorption process in the single dehumidifying and heating mode.

[0371] 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 and heating mode of the second embodiment. Therefore, in the vehicle air conditioner 1b in the desorption process in 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.

[0372] (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 refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the single cooling mode.

[0373] 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.

[0374] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the single defrost mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b in the single defrost mode, it is possible to continue defrosting the exterior heat exchanger 16 and dehumidifying and heating the vehicle cabin in the same manner as in the second embodiment.

[0375] (c-2) Waste heat defrost mode In the waste heat 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 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 defrost mode, as shown by the black arrows in Fig. 12, the refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the single cooling mode.

[0376] 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 superheat degree of the refrigerant on the outlet side of the indoor evaporator 15 approaches a target superheat degree. Also, the control signal to be output to the cooling expansion valve 14e is determined by the control device 60 so that the superheat degree of the refrigerant on the outlet side of the chiller 19 approaches a target superheat degree.

[0377] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the waste heat defrost mode of the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices. Therefore, in the vehicle air conditioner 1b in the waste heat defrost mode, it is possible to continue cooling the battery 80, defrosting the exterior heat exchanger 16, and dehumidifying and heating the vehicle interior, in the same manner as in the second embodiment.

[0378] As described above, according to the vehicle air conditioner 1b of this embodiment, by switching the operation mode, it is possible to realize comfortable air conditioning in the vehicle cabin and appropriate cooling of heat-generating devices.

[0379] Furthermore, the vehicle air conditioner 1b of this embodiment can also provide 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 provides an improved operating efficiency, and the refrigerating machine oil can be appropriately returned to the compressor 11 regardless of the operation mode.

[0380] In addition, in the refrigeration cycle device 10b of the present embodiment, the refrigerant at the outlet side of the heat exchanger functioning as an evaporator can be made to have a degree of superheat, so that the amount of heat absorbed by the refrigerant in the heat exchanger functioning as an evaporator can be increased, thereby improving the coefficient of performance of the refrigeration cycle device 10b and further improving the operating efficiency of the vehicle air conditioner 1b.

[0381] (Fourth embodiment) In this embodiment, a description will be given of a vehicle air conditioner 1c shown in the overall configuration diagrams of Figures 14 to 19. The vehicle air conditioner 1c is an air conditioner with a heat-generating device cooling function, similar to the vehicle air conditioner 1a etc. described in the second embodiment.

[0382] The vehicle air conditioner 1c includes 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.

[0383] 14 to 19, in the same manner as in the third embodiment, the indoor air conditioning unit 30 is omitted from illustration for clarity of illustration. Therefore, the indoor evaporator 15 of the refrigeration cycle apparatus 10c 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 40a is disposed in the casing 31 of the indoor air conditioning unit 30.

[0384] In the refrigeration cycle apparatus 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 apparatus 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 apparatus 10c, the fourth three-way joint 17d serves as a branching part.

[0385] One of the outlets of the fourth three-way joint 17d is connected to the inlet side of the cooling expansion valve 14d similar to that of the second embodiment. The cooling expansion valve 14d of the present embodiment is an air cooling pressure reducing part that reduces the pressure of one of the refrigerants branched at the fourth three-way joint 17d.

[0386] The outlet of the cooling expansion valve 14d is connected to the refrigerant inlet side of the indoor evaporator 15 similar to that of the first embodiment. The indoor evaporator 15 of this embodiment is an air-cooling heat exchanger that evaporates the refrigerant decompressed by the cooling expansion valve 14d to cool the blown air.

[0387] The other outlet of the fourth three-way joint 17d is connected to the inlet side of the cooling expansion valve 14e similar to that of the second embodiment. The cooling expansion valve 14e of the present embodiment is a cooling pressure reducing part that reduces the pressure of the other refrigerant branched at the fourth three-way joint 17d.

[0388] An outlet of the cooling expansion valve 14e is connected to an inlet side of a refrigerant passage of a chiller 19 similar to that of the second embodiment. The chiller 19 of the present embodiment is a cooling heat exchanger that exchanges heat between the refrigerant decompressed by the cooling expansion valve 14e and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50a.

[0389] The inlet side of an evaporation pressure regulating valve 20 is connected to a refrigerant outlet of the indoor evaporator 15 and an 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 apparatus 10c is similar to that of the refrigeration cycle apparatus 10a described in the second embodiment.

[0390] 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.

[0391] In the high-temperature side heat medium circuit 40a, the outlet of the water passage of the water-refrigerant heat exchanger 12a is connected to the inlet side of the high-temperature side three-way valve 43. 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.

[0392] The high-temperature side three-way valve 43 can also cause 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.

[0393] 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 chamber, 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.

[0394] 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, etc. 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 port side of the high-temperature side heat medium pump 41 is connected to the outlet of the high-temperature side junction 45.

[0395] 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 addition to the low-temperature side heat medium circuit 50 described in the second embodiment.

[0396] In the low-temperature side heat medium circuit 50a, the inlet side of the low-temperature side three-way valve 53 is connected to the outlet of the water passage of the chiller 19. The low-temperature side three-way valve 53 is a three-way flow control valve that can continuously adjust the flow rate of the low-temperature side heat medium flowing out from the chiller 19 to the low-temperature side 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.

[0397] The basic configuration of the low-temperature side three-way valve 53 is similar to that of the high-temperature side three-way valve 43. The low-temperature side three-way valve 53 can also cause the low-temperature side heat medium flowing out from 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.

[0398] 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 disposed on the front side of the drive unit chamber, downstream of the outdoor air flow of the high-temperature side radiator 44.

[0399] Therefore, the low-temperature side radiator 54 exchanges heat between the low-temperature side heat medium and the outside air that has passed through the high-temperature side radiator 44. Furthermore, the high-temperature side radiator 44 and the low-temperature side radiator 54 of this embodiment are integrated to enable heat transfer between the high-temperature side heat medium and the low-temperature side heat medium.

[0400] Specifically, in the high-temperature side radiator 44 and the low-temperature side radiator 54 of this embodiment, some of the components (heat exchange fins in this embodiment) are formed from common materials. Heat from the high-temperature side heat medium and the low-temperature side heat medium can be transferred between them via the common components. This allows, for example, the heat from the high-temperature side heat medium flowing through the high-temperature side radiator 44 to be transferred to the low-temperature side radiator 54.

[0401] The high-temperature side three-way valve 43 of the high-temperature side heat medium circuit 40a can adjust the heat medium flow rate supplied to the heater core 42 and the heat medium flow rate 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.

[0402] 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.

[0403] Next, an overview of the electrical control unit of the vehicle air conditioner 1c will be described with reference to 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.

[0404] Other configurations of the vehicle air conditioner 1c are similar to those of the vehicle air conditioner 1a described in the second embodiment.

[0405] 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.

[0406] (a-1) Single cooling mode In the single cooling mode, the control device 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.

[0407] Therefore, in the refrigeration cycle apparatus 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.

[0408] 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. Moreover, 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.

[0409] 14, the controller 60 determines 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 both the high-temperature side radiator 44 and the heater core 42. Furthermore, in the single cooling mode, the controller 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.

[0410] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the single cooling mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0411] 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 type 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.

[0412] 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.

[0413] In the interior air conditioning unit 30 in the single cooling mode, the temperature of the blown air is adjusted and the blown air is blown out to an appropriate location in the vehicle cabin, as in the single cooling mode of the third embodiment, thereby realizing cooling of the vehicle cabin.

[0414] (a-2) Cooling mode In the cooling / cooling mode, the control device 60 puts the cooling expansion valve 14d in a throttled state and the cooling expansion valve 14e in a throttled state.

[0415] 15, the refrigerant discharged from the compressor 11 circulates through the water-refrigerant heat exchanger 12a, the receiver 23, the cooling expansion valve 14d, the indoor evaporator 15, the evaporation pressure control valve 20, and the suction port of the compressor 11 in that order. At the same time, the refrigerant is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates through the water-refrigerant heat exchanger 12a, the receiver 23, 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.

[0416] That is, in the refrigeration cycle apparatus 10c in the cooling / air-cooling mode, the refrigerant circuit is switched to one in which the indoor evaporator 15 and the chiller 19 are connected in parallel with respect to the refrigerant flow.

[0417] 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.

[0418] 15, the controller 60 determines the high-temperature side three-way valve 43 to be a heat medium circuit in which the high-temperature side heat medium flowing out of the water-refrigerant heat exchanger 12a flows into both the high-temperature side radiator 44 and the heater core 42. Furthermore, in the cooling / cooling mode, the controller 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.

[0419] Furthermore, 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.

[0420] In addition, with regard to 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 in which it flows into the coolant passage 80a of the battery 80, as shown by the dashed arrow in FIG. 15.

[0421] The control signals to be output to the other controlled devices are determined in the same manner as in the cooling / air-cooling mode of the third embodiment. Then, the control device 60 outputs the control signals determined as described above to the various controlled devices.

[0422] 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 the 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.

[0423] In the high-temperature side heat medium circuit 40a in the sole 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.

[0424] In the low-temperature side heat medium circuit 50a 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 into the cooling water passage 80a of the battery 80. The low-temperature side heat medium that has flowed into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. As a result, the battery 80 is cooled.

[0425] In the interior air conditioning unit 30 in the cooling / cooling mode, the temperature of the blown air is adjusted and the air is blown out to an appropriate location in the vehicle cabin, as in the cooling / cooling mode of the third embodiment, thereby realizing cooling of the vehicle cabin.

[0426] (b-1) Single dehumidification and heating mode In the adsorption process of the single dehumidification and heating 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 adsorption process of the single dehumidification 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.

[0427] 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.

[0428] 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 arrows in Figure 16.

[0429] Furthermore, 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.

[0430] In addition, 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 Figure 16.

[0431] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the adsorption process in the single dehumidification and heating mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0432] Therefore, in the refrigeration cycle apparatus 10c in the adsorption stroke in the single dehumidification and 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 to 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.

[0433] One of the refrigerant branches off at the fourth three-way joint 17d is decompressed by the cooling expansion valve 14d (from point b21 to point e21 in FIG. 21) and flows into the indoor evaporator 15. The refrigerant that has flowed into the indoor evaporator 15 exchanges heat with the blown air and evaporates (from point e21 to point f21 in FIG. 21).

[0434] The other refrigerant branched off at the fourth three-way joint 17d is decompressed by the cooling expansion valve 14e (from point b21 to point c21 in FIG. 21) and flows into the chiller 19. The refrigerant that has flowed into the chiller 19 exchanges heat with the low-temperature side heat medium and evaporates (from point c21 to point d21 in FIG. 21).

[0435] The refrigerant flowing out from the cooling expansion valve 14d and the refrigerant flowing out from the chiller 19 are adjusted to the same pressure by the evaporation pressure regulating valve 20 and merge at the merging point 17g. The refrigerant flowing out from the merging 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 g21 to point a21 in FIG. 21).

[0436] That is, in the refrigeration cycle device 10c in the adsorption stroke of the single dehumidification heating mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and the chiller 19 function as evaporators to configure a vapor compression refrigeration cycle. Note that, although an example in which the refrigerant evaporation pressure in the indoor evaporator 15 is higher than the refrigerant pressure in the chiller 19 has been described in Fig. 21, the refrigerant evaporation pressure in the indoor evaporator 15 may be lower than the refrigerant pressure in the chiller 19.

[0437] In the refrigeration cycle device 10c in the adsorption process in 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.

[0438] In the high-temperature side heat medium circuit 40a during the adsorption stroke in the single dehumidification and 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.

[0439] In the low-temperature side heat medium circuit 50a during the adsorption process in the single dehumidification 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. The low-temperature side heat medium that has flowed into the low-temperature side radiator 54 exchanges heat with the outside air and absorbs heat from the outside air.

[0440] In the interior air conditioning unit 30 in the adsorption process in the single dehumidification and heating mode, the temperature of the blown air is adjusted and the air is blown out to an appropriate location in the vehicle cabin, as in the adsorption process in the single dehumidification and heating mode of the second embodiment, as shown by the dashed arrow in the Mollier diagram of Fig. 21. Therefore, in the vehicle air conditioning device 1c in the adsorption process in the single dehumidification and heating mode, the adsorption action of the desiccant material 15a can be used to dehumidify and heat the vehicle cabin, as in the second embodiment.

[0441] 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 refrigerant circuit is switched to one in which the refrigerant circulates, as shown by the outline arrow in FIG.

[0442] 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.

[0443] 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 arrows in Figure 17.

[0444] Furthermore, with regard to 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.

[0445] The control signals and the like 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 in the second embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0446] Therefore, in the refrigeration cycle apparatus 10c in the desorption process in the single dehumidification and heating mode, the refrigerant discharged from the compressor 11 (point a22 in FIG. 22) flows into the water-refrigerant heat exchanger 12a as shown in the Mollier diagram of FIG. 22. 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 to point b22 in FIG. 22).

[0447] The refrigerant flowing out of the water-refrigerant heat exchanger 12a flows through the receiver 23 into the cooling expansion valve 14d and is reduced in pressure (point b22 to point c22 in FIG. 22). The refrigerant reduced in pressure by the cooling expansion valve 14d flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 dissipates heat to the outside air and the desiccant material 15a (point c22 to point d22 in FIG. 22).

[0448] 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).

[0449] That is, in the refrigeration cycle apparatus 10c in the desorption process in the single dehumidification heating mode, the water-refrigerant heat exchanger 12a and the indoor evaporator 15 function as a radiator to configure a hot gas cycle. In the refrigeration cycle apparatus 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 apparatus 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.

[0450] In the high-temperature side heat medium circuit 40a during the desorption process in the single dehumidification and 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.

[0451] In the interior air conditioning unit 30 in the desorption process of 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 interior blower 32 passes through the interior evaporator 15 and is humidified, as in the second embodiment. This regenerates the desiccant material 15a. The outside air humidified by passing through the interior evaporator 15 is exhausted to the outside of the vehicle compartment from the exhaust port 31b of the exhaust device 38.

[0452] Another part of the outside air blown from the interior blower 32 flows through the outside air bypass passage 35c and the auxiliary outside air inlet 31a into the heating passage 35a. The outside air that has flowed into the heating passage 35a is heated by the heater core 42 as blown air and is blown out into the vehicle cabin. This makes it possible to heat the vehicle cabin even during the desorption process in the single dehumidification and heating mode.

[0453] (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, the refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the cooling and air-conditioning mode, as shown by the black arrows in FIG.

[0454] 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.

[0455] 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 arrows in Figure 18.

[0456] Furthermore, 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.

[0457] In addition, 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 Figure 18.

[0458] In addition, 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.

[0459] The control signals to be output to the other controlled devices are determined in the same manner as in the adsorption process in the cooling, dehumidifying and heating mode of the third embodiment. Then, the control device 60 outputs the control signals determined as described above to the various controlled devices.

[0460] 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 the chiller 19 function as evaporators, forming a vapor compression refrigeration cycle.

[0461] 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.

[0462] In the adsorption process of the cooling / dehumidifying / heating mode, the high-temperature side heat medium pumped from the high-temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12a in the high-temperature side heat medium circuit 40a. The high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a flows into the heater core 42.

[0463] In the low-temperature side heat medium circuit 50a during the adsorption process in the cooling / dehumidifying / heating mode, the low-temperature side heat medium pumped from the low-temperature side heat medium pump 51 flows into the chiller 19. The low-temperature side heat medium cooled in the chiller 19 flows into the low-temperature side radiator 54 and the coolant passage 80a of the battery 80.

[0464] 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. The low-temperature side heat medium that flows into the coolant passage 80a of the battery 80 absorbs heat from the battery 80. This causes the battery 80 to be cooled.

[0465] In the interior air conditioning unit 30 in the adsorption process of the cooling / dehumidifying / heating mode, the temperature of the blown air is adjusted and the air is blown out to an appropriate location in the vehicle cabin, as in the adsorption process of the single dehumidifying / heating mode. Therefore, the vehicle air conditioner 1c in the adsorption process of the single dehumidifying / heating mode can dehumidify and heat the vehicle cabin by utilizing the adsorption action of the desiccant material 15a.

[0466] 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, the refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the single dehumidifying and heating mode, as shown by the white arrows in FIG.

[0467] 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.

[0468] 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 arrows in Figure 19.

[0469] Furthermore, 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.

[0470] In addition, with regard to 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 in which it flows into the coolant passage 80a of the battery 80, as shown by the dashed arrow in FIG. 19.

[0471] Therefore, in the refrigeration cycle apparatus 10c in the desorption process of 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, as in the desorption process of the single dehumidifying / heating mode. In the refrigeration cycle apparatus 10a in the desorption process, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12c.

[0472] 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.

[0473] 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.

[0474] In the desorption process of the cooling, dehumidifying and heating mode, the interior air conditioning unit 30 regenerates the desiccant material 15a of the interior evaporator 15 in the same manner as in the desorption process of the single dehumidifying and heating mode. The outside air that has been humidified while passing through the interior evaporator 15 is exhausted from the exhaust port 31b of the exhaust device 38 to the outside of the vehicle compartment.

[0475] Furthermore, the outside air that has flowed into the heating passage 35a via the outside air bypass passage 35c is heated by heat exchange with the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12a when passing through the heater core 42 as blown air, and is then blown into the vehicle cabin. This allows the vehicle cabin to be heated even during the desorption process in the cooling / dehumidifying / heating mode.

[0476] (c) Defrost 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.

[0477] (c-1) Single defrost mode In the single defrosting 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, the refrigerant circuit is switched to one in which the refrigerant circulates in the same order as in the single cooling mode, as shown by the white arrows in FIG.

[0478] Furthermore, the control device 60 appropriately determines the control signals to be output to 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.

[0479] As for high-temperature side three-way valve 43, controller 60 determines, as in the single cooling mode, that the high-temperature side heat medium flowing out of water-refrigerant heat exchanger 12a forms a heat medium circuit in which it flows into both high-temperature side radiator 44 and heater core 42, as shown by the solid arrows in Fig. 14. Therefore, high-temperature side three-way valve 43, which is a heat quantity distributor, increases the flow rate of the high-temperature side heat medium flowing into high-temperature side radiator 44 in the single defrost mode compared to the single dehumidification heating mode.

[0480] As described above, in this embodiment, the high-temperature side radiator 44 and the low-temperature side radiator 54 are integrated so as to transfer heat of the high-temperature side heat medium 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.

[0481] The control signals and the like to be output to the other controlled devices are determined in the same manner as in the single defrosting mode of the third embodiment. Then, the control device 60 outputs the control signals and the like determined as described above to the various controlled devices.

[0482] Therefore, in the refrigeration cycle apparatus 10c in the single defrost mode, the refrigerant discharged from the compressor 11 (point a23 in FIG. 23) flows into the water-refrigerant heat exchanger 12a as shown in the Mollier diagram of FIG. 23. The refrigerant that flows into the water-refrigerant heat exchanger 12a exchanges heat with the high-temperature side heat medium and condenses (point a23 to point b23 in FIG. 23).

[0483] The refrigerant flowing out from 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 flowing into the indoor evaporator 15 exchanges heat with the blown air and evaporates (point d23→point e23 in FIG. 23). The refrigerant flowing out from the indoor evaporator 15 is drawn into the compressor 11 via the accumulator 21 and compressed again (point f23→point a23 in FIG. 23).

[0484] That is, in the refrigeration cycle apparatus 10c in the single defrosting 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 apparatus 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.

[0485] 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.

[0486] The heat of the high-temperature side heat medium that has flowed into the high-temperature side radiator 44 is transferred to the integrated low-temperature side radiator 54. As a result, the frost on the low-temperature side radiator 54 is melted and removed. In other words, the low-temperature side radiator 54 is defrosted.

[0487] In the interior air conditioning unit 30 in the single defrost mode, as shown by the dashed arrows in the Mollier diagram of Fig. 23, the blown air cooled and dehumidified in the interior evaporator 15 is reheated using the heat radiated by the refrigerant in the water-refrigerant heat exchanger 12a as a heat source when passing through the heater core 42. Therefore, the dehumidification and heating of the vehicle interior can be continued.

[0488] (c-2) Waste heat defrost 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.

[0489] Furthermore, the control device 60 appropriately determines the control signals to be output to 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-cooling mode.

[0490] As for high-temperature side three-way valve 43, controller 60 determines, as in the cooling / air-conditioning mode, a heat medium circuit in which the high-temperature side heat medium flowing out of water-refrigerant heat exchanger 12a flows into both high-temperature side radiator 44 and heater core 42, as shown by the solid arrows in Fig. 15. Therefore, in the waste heat defrost mode, high-temperature side three-way valve 43 increases the flow rate of the high-temperature side heat medium flowing into high-temperature side radiator 44 more than in the cooling / dehumidification / heating mode.

[0491] In addition, with regard to the low-temperature side three-way valve 53, the control device 60 determines that, as in the cooling / air-conditioning mode, a heat medium circuit will be formed in which the low-temperature side heat medium flowing out of the chiller 19 flows into the cooling water passage 80a of the battery 80, as shown by the dashed arrow in Figure 15.

[0492] The control signals and the like 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 and the like determined as described above to the various controlled devices.

[0493] Therefore, in the refrigeration cycle apparatus 10c in the waste heat defrosting mode, the water-refrigerant heat exchanger 12a functions as a condenser, and the indoor evaporator 15 and the chiller 19 function as evaporators to configure a vapor compression refrigeration cycle. In the refrigeration cycle apparatus 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.

[0494] 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.

[0495] The heat of the high-temperature side heat medium that has flowed into the high-temperature side radiator 44 is transferred to the integrated low-temperature side radiator 54. As a result, the frost on the low-temperature side radiator 54 is melted and removed. In other words, the low-temperature side radiator 54 is defrosted.

[0496] 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 has flowed into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. As a result, the battery 80 is cooled.

[0497] In addition, in the indoor air conditioning unit 30 in the single defrost mode, as in the waste heat defrost mode of the third embodiment, the blown air that has been cooled and dehumidified in the indoor evaporator 15 is reheated in the heater core 42, thereby making it possible to continue dehumidifying and heating the vehicle cabin.

[0498] As described above, according to the vehicle air conditioner 1c of this embodiment, by switching the operation mode, it is possible to realize comfortable air conditioning in the vehicle cabin and appropriate cooling of heat-generating devices.

[0499] 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.

[0500] In addition, in the defrost mode, the flow rate of the high-temperature side heat medium that is caused to flow into the high-temperature side radiator 44 by the high-temperature side three-way valve 43 is increased compared to the dehumidification heating mode. That is, 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.

[0501] 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 refrigerating machine oil can be appropriately returned to the compressor 11, a decrease in the temperature of the space to be air-conditioned can be suppressed.

[0502] Therefore, according to the vehicle air conditioner 1c of this embodiment, it is possible to obtain the same effect as the vehicle air conditioner 1 described in the first embodiment. That is, while obtaining the effect of improving the operating efficiency by providing the interior evaporator 15 to which the desiccant material 15a is applied, it is possible to appropriately return refrigerating machine oil to the compressor 11 regardless of the operation mode.

[0503] Moreover, the vehicle air conditioner 1c of this embodiment includes a coolant passage 80a for the battery 80 as a heat medium device heat exchanger. This allows the battery 80 to be cooled.

[0504] 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 allows the waste heat of the battery 80 to be used as a heat source for defrosting the outdoor 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.

[0505] (1) In the above embodiment, the air conditioner according to the present invention is applied to the 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.

[0506] In addition, in the vehicle air conditioners 1a to 1c, the battery 70 has been cooled as a heat-generating device, but the invention is not limited to this. For example, the vehicle air conditioners may cool in-vehicle devices that generate heat during operation, such as an electric motor for outputting driving force for driving, an inverter for supplying power to the electric motor, a transaxle as a power transmission mechanism, and a control device for an advanced driving assistance system. Use If so, other heat-generating equipment may be cooled.

[0507] (2) The operation 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 the vehicle air conditioners 1 to 1c can switch between at least the dehumidification heating mode and the defrosting mode described in each embodiment. That is, 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.

[0508] Therefore, the vehicle air conditioners 1 to 1c may be capable of executing another operation mode. For example, the vehicle air conditioner 1a described in the second embodiment may execute a serial dehumidification heating mode as another dehumidification heating mode.

[0509] 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 may be controlled in the same manner as in the dehumidifying and heating mode. Therefore, in the series 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 with respect to the refrigerant flow.

[0510] For example, the vehicle air conditioner 1a described in the second embodiment may further execute a heating mode. In the heating mode, the heated air is blown into the vehicle interior without being cooled and dehumidified by the interior evaporator 15.

[0511] 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 may be controlled in the same manner as in the cooling mode. In this way, the ventilation air heated by the heater core 42 is blown into the vehicle cabin, thereby heating the vehicle cabin.

[0512] Also, for example, the vehicle air conditioner 1b described in the third embodiment may execute the heating mode.

[0513] 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 manner as in the cooling mode. This allows the interior of the vehicle to be heated by blowing the blown air heated by the heater core 42 into the vehicle interior.

[0514] Also, for example, the vehicle air conditioner 1c described in the fourth embodiment may execute the heating mode.

[0515] Specifically, the cooling expansion valve 14d of the refrigeration cycle apparatus 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.

[0516] According to this, the ventilation air heated by the heater core 42 is blown into the vehicle compartment, thereby realizing heating of the vehicle compartment.

[0517] In the vehicle air conditioners 1a to 1c described in the second to fourth embodiments, defrosting may be performed using only waste heat from a heat generating device as a heat source. Specifically, the cooling expansion valve 14d may be fully closed in the waste heat defrosting mode.

[0518] (3) The execution conditions for executing each operation mode, or the switching conditions for switching the operation mode, are not limited to those disclosed in the above-described embodiment.

[0519] For example, when the time Tmf2 during which the outdoor air temperature Tam is continuously equal to or lower than the reference frosting outdoor air temperature Ktamf during execution of the dehumidifying heating mode becomes equal to or higher than the reference frosting time KTmf, it may be determined that the frosting condition is satisfied. For example, when the outdoor unit temperature Tout becomes equal to or higher than a predetermined reference defrosting temperature KToutdf during execution of the defrosting mode, it may be determined that the termination condition is satisfied.

[0520] 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 operation 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.

[0521] 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.

[0522] (4) The configurations of the refrigeration cycle devices 10, 10a to 10c are not limited to those disclosed in the above-described embodiments.

[0523] In the refrigeration cycle device 10, an example in which the four-way valve 13 is used as the refrigerant circuit switching unit has been described, but the present invention is not limited to this. For example, the refrigerant circuit switching unit may be formed by combining a plurality of (e.g., four) on-off valves.

[0524] In the refrigeration cycle devices 10a to 10c, an example has been described in which the evaporation pressure regulating valve 20 is used as the pressure regulating unit, but the present invention is not limited to this. For example, a mechanical evaporation pressure regulating valve that maintains the refrigerant pressure at or above the evaporation pressure of the refrigerant in the indoor evaporator 15 may be disposed in the refrigerant flow path extending from the refrigerant outlet of the indoor evaporator 15 to the junction 17g. As the mechanical evaporation pressure regulating valve, a variable throttle mechanism that increases the valve opening degree as the refrigerant pressure on the refrigerant outlet side of the indoor evaporator 15 increases can be used.

[0525] In the above embodiment, the refrigerant is R1234yf, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be used. Alternatively, a mixed refrigerant made by mixing a plurality of these refrigerants 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.

[0526] In the adsorption stroke of the dehumidifying and heating mode in the above embodiment, the operation of the inside / outside air switching device 33 is controlled to fully open the inside air inlet and fully close the outside air inlet, but the present invention is not limited to this. In the adsorption stroke, the operation of the inside / outside air switching device 33 may be controlled so that the ratio of inside air to the blown air flowing into the indoor evaporator 15 is greater than the ratio of outside air.

[0527] Similarly, in the desorption stroke of the dehumidifying and heating mode, the operation of the inside / outside air switching device 33 is controlled to fully close the inside air inlet and fully open the outside air inlet, but the present invention is not limited to this. In the desorption stroke, 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.

[0528] In addition, in the cooling mode and the defrost mode, the operation of the inside / outside air switching device 33 is controlled to fully close the inside air inlet and fully open the outside air inlet, but the present invention is not limited to this. In the cooling mode and the defrost mode, the operation of the inside / outside air switching device 33 may be controlled so that the ratio of outside air in the blown air flowing into the indoor evaporator 15 is greater than the ratio of inside air.

[0529] 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 the outside air may be introduced directly from the auxiliary outside air inlet 31a. In this case, it is preferable to provide a dedicated auxiliary outside air blower for causing the outside air to flow into the auxiliary outside air inlet 31a. Then, when the control device 60 opens the auxiliary outside air inlet 31a, the auxiliary outside air blower may be operated.

[0530] (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 embodiment. For example, an electric heater may be provided in the high-temperature side heat medium circuit 40 as an auxiliary heat source for heating the high-temperature side heat medium.

[0531] Also, a bypass passage for causing the high-temperature side heat medium to flow around the heater core 42 may be provided in the high-temperature side heat medium circuit 40, 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 be used as the heat amount adjustment unit.

[0532] 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, an antifreeze, an aqueous liquid refrigerant containing alcohol, or a liquid medium containing oil may be used.

[0533] (7) Furthermore, the means disclosed in each of the above embodiments may be combined as appropriate within the scope of feasibility.

[0534] 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. [Explanation of symbols]

[0535] 1 to 1c... vehicle air conditioning device, 10 to 10c... refrigeration cycle device, 11... compressor, 12... indoor condenser (heating section), 12a... water-refrigerant heat exchanger (heating section), 13...four-way valve (refrigerant circuit switching unit), 13a...high pressure on-off valve (refrigerant circuit switching unit), 13b...high pressure on-off valve (refrigerant circuit switching unit), 13c...first high pressure on-off valve (refrigerant circuit switching unit), 13d... second high pressure on-off valve (refrigerant circuit switching section), 14a...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 (heat exchange section for cooling), 15a... desiccant material (adsorption section), 16...Outdoor heat exchanger (outdoor heat exchange part), 17a, 17d: 1st and 4th three-way joints (branching section), 17g: junction section 19... Chiller (cooling heat exchanger), 20... Evaporation pressure regulating valve (pressure regulating section), 40, 40a... high temperature side heat medium circuit (heating unit), 50, 50a... low temperature side heat medium circuit

Claims

1. An air conditioning device for use in a vehicle, comprising: 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.

2. An air conditioning device for use in a vehicle, comprising: 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 portion (17a) for branching the flow of the refrigerant flowing out from the heating portion; 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.

3. 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.

4. An air conditioning device for use in a vehicle, comprising: 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.

5. 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.

6. 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.

7. 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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