air conditioning unit

Abstract

In the present invention, in a desorption heating mode in which a space to be air conditioned is heated and moisture adsorbed by an adsorption part (18a) of a refrigerant / air heat exchange part (18) is desorbed, refrigerant circuit switching parts (15a-15e) switch to a refrigerant circuit that causes a refrigerant flowing out from heating parts (12, 121, 30b) to circulate in the order of the refrigerant / air heat exchange part (18), outside air-side pressure reduction parts (14a, 14d), refrigerant / outside air heat exchange parts (16, 19a), and a suction port of a compressor (11). In an inside air adsorption heating mode in which the space to be air conditioned is heated and moisture is adsorbed to the adsorption part (18a), the refrigerant circuit switching parts (15a-15e) switch to a refrigerant circuit that causes the refrigerant flowing out from the heating parts (12, 121, 30b) to bypass the refrigerant / air heat exchange part (18) and circulate in the order of the outside air-side pressure reduction parts (14a, 14d), the refrigerant / outside air heat exchange parts (16, 19a), and the suction port of the compressor (11), and an air blowing part (52) blows inside air to the refrigerant / air heat exchange part (18).

Description

Cross-reference to Related Applications

[0001] This application is based on Japanese Patent Application No. 2023-082251 filed on May 18, 2023, the contents of which are incorporated herein by reference.

Technical Field

[0002] The present disclosure relates to an air conditioner including a heat exchange unit having an adsorption unit.

Background Art

[0003] Conventionally, Patent Document 1 discloses a vehicle air conditioner including a heat exchange unit having an adsorption unit. More specifically, in the vehicle air conditioner of Patent Document 1, as an indoor evaporator of a heat pump cycle device that adjusts the temperature of blown air blown into a vehicle interior, which is an air conditioning target space, a heat exchange unit having an adsorption unit that adsorbs moisture contained in the blown air is adopted.

[0004] Further, Patent Document 1 describes that, in a heating mode in which the vehicle interior is heated while dehumidifying the blown air, the refrigerant circuit of the heat pump cycle device is switched to a refrigerant circuit in which an indoor evaporator and an outdoor heat exchanger are connected in parallel with respect to the refrigerant flow. In the vehicle air conditioner of Patent Document 1, in the heating mode, the indoor condenser of the heat pump cycle device functions as a condenser, and the indoor evaporator and the outdoor heat exchanger function as evaporators.

[0005] Furthermore, in the vehicle air conditioner of Patent Document 1, in the heating mode, inner air that is hotter and more humid than the outside air is made to flow into the indoor evaporator. Then, moisture contained in the inner air is adsorbed by the adsorption unit in the indoor evaporator. Further, the blown air dehumidified in the indoor evaporator is reheated in the indoor condenser and blown into the vehicle interior. At this time, in the indoor condenser, heat that the refrigerant has absorbed from the outside air in the outdoor heat exchanger is released to the blown air to heat the blown air.

[0006] As a result, the vehicle air conditioning system described in Patent Document 1 aims to reduce the energy consumed to dehumidify the air being blown in and the energy consumed to heat the air being blown in during heating mode. [Prior art documents] [Patent Documents]

[0007] [Patent Document 1] Japanese Patent Publication No. 2022-51624 [Overview of the project]

[0008] By the way, in the vehicle air conditioning system described in Patent Document 1, during heating mode, the indoor evaporator and the outdoor heat exchanger are connected in parallel with the refrigerant flow, and low-pressure refrigerant is introduced into both the indoor evaporator and the outdoor heat exchanger. However, even if more low-temperature refrigerant is introduced into the indoor evaporator than necessary during heating mode, it is not possible to increase the amount of moisture adsorbed in the adsorption section, and on the contrary, it increases the power consumption of the compressor.

[0009] In other words, in the vehicle air conditioning system of Patent Document 1, if an excessive amount of low-temperature refrigerant is allowed to flow into the indoor evaporator during heating mode, it may become impossible to fully obtain the energy reduction effect provided by the heat exchange section having an adsorption section.

[0010] In view of the above, this disclosure aims to provide an air conditioning system equipped with a heat exchange section having an adsorption section, which can sufficiently reduce the energy consumed when heating a space to be air-conditioned while dehumidifying the blown air.

[0011] An air conditioning system according to a first aspect of the present disclosure comprises a compressor, a heating unit, a refrigerant air heat exchange unit, a refrigerant outside air heat exchange unit, an outside air side pressure reduction unit, a refrigerant circuit switching unit, and a blower unit.

[0012] The compressor compresses and discharges the refrigerant. The heating unit heats the air blown into the air-conditioned space using the refrigerant discharged from the compressor as a heat source. The refrigerant-air heat exchange unit exchanges heat between the refrigerant and the air blown into the space before it is heated in the heating unit. The refrigerant-air heat exchange unit has an adsorption unit that adsorbs moisture contained in the air blown into the space. The refrigerant-outside air heat exchange unit exchanges heat between the refrigerant and the outside air outside the air-conditioned space. The outside air side pressure reduction unit reduces the pressure of the refrigerant flowing into the refrigerant-outside air heat exchange unit. The refrigerant circuit switching unit switches the refrigerant circuit through which the refrigerant circulates. The air blowing unit can draw in at least the indoor air from within the air-conditioned space and blow it into the refrigerant-air heat exchange unit as air blown into the space.

[0013] In the desorption heating mode, which heats the air-conditioned space and desorbs moisture adsorbed onto the adsorption unit, the refrigerant circuit switching unit switches to a circuit that circulates the refrigerant flowing out from the heating unit in the following order: refrigerant-air heat exchange unit, outside air side pressure reduction unit, refrigerant-outside air heat exchange unit, and compressor intake.

[0014] Furthermore, in the indoor air adsorption heating mode, which heats the air-conditioned space and adsorbs moisture to the adsorption unit, the refrigerant circuit switching unit switches to a circuit that circulates the refrigerant flowing out from the heating unit in the order of the outside air side pressure reduction unit, the refrigerant outside air heat exchange unit, and the compressor intake, bypassing the refrigerant air heat exchange unit. At the same time, the blower unit blows indoor air as blown air towards the refrigerant air heat exchange unit.

[0015] According to this, in detachable heating mode, heated air from the heating unit is blown into the space to be air-conditioned, thereby heating the space to be air-conditioned.

[0016] Furthermore, in the detachable heating mode, the relatively high-temperature refrigerant that has leaked out of the heating unit is introduced into the refrigerant-air heat exchange unit. This raises the temperature of the adsorption unit in the refrigerant-air heat exchange unit, allowing the moisture adsorbed on the adsorption unit to be detached (in other words, removed).

[0017] Furthermore, in the internal air adsorption heating mode, moisture contained in the blown air can be adsorbed onto the adsorption unit, which has absorbed moisture during the dehumidification heating mode. In addition, by reheating the blown air dehumidified in the adsorption unit in the heating unit and blowing it into the air-conditioned space, dehumidification and heating of the air-conditioned space can be performed.

[0018] In this case, the blower unit blows internal air as blown air towards the refrigerant air heat exchange unit. Therefore, the energy consumed in the heating unit to heat the blown air to the desired temperature can be reduced compared to when outside air is blown as blown air.

[0019] Furthermore, in the internal air adsorption heating mode, the refrigerant circuit switching unit switches to a refrigerant circuit that bypasses the refrigerant-air heat exchange unit and allows the refrigerant to flow through it. Therefore, unnecessary energy is not consumed in order to supply refrigerant to the refrigerant-air heat exchange unit.

[0020] As a result, the air conditioning system according to the first aspect of this disclosure can fully achieve the effect of reducing energy consumption by providing a refrigerant air heat exchange unit having an adsorption unit. In other words, it is possible to sufficiently reduce the energy consumed when heating a space to be air-conditioned while dehumidifying the blown air.

[0021] Furthermore, an air conditioning system according to a second aspect of the present disclosure includes a compressor, a high-temperature side heat transfer fluid heat exchange unit, a refrigerant pressure reduction unit, a low-temperature side heat transfer fluid heat exchange unit, a high-temperature side air heat exchange unit, a heat transfer fluid outside air heat exchange unit, a heat transfer fluid air heat exchange unit, a heat transfer fluid circuit switching unit, and a blower unit.

[0022] The compressor compresses and discharges the refrigerant. The high-temperature side heat transfer fluid heat exchange section exchanges heat between the refrigerant discharged from the compressor and the heat transfer fluid. The refrigerant depressurization section depressurizes the refrigerant that has flowed out of the high-temperature side heat transfer fluid heat exchange section. The low-temperature side heat transfer fluid heat exchange section exchanges heat between the refrigerant that has been depressurized in the refrigerant depressurization section and the heat transfer fluid. The high-temperature side air heat exchange section exchanges heat between the heat transfer fluid that has flowed out of at least the high-temperature side heat transfer fluid heat exchange section and the air being blown into the air-conditioned space. The outside air heat exchange section exchanges heat between the heat transfer fluid that has flowed out of at least the low-temperature side heat transfer fluid heat exchange section and the outside air outside the air-conditioned space. The air heat exchange section exchanges heat between the heat transfer fluid that has flowed out of at least one of the high-temperature side heat transfer fluid heat exchange section and the low-temperature side heat transfer fluid heat exchange section and the air being blown in before it is heated in the high-temperature side air heat exchange section. The air heat exchange section has an adsorption section that adsorbs moisture contained in the air being blown in. The heat transfer medium circuit switching unit switches the heat transfer medium circuit through which the heat transfer medium circulates. The air blowing unit can draw in at least indoor air from the space to be air-conditioned and blow it towards the heat transfer medium air heat exchange unit.

[0023] In the desorption heating mode, which heats the air-conditioned space and desorbs moisture adsorbed onto the adsorption part, the heat transfer medium circuit switching unit switches to a heat transfer medium circuit that allows the heat transfer medium that has flowed out from the high-temperature side heat transfer medium heat exchange unit to flow into the high-temperature side air heat exchange unit and the heat transfer medium air heat exchange unit.

[0024] Furthermore, in the indoor air adsorption heating mode, which heats the air-conditioned space and adsorbs moisture to the adsorption unit, the heat transfer medium circuit switching unit simultaneously flows the heat transfer medium that has flowed out of the high-temperature side heat transfer medium heat exchange unit into the high-temperature side air heat exchange unit, and at the same time, switches to a heat transfer medium circuit that flows the heat transfer medium that has flowed out of the low-temperature side heat transfer medium heat exchange unit into the heat transfer medium outside air heat exchange unit, bypassing the heat transfer medium air heat exchange unit, and blows the indoor air toward the heat transfer medium air heat exchange unit.

[0025] According to this, in detachable heating mode, the heat transfer medium heated in the high-temperature heat transfer medium heat exchange section is flowed into the high-temperature air heat exchange section. Then, the air heated in the high-temperature air heat exchange section is blown into the space to be air-conditioned, thereby heating the space to be air-conditioned.

[0026] Furthermore, in the desorption heating mode, the heat medium heated in the high-temperature side heat medium heat exchanger is made to flow into the heat medium-air heat exchanger. As a result, the temperature of the adsorption part of the heat medium-air heat exchanger can be raised, and the moisture adsorbed on the adsorption part can be desorbed.

[0027] Also, in the indoor air adsorption heating mode, the moisture contained in the blown air can be adsorbed by the adsorption part where moisture was desorbed in the desorption heating mode. Furthermore, by reheating the blown air dehumidified by the adsorption part in the high-temperature side air heat exchanger and blowing it into the air-conditioning target space, dehumidifying heating of the air-conditioning target space can be performed.

[0028] At this time, the blower unit blows indoor air as the blown air toward the heat medium-air heat exchanger. Therefore, the energy consumed for reheating the blown air in the high-temperature side air heat exchanger can be reduced compared to the case of blowing outside air as the blown air.

[0029] Furthermore, in the indoor air adsorption heating mode, the heat medium circuit switching unit switches to a heat medium circuit that does not allow the heat medium to flow into the heat medium-air heat exchanger. Therefore, unnecessary energy is not consumed for allowing the heat medium to flow into the heat medium-air heat exchanger.

[0030] As a result, according to the air conditioner of the second aspect of the present disclosure, the effect of reducing the energy consumption by providing the heat medium-air heat exchanger having the adsorption part can be sufficiently obtained. That is, the energy consumed when heating the air-conditioning target space while dehumidifying the blown air can be sufficiently reduced.

Brief Description of the Drawings

[0031] The above objects, other objects, features, and advantages of the present disclosure will become clearer from the following detailed description with reference to the accompanying drawings. [Figure 1] It is a schematic overall configuration diagram of the vehicle air conditioner of the first embodiment. [Figure 2] It is an explanatory diagram for explaining the characteristics of the adsorbent of the first embodiment. [Figure 3] This is a block diagram showing the electrical control unit of a vehicle air conditioning system according to the first embodiment. [Figure 4] This is a schematic overall diagram showing the flow of refrigerant and heat transfer medium in the detachable heating mode of the vehicle air conditioning system according to the first embodiment. [Figure 5] This is a Mollier diagram showing the change in the state of the refrigerant in the detachable heating mode of the heat pump cycle of the first embodiment. [Figure 6] This is a schematic overall configuration diagram showing the flow of refrigerant and heat transfer medium in the internal air adsorption heating mode of the vehicle air conditioning system according to the first embodiment. [Figure 7] This is a Mollier diagram showing the change in the state of the refrigerant in the standalone internal adsorption heating mode of the heat pump cycle of the first embodiment. [Figure 8] This is a schematic overall diagram showing the flow of refrigerant and heat transfer medium in the low-temperature adsorption heating mode of the vehicle air conditioning system according to the first embodiment. [Figure 9] This is a Mollier diagram showing the change in the state of the refrigerant in the standalone low-temperature adsorption heating mode of the heat pump cycle of the first embodiment. [Figure 10] This is a schematic psychrometric chart illustrating the properties of the adsorbent in the first embodiment. [Figure 11] This is a schematic overall configuration diagram of a vehicle air conditioning system according to the second embodiment. [Figure 12] This is a schematic overall diagram showing the flow of refrigerant and heat transfer medium in the detachable heating mode of the vehicle air conditioning system of the second embodiment. [Figure 13] This is a schematic overall configuration diagram showing the flow of refrigerant and heat transfer medium in the internal air adsorption heating mode of the vehicle air conditioning system according to the second embodiment. [Figure 14] This is a schematic overall diagram showing the flow of refrigerant and heat transfer medium in the low-temperature adsorption heating mode of the vehicle air conditioning system according to the second embodiment. [Figure 15] This is a schematic overall configuration diagram of a vehicle air conditioning system according to the third embodiment. [Figure 16] This is a block diagram showing the electrical control unit of a vehicle air conditioning system according to the third embodiment. [Figure 17] This is a schematic overall diagram showing the flow of refrigerant and heat transfer medium in the detachable heating mode of the vehicle air conditioning system according to the third embodiment. [Figure 18] This is a schematic overall diagram showing the flow of refrigerant and heat transfer medium in the internal air adsorption heating mode of the vehicle air conditioning system according to the third embodiment. [Figure 19] This is a schematic overall diagram showing the flow of refrigerant and heat transfer medium in the low-temperature adsorption heating mode of the vehicle air conditioning system according to the third embodiment. [Modes for carrying out the invention]

[0032] Several embodiments for implementing this disclosure are described below with reference to the drawings. In each embodiment, parts corresponding to matters described in a prior embodiment are denoted by the same reference numerals, and redundant descriptions may be omitted. If only a part of the configuration is described in each embodiment, other parts of the configuration can be applied to other embodiments described in advance. Not only are combinations of parts that are explicitly shown to be combinable in each embodiment possible, but embodiments can also be partially combined even if not explicitly shown, as long as there are no particular problems with the combination.

[0033] (First Embodiment) A first embodiment of the air conditioning system according to this disclosure will be described using Figures 1 to 10. In this embodiment, the air conditioning system according to this disclosure is applied to a vehicle air conditioning system 1 installed in an electric vehicle. The vehicle air conditioning system 1 provides air conditioning to the vehicle interior, which is the space to be air-conditioned, and also adjusts the temperature of the in-vehicle equipment. Therefore, the vehicle air conditioning system 1 can be called an air conditioning system with an in-vehicle equipment temperature adjustment function, or an in-vehicle equipment temperature adjustment device with an air conditioning function.

[0034] In the vehicle air conditioning system 1, the temperature of the battery 80 is specifically controlled as an in-vehicle device. The battery 80 is a secondary battery that stores power supplied to multiple in-vehicle devices that operate electrically. The battery 80 is a battery pack formed by electrically connecting multiple stacked battery cells in series or parallel. The battery cells in this embodiment are lithium-ion batteries.

[0035] The battery 80 generates heat during operation (i.e., during charging and discharging). The battery 80 tends to lose output at low temperatures and deteriorates quickly at high temperatures. Therefore, the temperature of the battery 80 needs to be maintained within an appropriate temperature range (in this embodiment, 15°C or higher and 55°C or lower). For this reason, in the electric vehicle of this embodiment, the temperature of the battery 80 is controlled using the vehicle air conditioning system 1.

[0036] As shown in the overall configuration diagram in Figure 1, the vehicle air conditioning system 1 includes a heat pump cycle 10, a low-temperature side heat transfer medium circuit 30a, an indoor air conditioning unit 50, and the like.

[0037] First, let's explain the heat pump cycle 10. The heat pump cycle 10 is a vapor compression type refrigeration cycle that adjusts the temperature of the air supplied to the vehicle interior and the heat transfer medium circulating in the low-temperature heat transfer medium circuit 30a. The heat pump cycle 10 is configured to allow switching of the refrigerant circuit according to each operating mode, which will be described later, in order to adjust the temperature of the air conditioning and onboard equipment in the vehicle interior.

[0038] The heat pump cycle 10 uses R1234yf as the refrigerant. The heat pump cycle 10 constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure side refrigerant does not exceed the critical pressure of the refrigerant. The refrigerant is mixed with refrigerant oil for lubricating the compressor 11. The refrigerant oil is PAG oil (i.e., polyalkylene glycol oil) which is compatible with the liquid phase refrigerant. A portion of the refrigerant oil circulates in the refrigerant circuit together with the refrigerant.

[0039] The compressor 11 in the heat pump cycle 10 draws in refrigerant, compresses it, and discharges it. The compressor 11 is an electric compressor in which a fixed-capacity compression mechanism with a fixed discharge capacity is rotationally driven by an electric motor. The rotational speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 70, which will be described later.

[0040] The compressor 11 is located in the drive unit compartment, which is formed on the front side of the passenger compartment. The drive unit compartment forms a space in which at least some of the equipment used for generating and adjusting the driving force for vehicle operation (e.g., electric motors for driving) is located. Therefore, the space formed by the drive unit compartment is outside the passenger compartment (i.e., outside the space subject to air conditioning).

[0041] The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port of the compressor 11. The indoor condenser 12 is located inside the air conditioning case 51 of the indoor air conditioning unit 50, which will be described later. The indoor condenser 12 is a heat exchange unit for heating that exchanges heat between the discharged refrigerant discharged from the compressor and the blown air that has passed through the indoor evaporator 18, which will be described later. In the indoor condenser 12, the heat contained in the discharged refrigerant is released into the blown air, heating the blown air.

[0042] Therefore, the indoor condenser 12 is a heating unit that heats the blown air using the discharged refrigerant discharged from the compressor 11 as a heat source.

[0043] The inlet side of the first three-way joint 13a is connected to the refrigerant outlet of the indoor condenser 12. The first three-way joint 13a has three inlet and outlet ports that communicate with each other. The first three-way joint 13a can be a joint formed by joining multiple pipes, or a joint formed by providing multiple refrigerant passages in a metal block or resin block.

[0044] Furthermore, the heat pump cycle 10 is equipped with second three-way joints 13b to sixth three-way joints 13f, as will be described later. The basic configuration of the second three-way joints 13b to sixth three-way joints 13f is the same as that of the first three-way joint 13a. Also, the basic configuration of each three-way joint, which will be described in the embodiments described later, is the same as that of the first three-way joint 13a.

[0045] A three-way joint acts as a branching point where the flow of refrigerant is divided when one of its three inlets / outlets is used as an inlet and the other two as outlets. Conversely, when two of its three inlets / outlets are used as inlets and the remaining one as an outlet, a three-way joint acts as a merging point where the flows of refrigerant are combined.

[0046] One outlet of the first three-way joint 13a is connected to one inlet side of the second three-way joint 13b via the first on-off valve 15a. The other outlet of the first three-way joint 13a is connected to one inlet side of the fourth three-way joint 13d via the second on-off valve 15b.

[0047] The first on-off valve 15a is an on-off valve that opens and closes the refrigerant flow path from one outlet of the first three-way joint 13a to one inlet of the second three-way joint 13b. The first on-off valve 15a is a solenoid valve whose opening and closing operation is controlled by a control voltage output from the control device 70.

[0048] The second on-off valve 15b is an on-off valve that opens and closes the refrigerant flow path from the other outlet of the first three-way joint 13a to one inlet of the fourth three-way joint 13d. The basic configuration of the second on-off valve 15b is the same as that of the first on-off valve 15a.

[0049] Furthermore, as will be described later, the heat pump cycle 10 is equipped with a third on-off valve 15c to a fifth on-off valve 15e. The basic configuration of the third on-off valve 15c to the fifth on-off valve 15e is the same as that of the first three-way joint 13a. The first on-off valve 15a to the fifth on-off valve 15e can switch the refrigerant circuit by opening and closing the refrigerant flow path. Therefore, the first on-off valve 15a to the fifth on-off valve 15e constitute the refrigerant circuit switching section.

[0050] The outlet of the second three-way joint 13b is connected to the inlet side of the heating expansion valve 14a. The heating expansion valve 14a is an outside air side pressure reduction unit that reduces the pressure of the refrigerant flowing into the outdoor heat exchanger 16, as will be described later, during heating mode, etc. Furthermore, the heating expansion valve 14a is an outside air side flow rate adjustment unit that adjusts the flow rate (mass flow rate in this embodiment) of the refrigerant flowing into the outdoor heat exchanger 16.

[0051] The heating expansion valve 14a is an electrically operated variable throttling mechanism having a valve body that changes the opening degree of the throttling passage (i.e., valve opening degree) and an electric actuator (specifically, a stepping motor) that displaces the valve body. The operation of the heating expansion valve 14a is controlled by a control signal (specifically, a control pulse) output from the control device 70.

[0052] The heating expansion valve 14a has a fully open function that allows it to function as a simple refrigerant passage without exerting much refrigerant pressure reduction or flow rate adjustment effect when the valve opening is fully open. Alternatively, the heating expansion valve 14a may also have a fully closed function that blocks the refrigerant passage by completely closing the throttling passage with the valve body.

[0053] Furthermore, the heat pump cycle 10 is equipped with a cooling expansion valve 14b and a cooling expansion valve 14c, as will be described later. The basic configuration of the cooling expansion valve 14b and the cooling expansion valve 14c is the same as that of the heating expansion valve 14a. The cooling expansion valve 14b and the cooling expansion valve 14c have a fully open function and a fully closed function.

[0054] The cooling expansion valve 14b and the defrosting expansion valve 14c can switch the circuit configuration of the refrigerant circuit by exhibiting a fully closed function. Therefore, the cooling expansion valve 14b and the defrosting expansion valve 14c also function as refrigerant circuit switching units.

[0055] Of course, the cooling expansion valve 14b and the refrigerant expansion valve 14c may be formed by combining a variable throttle mechanism that does not have a fully closing function with an on-off valve that opens and closes the throttle passage. In this case, the on-off valve becomes the refrigerant circuit switching unit.

[0056] The outlet of the heating expansion valve 14a is connected to the refrigerant inlet side of the outdoor heat exchanger 16. The outdoor heat exchanger 16 is a refrigerant-outside-air heat exchange unit that exchanges heat between the refrigerant flowing out from the heating expansion valve 14a and outside air blown by an outside air fan (not shown). The outdoor heat exchanger 16 is located on the front side of the drive unit compartment. Therefore, when the vehicle is running, the airflow entering the drive unit compartment through the grille can be directed onto the outdoor heat exchanger 16.

[0057] The inlet side of the third three-way joint 13c is connected to the refrigerant outlet of the outdoor heat exchanger 16. The other inlet side of the fourth three-way joint 13d is connected to one outlet of the third three-way joint 13c via the first check valve 17a. The other inlet side of the sixth three-way joint 13f is connected to the other outlet of the third three-way joint 13c via the third on / off valve 15c.

[0058] The third on-off valve 15c is an on-off valve that opens and closes the refrigerant flow path from the other outlet of the third three-way joint 13c to one inlet of the sixth three-way joint 13f. The refrigerant flow path from the other outlet of the third three-way joint 13c to one inlet of the sixth three-way joint 13f is a refrigerant bypass passage that, in the detachable heating mode described later, guides the refrigerant that has flowed out of the outdoor heat exchanger 16 to the suction port side of the compressor 11, bypassing the indoor evaporator 18.

[0059] The first check valve 17a allows refrigerant to flow from the third three-way joint 13c side to the fourth three-way joint 13d side, and prevents refrigerant from flowing from the fourth three-way joint 13d side to the third three-way joint 13c side. The outlet of the fourth three-way joint 13d is connected to the inlet side of the fifth three-way joint 13e.

[0060] One outlet of the fifth three-way joint 13e is connected to the inlet side of the cooling expansion valve 14b. The other outlet of the fifth three-way joint 13e is connected to the inlet side of the cooling expansion valve 14c.

[0061] The cooling expansion valve 14b is a refrigerant air-side pressure reduction unit that reduces the pressure of the refrigerant flowing into the indoor evaporator 18 during cooling mode, etc. Furthermore, the cooling expansion valve 14b is a refrigerant air-side flow rate adjustment unit that adjusts the flow rate of the refrigerant flowing into the indoor evaporator 18.

[0062] The outlet of the cooling expansion valve 14b is connected to the refrigerant inlet side of the indoor evaporator 18. The indoor evaporator 18 is located inside the air conditioning case 51 of the indoor air conditioning unit 50, upstream of the indoor condenser 12 in the airflow.

[0063] The indoor evaporator 18 is a refrigerant-air heat exchange unit that exchanges heat between the low-pressure refrigerant, which has been reduced in pressure by the cooling expansion valve 14b, and the blown air before it is heated by the indoor condenser 12. The indoor evaporator 18 cools the blown air by evaporating the low-pressure refrigerant and exerting an endothermic effect, such as during cooling mode.

[0064] In this embodiment, a so-called tank-and-tube type heat exchanger is used as the indoor evaporator 18. The tank-and-tube type heat exchanger has a plurality of refrigerant tubes and a pair of refrigerant tanks.

[0065] Refrigerant tubes are metal pipes through which refrigerant flows. Multiple refrigerant tubes are stacked in a predetermined direction with spacing between them. Air passages are formed between adjacent tubes to allow the flow of vented air. Heat exchange fins are placed in the air passages to promote heat exchange between the refrigerant and the vented air. The heat exchange fins are corrugated fins formed by bending thin metal sheets into a wave shape.

[0066] A refrigerant tank is a metal, bottomed cylindrical member that extends in the direction of stacking of multiple refrigerant tubes. A pair of refrigerant tanks are each connected to both ends of the refrigerant tubes. Inside the refrigerant tank, there is a distribution space for distributing refrigerant to the multiple refrigerant tubes, and a collection space for collecting the refrigerant that has flowed out of the multiple refrigerant tubes.

[0067] Therefore, in a tank-and-tube type heat exchanger, a heat exchange core is formed mainly by refrigerant tubes and heat exchange fins to exchange heat between the refrigerant and the blown air. Furthermore, a solid layer of adsorbent 18a is arranged on the outer surface of the heat exchange core of the indoor evaporator 18. The adsorbent 18a is an adsorption part mainly composed of zeolite that adsorbs moisture contained in the blown air. In other words, the indoor evaporator 18 has an adsorption part.

[0068] In this embodiment, as the adsorbent 18a, as shown in Figure 2, one is adopted in which the maximum relative pressure ratio Rmax satisfies the following formula F1. 0.05 ≤ Rmax ≤ 0.35 …(F1) The maximum relative pressure ratio Rmax is the relative pressure ratio at which the increase in the adsorption amount of the adsorbent 18a is maximized when the relative pressure ratio is increased by a small amount. The relative pressure ratio is defined as the ratio of the partial pressure of water vapor in the surrounding air to the saturated water vapor pressure at the temperature of the adsorbent 18a. Therefore, the relative pressure ratio is a parameter corresponding to relative humidity. The adsorption amount is defined as the weight (kg) of water that 1 kg of adsorbent 18a can adsorb.

[0069] In other words, the maximum relative pressure ratio Rmax can be defined as the relative pressure ratio at which the ratio of the increase in adsorption to the increase in the relative pressure ratio is maximized. That is, the maximum relative pressure ratio Rmax can be defined as the relative pressure ratio at which the derivative of the derivative obtained by expressing the adsorption amount as a function of the relative pressure ratio with respect to the relative pressure ratio is localized.

[0070] Furthermore, in this embodiment, the adsorbent 18a specifically employs an adsorbent having isothermal adsorption characteristics equivalent to AQSOA(registered trademark) Z05 or Z02.

[0071] The adsorbent 18a preferably employs a crystalline aluminophosphate (ALPO-based zeolite) containing at least aluminum and phosphorus in its skeletal structure. The binder of the adsorbent 18a preferably contains epoxy resin, and the dry weight of the binder is preferably 0.5% or more and 40% or less of the weight of the adsorbent 18a.

[0072] Figure 2 also illustrates the adsorption characteristics at 25°C for two types of adsorption sections: adsorbent Da, where the maximum relative pressure ratio Rmax is approximately 0.05, and adsorbent Db, where the maximum relative pressure ratio Rmax is approximately 0.35. The adsorption rate (kg / s) of adsorbent 18a depends on the adsorption characteristics of adsorbent 18a. The adsorption rate (kg / s) of adsorbent 18a tends to increase as the maximum relative pressure ratio Rmax decreases.

[0073] One inlet side of a four-way joint 13x is connected to the refrigerant outlet of the indoor evaporator 18 via an evaporation pressure regulating valve 20 and a second check valve 17b.

[0074] The evaporation pressure regulating valve 20 maintains the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined set pressure in order to suppress frost formation in the indoor evaporator 18. The evaporation pressure regulating valve 20 is composed of a mechanical mechanism that increases the valve opening in response to an increase in the refrigerant pressure on the refrigerant outlet side of the indoor evaporator 18.

[0075] The second check valve 17b allows refrigerant to flow from the indoor evaporator 18 side to the four-way joint 13x side, and prevents refrigerant from flowing from the four-way joint 13x side to the indoor evaporator 18 side. The four-way joint 13x is a joint section having four inlet and outlet ports that communicate with each other. A joint section formed in the same way as a three-way joint can be used as the four-way joint 13x.

[0076] The cooling expansion valve 14c is a refrigerant pressure reduction unit that reduces the amount of refrigerant flowing into the chiller 19 when operating in a mode that utilizes the cooling capacity of the heat pump cycle 10 to cool the battery 80. Furthermore, the cooling expansion valve 14c is a refrigerant flow rate adjustment unit that adjusts the flow rate of refrigerant flowing into the chiller 19.

[0077] The outlet of the cooling expansion valve 14c is connected to the inlet side of the refrigerant passage of the chiller 19. The chiller 19 has a refrigerant passage through which low-pressure refrigerant, which has been reduced in pressure by the cooling expansion valve 14c, flows, and a heat transfer medium passage through which heat transfer medium circulates in the low-temperature side heat transfer medium circuit 30a.

[0078] Chiller 19 is a low-temperature heat transfer fluid heat exchange section that exchanges heat between a low-pressure refrigerant flowing through a refrigerant passage and a heat transfer fluid flowing through a heat transfer fluid passage. In chiller 19, the heat transfer fluid is cooled by evaporating the low-pressure refrigerant, which exerts an endothermic effect.

[0079] The outlet of the refrigerant passage of the chiller 19 is connected to the other inlet side of the four-way joint 13x via a third check valve 17c. The third check valve 17c allows refrigerant to flow from the chiller 19 side to the four-way joint 13x side, and prevents refrigerant from flowing from the four-way joint 13x side to the chiller 19 side.

[0080] One outlet of the four-way joint 13x is connected to the other inlet side of the second three-way joint 13b via a fourth on-off valve 15d and a fourth check valve 17d.

[0081] The fourth on-off valve 15d is an on-off valve that opens and closes the refrigerant flow path from one outlet of the four-way joint 13x to the other inlet of the second three-way joint 13b. The fourth check valve 17d allows refrigerant to flow from the four-way joint 13x side to the second three-way joint 13b side, and prevents refrigerant from flowing from the second three-way joint 13b side to the four-way joint 13x side.

[0082] The other outlet of the four-way joint 13x is connected to the other inlet side of the sixth three-way joint 13f via the fifth on-off valve 15e. The fifth on-off valve 15e is an on-off valve that opens and closes the refrigerant flow path from the other outlet of the four-way joint 13x to the other inlet of the sixth three-way joint 13f.

[0083] The outlet of the sixth three-way joint 13f is connected to the inlet side of the accumulator 21. The accumulator 21 is a low-pressure gas-liquid separator that separates the gas-liquid phase of the low-pressure refrigerant flowing out from the sixth three-way joint 13f and stores the separated liquid-phase refrigerant as excess refrigerant in the cycle. The outlet of the gas-phase refrigerant of the accumulator 21 is connected to the suction side of the compressor 11.

[0084] Next, the low-temperature side heat transfer medium circuit 30a will be described. The low-temperature side heat transfer medium circuit 30a is a circuit that circulates the heat transfer medium. In this embodiment, an aqueous solution of ethylene glycol is used as the heat transfer medium. The low-temperature side heat transfer medium circuit 30a is equipped with a low-temperature side heat transfer medium pump 31a, a heat transfer medium passage of the chiller 19, a cooling water passage 80a of the battery 80, a low-temperature side heat transfer medium three-way valve 32a, a low-temperature side radiator 34a, and the like.

[0085] The low-temperature side heat transfer pump 31a is a heat transfer pumping unit that sucks in the heat transfer fluid that has flowed out from the heat transfer fluid three-way joint 33a and pumps it into the heat transfer fluid passage of the chiller 19. The low-temperature side heat transfer pump 31a is an electric water pump whose rotational speed (i.e., pumping capacity) is controlled by a control voltage output from the control device 70.

[0086] The outlet of the heat transfer medium passage of the chiller 19 is connected to the inlet side of the cooling water passage 80a of the battery 80. The cooling water passage 80a of the battery 80 is a heat transfer medium passage for cooling the battery 80 by circulating the heat transfer medium that has flowed out of the chiller 19. In other words, the cooling water passage 80a is a heat exchange section for battery cooling that cools the battery 80 by exchanging heat between the heat transfer medium circulating in the heat transfer medium passage and the battery cells.

[0087] The cooling water passage 80a is formed inside a battery-specific case that houses multiple stacked battery cells. The cooling water passage 80a has a passage configuration in which multiple passages are connected in parallel inside the battery-specific case. This allows all battery cells to be cooled evenly in the cooling water passage 80a.

[0088] The outlet of the cooling water passage 80a of the battery 80 is connected to the inlet side of the low-temperature side heat transfer medium three-way valve 32a. The low-temperature side heat transfer medium three-way valve 32a has one inlet and two outlets, and is an electrically operated three-way flow control valve that can continuously adjust the ratio of the passage areas of the two outlets. The operation of the low-temperature side heat transfer medium three-way valve 32a is controlled by a control signal output from the control device 70.

[0089] One outlet of the low-temperature side heat transfer fluid three-way valve 32a is connected to one inlet side of the heat transfer fluid three-way joint 33a via the radiator bypass passage 35a. The other outlet of the low-temperature side heat transfer fluid three-way valve 32a is connected to the heat transfer fluid inlet side of the low-temperature side radiator 34a.

[0090] The low-temperature side heat transfer fluid three-way valve 32a can cause the entire flow rate of heat transfer fluid that has entered it to flow out to either the low-temperature side radiator 34a or the radiator bypass passage 35a. Therefore, the low-temperature side heat transfer fluid three-way valve 32a also functions as a heat transfer fluid circuit switching unit that switches the circuit configuration of the low-temperature side heat transfer fluid circuit 30a.

[0091] The low-temperature side radiator 34a is a heat exchange unit that exchanges heat between the heat transfer medium flowing out from the cooling water passage 80a of the battery 80 and outside air blown by an outside air fan (not shown). The low-temperature side radiator 34a is located on the front side of the drive unit cabin. Therefore, when the vehicle is running, the airflow from the vehicle can be directed onto the low-temperature side radiator 34a. The low-temperature side radiator 34a may be formed integrally with the outdoor heat exchanger 16.

[0092] The other inlet side of the heat transfer medium three-way connector 33a is connected to the outlet of the heat transfer medium of the low-temperature side radiator 34a. The basic configuration of the heat transfer medium three-way connector 33a is the same as that of the first three-way connector 13a for the refrigerant, etc. Furthermore, the basic configuration of each heat transfer medium three-way connector described in the embodiments described later is the same as that of the heat transfer medium three-way connector 33a. The inlet side of the low-temperature side heat transfer medium pump 31a is connected to the outlet of the heat transfer medium three-way connector 33a.

[0093] Next, the interior air conditioning unit 50 will be described. The interior air conditioning unit 50 is a unit that integrates various components to blow air adjusted to an appropriate temperature for air conditioning inside the vehicle into the appropriate location inside the vehicle. The interior air conditioning unit 50 is located inside the instrument panel at the very front of the vehicle interior.

[0094] The indoor air conditioning unit 50 has an air conditioning case 51 that forms an air passage through which supplied air circulates. A blower 52, an indoor evaporator 18, an indoor condenser 12, etc., are arranged in the air passage formed inside the air conditioning case. The air conditioning case 51 is molded from a resin (for example, polypropylene) that has a certain degree of elasticity and excellent strength.

[0095] An internal / external air switching device 53 is located at the uppermost part of the airflow in the air conditioning case 51. The internal / external air switching device 53 is an internal / external air ratio adjustment unit that can continuously adjust the ratio of internal air to external air in the air supplied to the air conditioning case 51. Internal air is the air that has flowed out from the vehicle interior, which is the space to be air-conditioned. External air is the air from outside the vehicle interior. The operation of the internal / external air switching device 53 is controlled by a control signal output from the control device 70.

[0096] A blower 52 is positioned downstream of the airflow of the internal / external air switching device 53. The blower 52 is a blower that blows air drawn in via the internal / external air switching device 53 into the vehicle interior. The rotational speed (i.e., blowing capacity) of the blower 52 is controlled by a control voltage output from the control device 70. When internal air is introduced via the internal / external air switching device 53, the blower 52 can draw in internal air and blow it out into the vehicle interior.

[0097] An indoor evaporator 18 is located downstream of the airflow of the blower 52. Furthermore, a heating passage 55a and a cold air bypass passage 55b are formed downstream of the airflow of the indoor evaporator 18 inside the air conditioning case 51.

[0098] The heating passage 55a is equipped with an indoor condenser 12. Therefore, the heating passage 55a is an air passage that allows the supplied air, which has passed through the indoor evaporator 18, to flow downstream by passing it through the indoor condenser 12. The cold air bypass passage 55b is an air passage that allows the supplied air, which has passed through the indoor evaporator 18, to flow downstream by bypassing the indoor condenser 12.

[0099] Furthermore, an air mix door 54 is provided in the air passage located downstream of the airflow of the indoor evaporator 18, and upstream of the airflow of the heating passage 55a and the cold air bypass passage 55b.

[0100] The air mix door 54 is an airflow ratio adjustment unit that adjusts the airflow ratio between the amount of air that flows into the heating passage 55a and the amount of air that flows into the cold air bypass passage 55b, from the air that has passed through the indoor evaporator 18. The operation of the actuator for driving the air mix door 54 is controlled by a control signal output from the control device 70.

[0101] A mixing space 56 is formed downstream of the airflow in the heating passage 55a and the cold air bypass passage 55b within the air conditioning case 51. The mixing space 56 is a space in which the blown air heated by the indoor condenser 12 located in the heating passage 55a is mixed with the blown air that has passed through the cold air bypass passage 55b and has not been heated.

[0102] Therefore, the indoor air conditioning unit 50 can adjust the temperature of the air (i.e., conditioned air) that is mixed in the mixing space 56 and blown into the passenger compartment by adjusting the airflow ratio of the air mix door 54.

[0103] Furthermore, at the downstream end of the airflow in the air conditioning case 51, multiple openings are formed to blow the air, which has been mixed and temperature-adjusted in the mixing space 56, into the vehicle interior.

[0104] Multiple openings are provided, including a face opening, a foot opening, and a defroster opening (none of which are shown). The face opening is for blowing conditioned air towards the upper body of the occupant inside the vehicle. The foot opening is for blowing conditioned air towards the occupant's feet. The defroster opening is for blowing conditioned air towards the inner surface of the vehicle's front window glass.

[0105] Furthermore, face doors, foot doors, and defroster doors (none of which are shown) are positioned upstream of the airflow to the face opening, foot opening, and defroster opening, respectively. The face doors adjust the opening area of ​​the face opening. The foot doors adjust the opening area of ​​the foot opening. The defroster doors adjust the opening area of ​​the defroster opening.

[0106] The face door, foot door, and defroster door are outlet mode switching units that switch the outlet mode. These doors are connected via a linkage mechanism or the like to a common electric actuator for driving the outlet mode door, and are rotated in conjunction with each other. The operation of the electric actuator for driving the outlet mode door is controlled by a control signal output from the control device 70.

[0107] Therefore, the indoor air conditioning unit 50 can switch the outlet mode by switching the opening that the outlet mode switching unit opens and closes, thereby blowing conditioned air from the mixing space 56 to the appropriate location in the vehicle interior.

[0108] Furthermore, an outside air bypass passage 55c is formed inside the air conditioning case 51. The outside air bypass passage 55c is a passage that guides the air blown from the blower 52 to the upstream side of the indoor condenser 12 in the heating passage 55a, bypassing the indoor evaporator 18.

[0109] An auxiliary outside air door 57, which opens and closes the outside air bypass passage 55c, is located at the downstream end of the airflow in the outside air bypass passage 55c. The operation of the actuator for driving the auxiliary outside air door 57 is controlled by a control signal output from the control device 70.

[0110] Furthermore, an exhaust door 58 that opens and closes the exhaust port 51a is located at the downstream end of the airflow in the cool air bypass passage 55b. The exhaust port 51a is an opening for discharging the air that has flowed through the cool air bypass passage 55b to the outside of the vehicle.

[0111] The exhaust door 58 can adjust the ratio of the amount of airflow that flows through the cold air bypass passage 55b into the mixing space 56 and the amount of airflow that is exhausted outside the vehicle. The exhaust door 58 can also discharge the entire amount of airflow that flows into the cold air bypass passage 55b to either the mixing space 56 or outside the vehicle. The operation of the actuator for driving the exhaust door 58 is controlled by a control signal output from the control device 70.

[0112] Next, the electrical control unit of the vehicle air conditioning system 1 will be described. The control unit 70 is composed of a well-known microcomputer including a CPU, ROM, and RAM, and its peripheral circuits. The control unit 70 performs various calculations and processes based on the control program stored in the ROM. Then, based on the calculation and processing results, the control unit 70 controls the operation of various controlled devices connected to the output side.

[0113] As shown in the block diagram in Figure 3, a group of control sensors is connected to the input side of the control device 70. The detection signals from the control sensors are input to the control device 70. Each sensor is described below.

[0114] The interior temperature sensor 71a is an interior temperature detection unit that detects the temperature inside the vehicle (interior temperature) Tr. The exterior temperature sensor 71b is an exterior temperature detection unit that detects the temperature outside the vehicle (outside temperature) Tam. The solar radiation sensor 71c is a solar radiation detection unit that detects the amount of solar radiation As irradiated into the vehicle interior.

[0115] The discharge refrigerant temperature and pressure sensor 72a is a discharge refrigerant temperature and pressure detection unit that detects the discharge refrigerant temperature Td and discharge refrigerant pressure Pd of the discharge refrigerant discharged from the compressor 11.

[0116] The high-pressure side refrigerant temperature and pressure sensor 72b is a high-pressure side refrigerant temperature and pressure detection unit that detects the high-pressure side refrigerant temperature T1 and high-pressure side refrigerant pressure P1 of the refrigerant flowing out from the heating unit. In this embodiment, the high-pressure side refrigerant temperature and pressure sensor 72b detects the temperature and pressure of the refrigerant flowing out from the indoor condenser 12 and into the heating expansion valve 14a.

[0117] The outdoor unit-side refrigerant temperature and pressure sensor 72c is an outdoor unit-side refrigerant temperature and pressure detection unit that detects the outdoor unit-side refrigerant temperature T2 and outdoor unit-side refrigerant pressure P2 of the refrigerant that has flowed out from the outdoor heat exchanger 16.

[0118] The chiller-side refrigerant temperature and pressure sensor 72d is a chiller-side refrigerant temperature and pressure detection unit that detects the chiller-side refrigerant temperature Tc and chiller-side refrigerant pressure Pc of the refrigerant that has flowed out from the refrigerant passage of the chiller 19.

[0119] In this embodiment, a detection unit is used as the refrigerant temperature and pressure sensor, in which the pressure detection unit and the temperature detection unit are integrated. However, of course, a pressure detection unit and a temperature detection unit that are configured separately may also be used.

[0120] The evaporator temperature sensor 72f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18. Specifically, the evaporator temperature sensor 72f in this embodiment detects the temperature of the heat exchange fins of the indoor evaporator 18.

[0121] The heat transfer medium temperature sensor 73 is a heat transfer medium temperature detection unit that detects the temperature of the cooling heat transfer medium TWB, which is the temperature of the heat transfer medium flowing into the cooling water passage 80a of the battery 80.

[0122] The battery temperature sensor 74 is a battery temperature detection unit that detects the battery temperature TB, which is the temperature of the battery 80. The battery temperature sensor 74 has multiple temperature sensors and detects the temperature at multiple locations on the battery 80. Therefore, the control device 70 can detect the temperature difference and temperature distribution of each battery cell that makes up the battery 80. Furthermore, the average value of the detected values ​​from the multiple temperature sensors is used as the battery temperature TB.

[0123] The air conditioning air temperature sensor 75 is an air conditioning air temperature detection unit that detects the air temperature TAV, which is the temperature of the air blown from the mixing space 56 into the vehicle interior.

[0124] The humidity sensor 76 is an interior humidity detection unit that detects the interior humidity RHr (relative humidity in this embodiment) near the vehicle window glass inside the vehicle cabin. Interior humidity RHr is a physical quantity that correlates with how easily the vehicle window glass fogs up. Therefore, interior humidity RHr can be used to determine whether or not anti-fogging of the vehicle window glass is necessary. For this reason, the humidity sensor 76 in this embodiment is a window fogging detection unit.

[0125] Furthermore, as shown in Figure 3, an operation panel 79 located near the instrument panel at the front of the vehicle interior is connected to the input side of the control device 70. Operation signals from various operation switches provided on the operation panel 79 are input to the control device 70.

[0126] The various control switches provided on the control panel 79 include, specifically, an auto switch, an air conditioner switch, an airflow setting switch, a temperature setting switch, and the like.

[0127] The auto switch is an automatic control setting unit that sets or cancels the automatic control operation of the vehicle air conditioning system 1. The air conditioner switch is a cooling request unit that requests the indoor evaporator 18 to cool the blown air. The airflow setting switch is an airflow setting unit that manually sets the airflow rate of the blower 52. The temperature setting switch is a temperature setting unit that sets the in-vehicle temperature Tset.

[0128] In this embodiment, the control device 70 is configured with an integrated control unit that controls various controlled devices connected to its output side. Therefore, the configuration (hardware and software) that controls the operation of each controlled device constitutes the control unit that controls the operation of each controlled device.

[0129] For example, the configuration of the control device 70 that controls the rotational speed of the compressor 11 constitutes the discharge capacity control unit 70a. The configuration that controls the operation of the refrigerant circuit switching section, such as the first on-off valve 15a to the fifth on-off valve 15e, constitutes the refrigerant circuit switching control unit 70b. The configuration that controls the operation of the heat transfer medium circuit switching section, such as the low-temperature side heat transfer medium three-way valve 32a, constitutes the heat transfer medium circuit switching control unit 70c.

[0130] The configuration that controls the actuator for driving the auxiliary outside air door 57 constitutes the auxiliary outside air door control unit 70d. The configuration that controls the actuator for driving the exhaust door 58 constitutes the exhaust door control unit 70e.

[0131] Furthermore, the control device 70 includes a cooling determination unit 70f which determines whether or not cooling of the battery 80 using the cooling capacity of the heat pump cycle 10 is necessary. Also, the control device 70 includes an anti-fogging determination unit 70g which determines whether or not anti-fogging of the vehicle window glass is necessary.

[0132] Next, the operation of the vehicle air conditioning system 1 will be described. The vehicle air conditioning system 1 can switch between various operating modes in order to provide appropriate air conditioning inside the vehicle and appropriate temperature control for the battery 80. Switching between operating modes is performed by executing a control program that is pre-stored in the control device 70.

[0133] The control program is executed not only when the vehicle system's start switch (the so-called ignition switch) is turned on and the vehicle system is running, but also when the battery 80 is being charged from an external power source, etc. The control program controls the air conditioning inside the vehicle when the auto switch is turned on.

[0134] The control program reads the detection signals from the control sensors described above and the operation signals from the operation switches on the control panel 79. Furthermore, when the auto switch on the control panel 79 is turned on, the control program calculates the target discharge temperature TAO based on the read detection signals and operation signals. The target discharge temperature TAO is the target temperature of the air blown into the vehicle cabin.

[0135] The target discharge temperature TAO is calculated using the following formula F2. TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×As+C…(F2) Tset is the in-cabin temperature set by the temperature setting switch on the control panel 79. Tr is the in-cabin temperature detected by the in-cabin temperature sensor 71a. Tam is the outside temperature detected by the outside temperature sensor 71b. As is the solar radiation detected by the solar radiation sensor 71c. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

[0136] Furthermore, the control program selects an operating mode based on detection signals, operation signals, target discharge temperature (TAO), etc. Then, it controls the operation of various controlled devices according to the selected operating mode.

[0137] The control program repeats control routines at predetermined control cycles until a predetermined termination condition is met. These routines include reading detection signals and operation signals, calculating the target discharge temperature (TAO), selecting an operating mode, and controlling the operation of various controlled devices according to the selected operating mode. The detailed operation of each operating mode is described below.

[0138] (a) Cooling mode The cooling mode is an operating mode that cools the interior of the vehicle by blowing cooled air into the vehicle interior. The cooling mode is likely to be selected when the outside temperature Tam is relatively high (25°C or higher in this embodiment) or when the target outlet temperature TAO is relatively low, with the auto switch and air conditioner switch turned on.

[0139] There are two cooling modes: standalone cooling mode and combined cooling mode. Standalone cooling mode is an operating mode that cools the vehicle interior without cooling the battery 80, utilizing the cooling capacity of the heat pump cycle 10. Combined cooling mode is an operating mode that cools the vehicle interior while also cooling the battery 80, utilizing the cooling capacity of the heat pump cycle 10.

[0140] In this embodiment, the cooling determination unit 70f determines that cooling of the battery 80 using the cooling capacity of the heat pump cycle 10 is necessary when the battery temperature TB detected by the battery temperature sensor 74 is equal to or greater than a predetermined reference cooling temperature KTB. This is the same in other operating modes as well.

[0141] (a-1) Standalone cooling mode In the standalone cooling mode heat pump cycle 10, the control device 70 fully opens the heating expansion valve 14a, throttles the cooling expansion valve 14b to exert a refrigerant pressure reduction effect, and fully closes the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, closes the second on-off valve 15b, closes the third on-off valve 15c, closes the fourth on-off valve 15d, and opens the fifth on-off valve 15e.

[0142] Therefore, in the standalone cooling mode of the heat pump cycle 10, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, heating expansion valve 14a (which is in a fully open state), outdoor heat exchanger 16, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, accumulator 21, and the intake side of the compressor 11.

[0143] Furthermore, the control device 70 controls the refrigerant discharge capacity of the compressor 11 so that the evaporator temperature Tefin detected by the evaporator temperature sensor 72f approaches the target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target discharge temperature TAO by referring to a control map pre-stored in the control device 70.

[0144] In the control map, the target evaporator temperature TEO is increased as the target discharge temperature TAO increases. Furthermore, the control map determines the target evaporator temperature TEO within a range that suppresses frost formation on the indoor evaporator 18.

[0145] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14b so that the degree of subcooling SC2 of the refrigerant flowing into the cooling expansion valve 14b approaches the target degree of subcooling SCO2. The control device 70 detects the degree of subcooling SC2 based on the outdoor unit side refrigerant temperature T2 and outdoor unit side refrigerant pressure P2 detected by the outdoor unit side refrigerant temperature and pressure sensor 72c.

[0146] The target subcooling degree SCO2 is determined based on the discharge refrigerant pressure Pd detected by the discharge refrigerant temperature and pressure sensor 72a, by referring to a control map pre-stored in the control device 70. The control map determines the target subcooling degree SCO2 such that the coefficient of performance (i.e., COP) of the heat pump cycle 10 reaches its maximum value.

[0147] In the low-temperature heat transfer medium circuit 30a of the standalone cooling mode, the control device 70 operates the low-temperature heat transfer medium pump 31a to achieve a predetermined standard pumping capacity. The control device 70 also controls the operation of the low-temperature heat transfer medium three-way valve 32a so that the cooling heat transfer medium temperature TWB detected by the heat transfer medium temperature sensor 73 approaches a predetermined standard cooling heat transfer medium temperature KTW.

[0148] In the indoor air conditioning unit 50 in standalone cooling mode, the control device 70 controls the airflow capacity of the fan 52 to achieve the target airflow capacity. The target airflow capacity of the fan 52 is determined by referring to a control map pre-stored in the control device 70, based on the target discharge temperature TAO. The control map increases the airflow of the fan 52 when high air conditioning capacity is required, such as during maximum cooling or maximum heating, in order to quickly bring the temperature inside the vehicle interior closer to the set temperature.

[0149] Furthermore, the control device 70 controls the operation of the electric actuator for the air mix door 54 so that the supplied air temperature TAV detected by the air conditioning air temperature sensor 75 approaches the target discharge temperature TAO.

[0150] Furthermore, the control device 70 controls the operation of the internal / external air switching device 53 based on the operation signal and the target discharge temperature TAO. Also, the control device 70 controls the operation of the electric actuator for the discharge mode door by referring to a control map pre-stored in the control device 70 based on the target discharge temperature TAO.

[0151] Furthermore, the control device 70 controls the operation of the electric actuator for the auxiliary outside air door 57 so as to close the outside air bypass passage 55c. The control device 70 also controls the operation of the electric actuator for the exhaust door 58 so as to close the exhaust port 51a. In addition, the control device 70 appropriately controls the operation of other controlled devices.

[0152] Therefore, in the standalone cooling mode heat pump cycle 10, a vapor compression type refrigeration cycle is configured in which the indoor condenser 12 and the outdoor heat exchanger 16 function as condensers, and the indoor evaporator 18 functions as an evaporator.

[0153] In the indoor condenser 12, the heat contained in the refrigerant is released into the blown air. This heats the blown air. In the outdoor heat exchanger 16, the heat contained in the refrigerant is released into the outside air. In the indoor evaporator 18, the refrigerant absorbs heat from the blown air and evaporates. This cools the blown air.

[0154] In the low-temperature side heat transfer medium circuit 30a of the standalone cooling mode, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a flows into the heat transfer medium passage of the chiller 19. Since there is no refrigerant flowing through the refrigerant passage, the heat transfer medium that has flowed into the heat transfer medium passage of the chiller 19 flows out of the chiller 19 without any temperature change.

[0155] The heat transfer fluid that flows out from the chiller 19 flows into the cooling water passage 80a of the battery 80. This cools the battery 80. The heat transfer fluid that flows out from the cooling water passage 80a flows out to one inlet side of the heat transfer fluid three-way joint 33a and to the inlet side of the low-temperature side radiator 34a, depending on the opening degree of the low-temperature side heat transfer fluid three-way valve 32a.

[0156] The heat transfer fluid that flows into the low-temperature side radiator 34a dissipates heat into the outside air. The heat transfer fluid that flows out of the low-temperature side radiator 34a flows into the other inlet of the three-way heat transfer fluid connector 33a. The heat transfer fluid that flows out of the three-way heat transfer fluid connector 33a is drawn into the low-temperature side heat transfer fluid pump 31a and pumped under pressure towards the heat transfer fluid passage of the chiller 19.

[0157] In the standalone cooling mode, the indoor air conditioning unit 50 receives air through the indoor / outdoor air switching device 53, which is then drawn into the blower 52 and blown out. In standalone cooling mode, the auxiliary outdoor air door 57 blocks the outdoor air bypass passage 55c. As a result, the entire volume of air blown from the blower 52 flows into the indoor evaporator 18 and is cooled.

[0158] The air cooled in the indoor evaporator 18 flows into the heating passage 55a and the cold air bypass passage 55b, depending on the opening of the air mix door 54. The air flowing into the heating passage 55a is heated as it passes through the indoor condenser 12 as ventilated air and flows into the mixing space 56. The air flowing into the cold air bypass passage 55b does not get exhausted outside the vehicle because the exhaust door 58 blocks the exhaust port 51a, but instead flows into the mixing space 56 as ventilated air.

[0159] The air, mixed and temperature-controlled in the mixing space 56, is blown out through openings to appropriate locations within the vehicle interior. This provides air conditioning to the vehicle interior.

[0160] Here, the cooling mode is the operating mode selected when the outside temperature Tam is relatively high. Therefore, when the cooling mode is selected, window fogging of the vehicle's windows is less likely to occur. Accordingly, in cooling mode, even when the adsorption amount of the adsorbent 18a reaches saturation, the operating mode for desorption of moisture from the adsorbent 18a is not executed. Consequently, in cooling mode, the interior of the vehicle is continuously cooled.

[0161] (a-2) Cooling mode The cooling mode is selected when it is determined that the battery 80 needs to be cooled using the cooling capacity of the heat pump cycle 10 while the standalone cooling mode is running.

[0162] In the cooling mode of the heat pump cycle 10, the control device 70 fully opens the heating expansion valve 14a, throttles the cooling expansion valve 14b, and throttles the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, closes the second on-off valve 15b, closes the third on-off valve 15c, closes the fourth on-off valve 15d, and opens the fifth on-off valve 15e.

[0163] Therefore, in the cooling mode of the heat pump cycle 10, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, heating expansion valve 14a (fully open), outdoor heat exchanger 16, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, accumulator 21, and the suction side of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, heating expansion valve 14a (fully open), outdoor heat exchanger 16, cooling expansion valve 14c, refrigerant passage of chiller 19, accumulator 21, and the suction side of the compressor 11. In other words, in the cooling mode, the indoor evaporator 18 and chiller 19 are switched to a refrigerant circuit that is connected in parallel with respect to the refrigerant flow.

[0164] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14c so that it becomes a predetermined throttle opening for the cooling mode. In addition, the control device 70 controls the operation of other controlled equipment in the same way as in the standalone cooling mode.

[0165] In the cooling mode, the low-temperature side heat transfer medium circuit 30a receives the heat transfer medium from the low-temperature side heat transfer medium pump 31a and flows into the heat transfer medium passage of the chiller 19. The heat transfer medium that flows into the heat transfer medium passage of the chiller 19 is cooled by the refrigerant absorbing heat. The heat transfer medium cooled by the chiller 19 flows into the cooling water passage 80a of the battery 80. This cools the battery 80. Other operations are the same as in the standalone cooling mode.

[0166] Therefore, in cooling mode, the vehicle interior can be cooled in the same way as in standalone cooling mode. Furthermore, in cooling mode, the cooling capacity of the heat pump cycle 10 can be used to cool the battery 80.

[0167] (b) Series dehumidification heating mode The series dehumidifying and heating mode is an operating mode that dehumidifies and heats the vehicle interior by reheating cooled and dehumidified air and blowing it into the vehicle interior. The series dehumidifying and heating mode is likely to be selected when the auto switch and air conditioner switch are turned on, and the outside temperature Tam is in the intermediate temperature range (in this embodiment, 10°C or higher and less than 25°C) or when the target discharge temperature TAO is in the intermediate temperature range.

[0168] The series dehumidification and heating modes include a standalone series dehumidification and heating mode and a cooled series dehumidification and heating mode. The standalone series dehumidification and heating mode is an operating mode that dehumidifies and heats the vehicle interior without cooling the battery 80, utilizing the cooling capacity of the heat pump cycle 10. The cooled series dehumidification and heating mode is an operating mode that cools the battery 80 using the cooling capacity of the heat pump cycle 10, while also dehumidifying and heating the vehicle interior.

[0169] (b-1) Standalone series dehumidification heating mode In the standalone series dehumidifying heating mode heat pump cycle 10, the control device 70 throttles the heating expansion valve 14a, throttles the cooling expansion valve 14b, and fully closes the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, closes the second on-off valve 15b, closes the third on-off valve 15c, closes the fourth on-off valve 15d, and opens the fifth on-off valve 15e.

[0170] Therefore, in the standalone series dehumidifying heating mode heat pump cycle 10, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, heating expansion valve 14a, outdoor heat exchanger 16, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, accumulator 21, and the intake side of the compressor 11.

[0171] Furthermore, the control device 70 determines the throttle openings of the heating expansion valve 14a and the cooling expansion valve 14b by referring to a control map pre-stored in the control device 70, based on the target discharge temperature TAO. In the control map, as the target discharge temperature TAO rises, the throttle opening of the heating expansion valve 14a is decreased and the throttle opening of the cooling expansion valve 14b is increased. In addition, the control device 70 controls the operation of other controlled equipment in the same way as in the standalone cooling mode.

[0172] Therefore, in the standalone series dehumidifying heating mode heat pump cycle 10, a vapor compression type refrigeration cycle is configured in which the indoor condenser 12 functions as a condenser and the indoor evaporator 18 functions as an evaporator. In the indoor condenser 12, the blown air is heated, similar to the standalone cooling mode. In the indoor evaporator 18, the blown air is cooled, similar to the standalone cooling mode.

[0173] Furthermore, in the standalone series dehumidifying heating mode heat pump cycle 10, if the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the temperature of the air flowing into the outdoor heat exchanger 16, the outdoor heat exchanger 16 functions as a condenser. Also, if the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the temperature of the air flowing into the outdoor heat exchanger 16, the outdoor heat exchanger 16 functions as an evaporator.

[0174] In the standalone series dehumidifying and heating mode of the indoor air conditioning unit 50, the entire volume of air blown from the blower 52 flows into the indoor evaporator 18, where it is cooled and dehumidified, similar to the standalone cooling mode. The air is then mixed in the mixing space 56 and temperature-adjusted before being blown out through openings to appropriate locations within the vehicle interior. This achieves dehumidifying and heating within the vehicle interior. Other operations are the same as in the standalone cooling mode.

[0175] Furthermore, in the standalone series dehumidifying heating mode heat pump cycle 10, as the target discharge temperature TAO increases, the throttling opening of the heating expansion valve 14a is decreased and the throttling opening of the cooling expansion valve 14b is increased. This makes it possible to improve the heating capacity of the blown air in the indoor condenser 12 as the target discharge temperature TAO increases, without increasing the rotational speed of the compressor 11.

[0176] More specifically, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the temperature of the air flowing into the outdoor heat exchanger 16, the temperature difference obtained by subtracting the temperature of the air flowing into the outdoor heat exchanger 16 from the saturation temperature of the refrigerant in the outdoor heat exchanger 16 can be reduced as the target discharge temperature TAO increases.

[0177] Therefore, as the target discharge temperature TAO increases, the amount of heat released from the refrigerant to the heat exchange air in the outdoor heat exchanger 16 can be reduced, and the amount of heat released from the refrigerant to the high-temperature heat transfer medium in the indoor condenser 12 can be increased.

[0178] Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the temperature of the air flowing into the outdoor heat exchanger 16, the temperature difference obtained by subtracting the saturation temperature of the refrigerant in the outdoor heat exchanger 16 from the temperature of the air flowing into the outdoor heat exchanger 16 can be increased as the target discharge temperature TAO rises.

[0179] Therefore, as the target discharge temperature TAO increases, the amount of heat absorbed by the refrigerant from the heat exchange air in the outdoor heat exchanger 16 increases, and the amount of heat released from the refrigerant to the heat transfer medium in the indoor condenser 12 increases.

[0180] As a result, in the series dehumidifying heating mode, the heating capacity of the blown air in the indoor condenser 12 can be improved as the target discharge temperature TAO rises, without increasing the rotational speed of the compressor 11.

[0181] Here, the series dehumidification and heating mode is an operating mode selected when the outside temperature Tam is in the intermediate temperature range. Therefore, when the series dehumidification and heating mode is selected, window fogging of the vehicle's windows is less likely to occur. Accordingly, in the series dehumidification and heating mode, even when the adsorption amount of the adsorbent 18a reaches the saturation amount, the operating mode for desorbing moisture from the adsorbent 18a is not executed. Consequently, in the series dehumidification and heating mode, continuous dehumidification and heating of the vehicle interior can be performed.

[0182] However, if it is determined that fogging of the vehicle windows is necessary while the serial dehumidifying heating mode is running, the system will switch to the heating mode described later.

[0183] (b-2) Cooling series dehumidification heating mode The cooling-series dehumidifying-heating mode is selected when it is determined that cooling of the battery 80 is necessary while the standalone-series dehumidifying-heating mode is running.

[0184] In the standalone series dehumidifying heating mode heat pump cycle 10, the control device 70 throttles the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, closes the second on-off valve 15b, closes the third on-off valve 15c, closes the fourth on-off valve 15d, and opens the fifth on-off valve 15e.

[0185] Therefore, in the standalone series dehumidifying heating mode, the heat pump cycle 10 switches to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates in the following order: indoor condenser 12, heating expansion valve 14a, outdoor heat exchanger 16, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, accumulator 21, and the suction side of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 switches to a refrigerant circuit in which the refrigerant circulates in the following order: indoor condenser 12, heating expansion valve 14a, outdoor heat exchanger 16, cooling expansion valve 14c, refrigerant passage of chiller 19, accumulator 21, and the suction side of the compressor 11. In other words, in standalone series dehumidifying heating mode, the indoor evaporator 18 and chiller 19 are switched to a refrigerant circuit in which they are connected in parallel with respect to the refrigerant flow.

[0186] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14c so that it becomes a predetermined throttle opening for the cooling series dehumidification heating mode. In addition, the control device 70 controls the operation of other controlled devices in the same way as the standalone series dehumidification heating mode.

[0187] Therefore, in the series cooling, dehumidifying, and heating mode heat pump cycle 10, a vapor compression type refrigeration cycle is configured in which the indoor condenser 12 functions as a condenser, and the indoor evaporator 18 and chiller 19 function as evaporators.

[0188] In the indoor condenser 12, the blown air is heated, similar to the standalone series dehumidifying heating mode. In the indoor evaporator 18, the blown air is cooled, similar to the standalone series dehumidifying heating mode. In the chiller 19, the heat transfer medium is cooled, similar to the cooling mode.

[0189] Furthermore, in the standalone series dehumidifying heating mode heat pump cycle 10, if the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the temperature of the air flowing into the outdoor heat exchanger 16, the outdoor heat exchanger 16 functions as a condenser. Also, if the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the temperature of the air flowing into the outdoor heat exchanger 16, the outdoor heat exchanger 16 functions as an evaporator.

[0190] In the cooling-series dehumidifying-heating mode, the low-temperature side heat transfer medium circuit 30a, similar to the cooling-cooling mode, is cooled by the chiller 19 after being pumped from the low-temperature side heat transfer medium pump 31a. The heat transfer medium cooled by the chiller 19 flows into the cooling water passage 80a of the battery 80. This cools the battery 80. Other operations are the same as in the standalone-series dehumidifying-heating mode.

[0191] Therefore, in the cooling-series dehumidifying-heating mode, dehumidifying and heating of the vehicle interior can be performed, similar to the standalone-series dehumidifying-heating mode. Furthermore, in the cooling-series dehumidifying-heating mode, the battery 80 can be cooled using the cooling capacity of the heat pump cycle 10, similar to the cooling-cooling mode.

[0192] (c) Heating mode The heating mode is an operating mode that performs dehumidifying and heating of the vehicle interior by heating the blown air with a higher heating capacity than the series dehumidifying heating mode and blowing it into the vehicle interior. The heating mode is likely to be selected when the outside temperature Tam is relatively low (less than 10°C in this embodiment) or when the target blown-out temperature TAO is relatively high, with the auto switch and air conditioner switch turned on. Furthermore, the heating mode is also selected when it is determined that anti-fogging of the vehicle windows is necessary while the series dehumidifying heating mode is running.

[0193] In this embodiment, the anti-fogging determination unit 70g determines that fogging of the vehicle window glass has been detected when the internal humidity RHr detected by the humidity sensor 76 is equal to or greater than the standard internal humidity KRHr. In other words, it determines that anti-fogging of the vehicle window glass is necessary. This is the same in other driving modes as well.

[0194] Furthermore, the heating mode is selected when the outside temperature Tam is relatively low, and in order to suppress fogging of the vehicle windows, the adsorption capacity of the adsorbent 18a is used to dehumidify the blown air. For this reason, in heating mode, when the amount of adsorption by the adsorbent 18a reaches saturation, it is necessary to dehydrate the moisture adsorbed on the adsorbent 18a. Therefore, in heating mode, the dehydration heating mode, the internal air adsorption heating mode, and the low-temperature adsorption heating mode are executed in sequence.

[0195] The de-adhesion heating mode is an operating mode that heats the interior of the vehicle while simultaneously de-adhes moisture adsorbed onto the adsorbent 18a.

[0196] The interior air adsorption heating mode is an operating mode that heats the interior of the vehicle while adsorbing moisture contained in the blown air onto the adsorbent 18a without introducing refrigerant into the interior evaporator 18. Furthermore, the interior air adsorption heating mode includes a standalone interior air adsorption heating mode and a cooled interior air adsorption heating mode.

[0197] The standalone internal air adsorption heating mode is an internal air adsorption heating mode that does not cool the battery 80 using the cooling capacity of the heat pump cycle 10. The cooled internal air adsorption heating mode is an internal air adsorption heating mode that cools the battery 80 using the cooling capacity of the heat pump cycle 10.

[0198] The low-temperature adsorption heating mode is an operating mode that heats the interior of the vehicle and also introduces a refrigerant into the interior evaporator 18, thereby increasing the amount of moisture adsorbed by the adsorbent 18a compared to the interior air adsorption heating mode. Furthermore, the low-temperature adsorption heating mode includes a standalone low-temperature adsorption heating mode and a cooled low-temperature adsorption heating mode.

[0199] The standalone low-temperature adsorption heating mode is a low-temperature adsorption heating mode that does not cool the battery 80 using the cooling capacity of the heat pump cycle 10. The cooled low-temperature adsorption heating mode is a low-temperature adsorption heating mode that cools the battery 80 using the cooling capacity of the heat pump cycle 10.

[0200] (c-1) Detachable heating mode The detachable heating mode needs to be selected when the amount of adsorption of the adsorbent 18a reaches saturation, or just before it reaches saturation. Therefore, in this embodiment, the detachable heating mode is selected when it is determined that anti-fogging of the vehicle window glass is necessary while the low-temperature adsorption heating mode is running. The detachable heating mode continues until a predetermined standard detachment time has elapsed.

[0201] In the detachable heating mode heat pump cycle 10, the control device 70 throttles the heating expansion valve 14a, throttles the cooling expansion valve 14b, and fully closes the cooling expansion valve 14c. The control device 70 also closes the first on-off valve 15a, opens the second on-off valve 15b, opens the third on-off valve 15c, opens the fourth on-off valve 15d, and closes the fifth on-off valve 15e.

[0202] Therefore, in the detachable heating mode heat pump cycle 10, as shown by the black arrows in Figure 4, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, heating expansion valve 14a, outdoor heat exchanger 16, accumulator 21, and the intake side of the compressor 11.

[0203] Furthermore, the control device 70 controls the refrigerant discharge capacity of the compressor 11 so that the discharge refrigerant pressure Pd detected by the discharge refrigerant temperature and pressure sensor 72a approaches the target high-pressure PDO. The target high-pressure PDO is determined based on the target blow-off temperature TAO by referring to a control map pre-stored in the control device 70. The control map determines that the target high-pressure PDO should be increased as the target blow-off temperature TAO increases.

[0204] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14b so that the evaporator temperature Tefin approaches a predetermined reference desorption temperature KTe1 (50°C in this embodiment).

[0205] The reference desorption temperature KTe1 is determined to be a value higher than the ambient temperature Tr and lower than the durability temperature of the indoor evaporator 18. As the durability temperature, the saturation temperature of the refrigerant at the maximum allowable pressure determined from the pressure resistance performance of the indoor evaporator 18 can be used. In this embodiment, the durability temperature of the indoor evaporator 18 is approximately 60°C.

[0206] Furthermore, the control device 70 controls the throttle opening of the heating expansion valve 14a so that the degree of subcooling SC1 of the refrigerant flowing into the heating expansion valve 14a approaches the target degree of subcooling SCO1. The control device 70 detects the degree of subcooling SC1 based on the high-pressure side refrigerant temperature T1 and high-pressure side refrigerant pressure P1 detected by the high-pressure side refrigerant temperature and pressure sensor 72b.

[0207] The target subcooling degree SCO1 is determined based on the discharge refrigerant pressure Pd by referring to a control map pre-stored in the control device 70. The control map determines the target subcooling degree SCO1 so that the COP of the heat pump cycle 10 reaches its maximum value.

[0208] In the indoor air conditioning unit 50 in detachable heating mode, the control device 70 controls the operation of the indoor / outdoor air switching device 53 so that outside air is introduced into the air conditioning case 51. The control device 70 also controls the operation of the electric actuator for the air mix door 54 so that the heating passage 55a is fully closed and the cold air bypass passage 55b is fully open.

[0209] Furthermore, the control device 70 controls the operation of the electric actuator for the auxiliary outside air door 57 so as to open the outside air bypass passage 55c. The control device 70 also controls the operation of the electric actuator for the exhaust door 58 so as to fully open the exhaust port 51a side and fully close the mixing space 56 side. In addition, the control device 70 controls the operation of other controlled equipment in the same way as in the standalone cooling mode.

[0210] Therefore, in the detachable heating mode of the heat pump cycle 10, the state of the refrigerant changes as shown in the Mollier diagram in Figure 5. That is, the refrigerant discharged from the compressor 11 (point a5 in Figure 5) flows into the indoor condenser 12. The refrigerant that flows into the indoor condenser 12 condenses by releasing heat into the outside air introduced through the outside air bypass passage 55c (from point a5 to point b5 in Figure 5). As a result, the outside air used as the blown air is heated.

[0211] The refrigerant flowing out of the indoor condenser 12 flows into the cooling expansion valve 14b and is depressurized (from point b5 to point e5 in Figure 5). At this time, the throttle opening of the cooling expansion valve 14b is adjusted so that the evaporator temperature Tefin approaches the reference desorption temperature KTe1. The refrigerant depressurized in the cooling expansion valve 14b flows into the indoor evaporator 18.

[0212] The refrigerant flowing into the indoor evaporator 18 condenses upon the outside air blown in by the fan 52 and the adsorbent 18a (from point e5 to point f5 in Figure 5). This causes the temperature of the adsorbent 18a to rise, and the moisture adsorbed on the adsorbent 18a is desorbed.

[0213] The refrigerant that flows out from the indoor evaporator 18 flows into the heating expansion valve 14a and is depressurized (from point f5 to point c5 in Figure 5). The refrigerant that has been depressurized in the heating expansion valve 14a flows into the outdoor heat exchanger 16. The refrigerant that flows into the outdoor heat exchanger 16 absorbs heat from the outside air and evaporates (from point c5 to point d5 in Figure 5).

[0214] The refrigerant that flows out from the outdoor heat exchanger 16 flows into the accumulator 21. The gaseous refrigerant separated in the accumulator 21 is drawn into the compressor 11 and compressed again (from point d5 to point a5 in Figure 5).

[0215] In the detachable heating mode, the indoor air conditioning unit 50 receives outside air via the indoor / outdoor air switching device 53, which is then drawn into the blower 52 and blown out. In detachable heating mode, the auxiliary outside air door 57 opens the outside air bypass passage 55c. As a result, the outside air blown from the blower 52 flows into both the indoor evaporator 18 and the outside air bypass passage 55c.

[0216] The outside air flowing from the blower 52 into the indoor evaporator 18 is heated by heat exchange with the refrigerant as it passes through the indoor evaporator 18, and is also humidified by moisture desorbed from the adsorbent 18a. In the desorbent heating mode, the air mix door 54 is fully closed on the heating passage 55a side, and the exhaust door 58 is fully closed on the mixing space 56 side. Therefore, the outside air humidified in the indoor evaporator 18 flows into the cold air bypass passage 55b and is exhausted outside the vehicle through the exhaust port 51a.

[0217] The outside air flowing from the blower 52 into the outside air bypass passage 55c flows into the heating passage 55a as blown air and is heated as it passes through the indoor condenser 12. The blown air heated in the indoor condenser 12 flows into the mixing space 56. The blown air that flows into the mixing space 56 is blown out to appropriate locations in the vehicle interior through openings. This provides heating to the vehicle interior. Other operations are the same as in the standalone cooling mode.

[0218] Therefore, in the detachable heating mode, the vehicle interior can be heated while the adsorbent 18a is being detached. Furthermore, in the detachable heating mode, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be lowered compared to the series dehumidification heating mode, thereby increasing the amount of heat absorbed by the refrigerant. Consequently, in the detachable heating mode, the heating capacity of the blown air in the indoor condenser 12 can be improved compared to the series dehumidification heating mode.

[0219] Furthermore, in the detachable heating mode, outside air with lower humidity than the inside air is blown into the vehicle interior as ventilated air, so window fogging of the vehicle's windows can be suppressed without the need to adsorb moisture contained in the ventilated air onto the adsorbent 18a.

[0220] (c-2-1) Standalone internal air adsorption heating mode The standalone internal air adsorption heating mode is selected when, after the detachable heating mode has finished, it is determined that it is not necessary to cool the battery 80 using the cooling capacity of the heat pump cycle 10.

[0221] In the heat pump cycle 10 of the standalone internal air adsorption heating mode, the control device 70 throttles the heating expansion valve 14a, fully closes the cooling expansion valve 14b, and fully closes the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, closes the second on-off valve 15b, opens the third on-off valve 15c, closes the fourth on-off valve 15d, and closes the fifth on-off valve 15e.

[0222] Therefore, in the standalone indoor adsorption heating mode, the heat pump cycle 10 switches to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates in the following order: indoor condenser 12, heating expansion valve 14a, outdoor heat exchanger 16, accumulator 21, and the intake side of the compressor 11, as shown by the black arrows in Figure 6. In other words, in standalone indoor adsorption heating mode, the refrigerant circuit switches to one that bypasses the indoor evaporator 18.

[0223] In the indoor air conditioning unit 50 operating in standalone indoor air adsorption heating mode, the control device 70 controls the operation of the indoor / outdoor air switching device 53 so that indoor air is introduced into the air conditioning case 51. The control device 70 also controls the operation of the electric actuator for the air mix door 54 so that the supplied air temperature TAV approaches the target discharge temperature TAO.

[0224] Furthermore, the control device 70 controls the operation of the electric actuator for the auxiliary outside air door 57 so as to close the outside air bypass passage 55c. The control device 70 also controls the operation of the electric actuator for the exhaust door 58 so as to close the exhaust port 51a. In addition, the control device 70 controls the operation of other controlled devices in the same manner as in the detachable heating mode.

[0225] Therefore, in the heat pump cycle 10 of the standalone indoor adsorption heating mode, the state of the refrigerant changes as shown in the Mollier diagram in Figure 7. That is, the refrigerant discharged from the compressor 11 (point a7 in Figure 7) flows into the indoor condenser 12. The refrigerant that flows into the indoor condenser 12 condenses by releasing heat into the blown air flowing through the heating passage 55a (from point a7 to point b7 in Figure 7). As a result, the blown air is heated.

[0226] The refrigerant that flows out from the indoor condenser 12 flows into the heating expansion valve 14a and is depressurized (from point b7 to point c7 in Figure 7). The refrigerant that has been depressurized in the heating expansion valve 14a flows into the outdoor heat exchanger 16. The refrigerant that flows into the outdoor heat exchanger 16 absorbs heat from the outside air and evaporates (from point c7 to point d7 in Figure 7).

[0227] The refrigerant that flows out from the outdoor heat exchanger 16 flows into the accumulator 21. The gaseous refrigerant separated in the accumulator 21 is drawn into the compressor 11 and compressed again (from point d7 to point a7 in Figure 7).

[0228] In the indoor air conditioning unit 50 operating in standalone indoor air adsorption heating mode, indoor air introduced via the indoor / outdoor air switching device 53 is drawn into the blower 52 and blown out. In standalone indoor air adsorption heating mode, the auxiliary outdoor air door 57 blocks the outdoor air bypass passage 55c. As a result, the entire volume of indoor air blown from the blower 52 flows into the indoor evaporator 18.

[0229] In standalone indoor air adsorption heating mode, no refrigerant is introduced into the indoor evaporator 18. As a result, the indoor air that enters the indoor evaporator 18 lowers the temperature of the indoor evaporator 18, which became relatively hot during the decompression heating mode, from the surface (i.e., outer surface) side as it passes through the indoor evaporator 18. This causes the moisture contained in the indoor air to be adsorbed by the adsorbent 18a of the indoor evaporator 18, thereby dehumidifying the indoor air.

[0230] The indoor air, dehumidified by the adsorbent 18a of the indoor evaporator 18, flows into the heating passage 55a and the cold air bypass passage 55b depending on the opening of the air mix door 54. The air flowing into the heating passage 55a is heated as it passes through the indoor condenser 12 as blown air and flows into the mixing space 56. The air flowing into the cold air bypass passage 55b flows into the mixing space 56 as blown air because the exhaust door 58 is blocking the exhaust port 51a.

[0231] The air, mixed and temperature-controlled in the mixing space 56, is blown through the openings to the appropriate locations within the vehicle interior. This achieves dehumidification and heating within the vehicle interior. Other operations are the same as in the detachable heating mode.

[0232] Furthermore, in the internal air adsorption heating mode, similar to the decompression heating mode, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be lowered compared to the series dehumidification heating mode, thereby increasing the amount of heat absorbed by the refrigerant. Consequently, in the internal air adsorption heating mode, the heating capacity of the blown air in the indoor condenser 12 can be improved compared to the series dehumidification heating mode.

[0233] Furthermore, in the internal air adsorption heating mode, internal air at a higher temperature than the outside air is introduced as the blown air. Therefore, compared to the case where outside air is introduced, the energy consumed in the indoor condenser 12 to heat the blown air to the desired temperature can be reduced. In addition, in the internal air adsorption heating mode, moisture contained in the blown air can be adsorbed by the adsorbent 18a, so fogging of the vehicle windows can be suppressed.

[0234] (c-2-2) Cooling internal air adsorption heating mode The cooling internal air adsorption heating mode is selected when it is determined that it is necessary to cool the battery 80 using the cooling capacity of the heat pump cycle 10 after the detachable heating mode has finished.

[0235] In the heat pump cycle 10 of the cooling internal air adsorption heating mode, the control device 70 throttles the heating expansion valve 14a, fully closes the cooling expansion valve 14b, and throttles the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, the second on-off valve 15b, the third on-off valve 15c, closes the fourth on-off valve 15d, and opens the fifth on-off valve 15e.

[0236] Therefore, in the cooling indoor air adsorption heating mode heat pump cycle 10, as shown by the white arrows in Figure 6, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, heating expansion valve 14a, outdoor heat exchanger 16, accumulator 21, and the suction side of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, cooling expansion valve 14c, refrigerant passage of chiller 19, and the suction side of the compressor 11. In other words, in the cooling indoor air adsorption heating mode, the refrigerant is routed to bypass the indoor evaporator 18, and the outdoor heat exchanger 16 and chiller 19 are switched to a refrigerant circuit that connects in parallel with the refrigerant flow.

[0237] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14c so that it becomes a predetermined throttle opening for the cooling internal air adsorption heating mode. In addition, the control device 70 controls the operation of other controlled devices in the same way as the standalone internal air adsorption heating mode.

[0238] Therefore, in the heat pump cycle 10 of the cooling indoor air adsorption heating mode, a vapor compression type refrigeration cycle is configured in which the indoor condenser 12 functions as a condenser, and the outdoor heat exchanger 16 and chiller 19 function as evaporators.

[0239] In the indoor condenser 12, the blown air is heated, similar to the standalone indoor adsorption heating mode. In the chiller 19, the heat transfer medium is cooled, similar to the cooling mode.

[0240] In the low-temperature side heat transfer medium circuit 30a of the cooling internal air adsorption heating mode, the heat transfer medium flows into the cooling water passage 80a of the battery 80, similar to the cooling air conditioning mode. This cools the battery 80. Other operations are the same as in the standalone internal air adsorption heating mode.

[0241] Therefore, in the cooling internal air adsorption heating mode, dehumidification and heating of the vehicle interior can be performed, similar to the standalone internal air adsorption heating mode. Furthermore, in the cooling internal air adsorption heating mode, the battery 80 can be cooled using the cooling capacity of the heat pump cycle 10, similar to the cooling air conditioning mode.

[0242] (c-3-1) Standalone low-temperature adsorption heating mode The standalone low-temperature adsorption heating mode is selected when it is determined that anti-fogging of the vehicle's windows is necessary while the standalone internal air adsorption heating mode is running.

[0243] In the heat pump cycle 10 of the standalone low-temperature adsorption heating mode, the control device 70 throttles the heating expansion valve 14a, throttles the cooling expansion valve 14b, and fully closes the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, the second on-off valve 15b, the third on-off valve 15c, closes the fourth on-off valve 15d, and closes the fifth on-off valve 15e.

[0244] Therefore, in the heat pump cycle 10 of the standalone low-temperature adsorption heating mode, as shown by the black arrows in Figure 8, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, heating expansion valve 14a, outdoor heat exchanger 16, accumulator 21, and the suction side of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, accumulator 21, and the suction side of the compressor 11. In other words, the outdoor heat exchanger 16 and the indoor evaporator 18 are switched to a refrigerant circuit that is connected in parallel with respect to the refrigerant flow.

[0245] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14b so that the evaporator temperature Tefin approaches the internal air temperature Tr. In addition, the control device 70 controls the operation of other controlled equipment in the same way as in the standalone internal air adsorption heating mode.

[0246] Therefore, in the heat pump cycle 10 of the standalone low-temperature adsorption heating mode, the state of the refrigerant changes as shown in the Mollier diagram in Figure 9. That is, the refrigerant discharged from the compressor 11 (point a9 in Figure 9) flows into the indoor condenser 12. The refrigerant that flows into the indoor condenser 12 condenses by releasing heat into the blown air flowing through the heating passage 55a (from point a9 to point b9 in Figure 9). As a result, the blown air is heated.

[0247] The flow of refrigerant discharged from the indoor condenser 12 is branched at the first three-way joint 13a. One of the refrigerant branches off at the first three-way joint 13a flows into the heating expansion valve 14a and is depressurized (from point b9 to point c9 in Figure 9). The refrigerant depressurized at the heating expansion valve 14a flows into the outdoor heat exchanger 16. The refrigerant that flows into the outdoor heat exchanger 16 absorbs heat from the outside air and evaporates (from point c9 to point d9 in Figure 9).

[0248] The other refrigerant, branched off at the first three-way joint 13a, flows into the cooling expansion valve 14b and is depressurized (from point b9 to point e9 in Figure 9). The refrigerant, depressurized in the cooling expansion valve 14b, flows into the indoor evaporator 18. The refrigerant that flows into the indoor evaporator 18 absorbs heat from the indoor evaporator 18 and the surrounding air and evaporates (from point e9 to point f9 in Figure 9). The refrigerant that flows out of the indoor evaporator 18 is depressurized in the evaporation pressure regulating valve 20 (from point f9 to point d9 in Figure 9).

[0249] The flow of refrigerant discharged from the outdoor heat exchanger 16 and the flow of refrigerant discharged from the evaporation pressure regulating valve 20 merge at the sixth three-way joint 13f. The refrigerant discharged from the sixth three-way joint 13f flows into the accumulator 21. The gaseous refrigerant separated in the accumulator 21 is drawn into the compressor 11 and compressed again (from point d9 to point a9 in Figure 9). Other operations are the same as in the standalone indoor adsorption heating mode. Therefore, in standalone low-temperature adsorption heating mode, dehumidification and heating of the vehicle interior can be performed in the same way as in standalone internal air adsorption heating mode.

[0250] Furthermore, in the low-temperature adsorption heating mode, similar to the desorption heating mode, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be lowered compared to the series dehumidification heating mode, thereby increasing the amount of heat absorbed by the refrigerant. Consequently, in the low-temperature adsorption heating mode, the heating capacity of the blown air in the indoor condenser 12 can be improved compared to the series dehumidification heating mode.

[0251] Furthermore, in the low-temperature adsorption heating mode, indoor air at a higher temperature than the outside air is introduced as the blown air. Therefore, similar to the indoor air adsorption heating mode, the energy consumed in the indoor condenser 12 to heat the blown air to the desired temperature can be reduced.

[0252] Furthermore, in the low-temperature adsorption heating mode, refrigerant is introduced into the indoor evaporator 18, so the temperature of the adsorbent 18a can be brought closer to the indoor temperature Tr not only on the surface side but also on the deeper side (i.e., the part closer to the indoor evaporator 18 than the outer surface). Therefore, in the low-temperature adsorption heating mode, the amount of moisture adsorbed by the adsorption part 18a can be increased compared to the indoor air adsorption heating mode. As a result, fogging of the vehicle windows can be suppressed in the low-temperature adsorption heating mode.

[0253] (c-3-2) Cooling Low Temperature Adsorption Heating Mode The cooling low-temperature adsorption heating mode is selected when it is determined that anti-fogging of the vehicle windows is necessary while the cooling internal air adsorption heating mode is running.

[0254] In the cooling low-temperature adsorption heating mode heat pump cycle 10, the control device 70 throttles the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c. The control device 70 also opens the first on-off valve 15a, the second on-off valve 15b, the third on-off valve 15c, closes the fourth on-off valve 15d, and opens the fifth on-off valve 15e.

[0255] Therefore, in the heat pump cycle 10 of the standalone low-temperature adsorption heating mode, as shown by the white arrows in Figure 8, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, heating expansion valve 14a, outdoor heat exchanger 16, accumulator 21, and the suction side of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, accumulator 21, and the suction side of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: indoor condenser 12, cooling expansion valve 14c, refrigerant passage of chiller 19, accumulator 21, and the suction side of the compressor 11. In other words, the outdoor heat exchanger 16, indoor evaporator 18, and chiller 19 are switched to a refrigerant circuit that is connected in parallel with the refrigerant flow.

[0256] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14c so that it becomes a predetermined throttle opening for the cooling low-temperature adsorption heating mode. In addition, the control device 70 controls the operation of other controlled devices in the same way as the standalone low-temperature adsorption heating mode.

[0257] Therefore, in the cooling low-temperature adsorption heating mode heat pump cycle 10, a vapor compression type refrigeration cycle is configured in which the indoor condenser 12 functions as a condenser, and the outdoor heat exchanger 16, indoor evaporator 18, and chiller 19 function as evaporators.

[0258] In the indoor condenser 12, the blown air is heated, similar to the standalone low-temperature adsorption heating mode. In the indoor evaporator 18, the indoor evaporator 18 and the indoor air are cooled, similar to the standalone low-temperature adsorption heating mode. In the chiller 19, the heat transfer medium is cooled, similar to the cooling mode.

[0259] In the low-temperature side heat transfer medium circuit 30a of the cooling low-temperature adsorption heating mode, the heat transfer medium flows into the cooling water passage 80a of the battery 80, similar to the cooling mode. This cools the battery 80. Other operations are the same as in the standalone low-temperature adsorption heating mode.

[0260] Therefore, in the cooling low-temperature adsorption heating mode, dehumidification and heating of the vehicle interior can be performed, similar to the standalone low-temperature adsorption heating mode. Furthermore, in the cooling low-temperature adsorption heating mode, the battery 80 can be cooled using the cooling capacity of the heat pump cycle 10, similar to the cooling air conditioning mode.

[0261] As described above, the vehicle air conditioning system 1 of this embodiment makes it possible to achieve comfortable air conditioning inside the vehicle and appropriate temperature control of the battery 80, which is an in-vehicle device, by switching the operating mode.

[0262] Furthermore, in the heating mode of the vehicle air conditioning system 1 of this embodiment, during the internal air adsorption heating mode and the low-temperature adsorption heating mode, internal air with a higher temperature than the outside air is introduced as the blown air. Therefore, compared to the case where outside air is introduced as the blown air, the energy consumed in the indoor condenser 12, which is the heating unit, to heat the blown air to the desired temperature can be reduced.

[0263] In addition, the heating mode of the vehicle air conditioning system 1 in this embodiment performs an internal air adsorption heating mode, which significantly reduces the energy consumed to dehumidify the blown air.

[0264] More specifically, in the indoor air adsorption heating mode, the refrigerant circuit of the heat pump cycle 10 is switched to a refrigerant circuit that bypasses the indoor evaporator 18 and allows the refrigerant to flow through it. In other words, the refrigerant circuit of the heat pump cycle 10 is switched to a refrigerant circuit that does not allow the refrigerant to flow into the indoor evaporator 18. Therefore, unnecessary energy is not consumed in order to allow the refrigerant to flow into the indoor evaporator 18.

[0265] As a result, the vehicle air conditioning system 1 of this embodiment can fully achieve the energy consumption reduction effect by providing an indoor evaporator 18 having an adsorbent 18a. In other words, it is possible to sufficiently reduce the energy consumed when heating the vehicle interior while dehumidifying the blown air.

[0266] Furthermore, in the vehicle air conditioning system 1 of this embodiment, when it is determined that fogging of the vehicle windows is necessary while the internal air adsorption heating mode is being executed, the system switches to the low-temperature adsorption heating mode. In the low-temperature adsorption heating mode, the throttle opening of the cooling expansion valve 14b is controlled so that the evaporator temperature Tefin approaches the internal air temperature Tr. This makes it possible to bring the temperature of the deep part of the adsorbent 18a closer to the internal air temperature Tr.

[0267] Therefore, in the low-temperature adsorption heating mode, the amount of moisture adsorbed by the adsorption unit 18a can be increased compared to the internal air adsorption heating mode. Furthermore, in the low-temperature adsorption heating mode, the temperature of the refrigerant flowing into the indoor evaporator 18 is not unnecessarily lowered, so dehumidifying and heating of the vehicle interior can be continued while suppressing the increase in energy consumed to dehumidify the blown air.

[0268] Furthermore, the vehicle air conditioning system 1 of this embodiment is equipped with a humidity sensor 76 as a window fogging detection unit, so that the detachable heating mode, the internal air adsorption heating mode, and the low-temperature adsorption heating mode can be appropriately switched to prevent fogging of the vehicle windows.

[0269] Furthermore, in the vehicle air conditioning system 1 of this embodiment, an adsorbent 18a that satisfies the above-mentioned formula F1 is used as the adsorption part. With this, when switching to the internal air adsorption heating mode, moisture can be quickly adsorbed onto the adsorbent 18a. Moreover, in the desorption heating mode, the moisture adsorbed onto the adsorbent 18a can be sufficiently desorbed.

[0270] More specifically, the indoor air adsorption heating mode is executed immediately after the desorption heating mode. Therefore, the temperature of the indoor evaporator 18 and the adsorbent 18a immediately after the start of the indoor air adsorption heating mode is close to the reference desorption temperature KTe1 (50°C in this embodiment). Consequently, it is desirable that the adsorbent 18a can begin adsorbing moisture contained in the blown air even at a relatively high temperature. In other words, it is desirable that the adsorption start temperature of the adsorbent 18a be relatively high.

[0271] In contrast, in this embodiment, an adsorbent 18a is used in the indoor air adsorption heating mode, based on the typical temperature and humidity of the indoor air flowing into the indoor evaporator 18 (specifically, around 25°C and 38% relative humidity), such that the maximum relative pressure ratio Rmax is 0.35 or less.

[0272] According to this, as shown by the line of 35% relative humidity in FIG. 10 corresponding to the case where the maximum relative pressure ratio Rmax is 0.35, the adsorption start temperature can also be set to a relatively high temperature. Therefore, even when the temperature of the adsorbent 18a is relatively high, the moisture contained in the blown air can be adsorbed by the adsorbent 18a.

[0273] Also, as described using FIG. 2, in the adsorbent 18a, as the maximum relative pressure ratio Rmax decreases, the adsorption rate (kg / s) tends to increase. That is, if an adsorbent 18a with a small maximum relative pressure ratio Rmax is adopted, it is easier to dehumidify the blown air, and the time for preventing window clouding of the vehicle window glass becomes longer.

[0274] Therefore, in order to quickly dehumidify the blown air in the internal air adsorption heating mode, it is desirable to adopt an adsorbent 18a with a small maximum relative pressure ratio Rmax. However, in an adsorbent 18a with a small maximum relative pressure ratio Rmax, even if the temperature of the adsorbent 18a is raised until it reaches the reference desorption temperature KTe1, there is a possibility that sufficient desorption of the adsorbent 18a cannot be achieved.

[0275] In contrast, in the present embodiment, based on the general temperature and humidity of the internal air flowing into the indoor evaporator 18 in the internal air adsorption heating mode, an adsorbent 18a with a maximum relative pressure ratio Rmax of 0.05 or more is adopted.

[0276] According to this, as shown by the line of 5% relative humidity in FIG. 10 corresponding to the case where the maximum relative pressure ratio Rmax is 0.05, by raising the temperature of the adsorbent 18a to the reference desorption temperature KTe1, a sufficient desorption amount can be ensured. That is, the moisture adsorbed by the adsorbent 18a can be sufficiently desorbed.

[0277] (Second Embodiment) In this embodiment, the vehicle air conditioner 1a shown in the overall configuration diagram of FIG. 11 will be described. The vehicle air conditioner 1a includes a heat pump cycle 10a, a low-temperature side heat medium circuit 30a, a high-temperature side heat medium circuit 30b, an indoor air conditioner unit 50, and the like. In FIG. 11, the indoor air conditioner unit 50 is omitted for clarity of illustration.

[0278] In the heat pump cycle 10a, compared with the heat pump cycle 10 described in the first embodiment, the indoor condenser 12, the heating expansion valve 14a, the first to third on-off valves 15a to 15c, the outdoor heat exchanger 16, the accumulator 21, etc. have been abolished.

[0279] Therefore, in the heat pump cycle 10a, the inlet side of the refrigerant passage of the water-cooled refrigerant heat exchanger 121 is connected to the discharge port of the compressor 11. The water-cooled refrigerant heat exchanger 121 has a refrigerant passage through which the refrigerant discharged from the compressor 11 flows, and a heat medium passage through which the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 30b flows.

[0280] The water-cooled refrigerant heat exchanger 121 is a high-temperature side heat medium heat exchange section that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature side heat medium flowing through the heat medium passage. In the water-cooled refrigerant heat exchanger 121, the heat possessed by the high-pressure refrigerant is radiated to the high-temperature side heat medium to heat the high-temperature side heat medium.

[0281] The inlet side of the receiver 22 is connected to the outlet of the refrigerant passage of the water-cooled refrigerant heat exchanger 121. The receiver 22 is a high-pressure side gas-liquid separator that separates the gas and liquid of the high-pressure refrigerant flowing out from the refrigerant passage of the water-cooled refrigerant heat exchanger 121 and stores the separated liquid-phase refrigerant as the surplus refrigerant in the cycle.

[0282] The inlet side of the fifth three-way joint 13e is connected to the liquid-phase refrigerant outlet of the receiver 22. The inlet side of the cooling expansion valve 14b is connected to one of the outlets of the fifth three-way joint 13e, similar to the first embodiment. The inlet side of one of the seventh three-way joints 13g is connected to the other outlet of the fifth three-way joint 13e.

[0283] Furthermore, the outlet side of the second check valve 17b in this embodiment is connected to the inlet side of the eighth three-way joint 13h. Therefore, the second check valve 17b in this embodiment allows refrigerant to flow from the indoor evaporator 18 side to the eighth three-way joint 13h side, and prevents refrigerant from flowing from the eighth three-way joint 13h side to the indoor evaporator 18 side.

[0284] One outlet of the eighth three-way joint 13h is connected to one inlet side of the sixth three-way joint 13f via the fifth on-off valve 15e. The other outlet of the eighth three-way joint 13h is connected to the other inlet side of the seventh three-way joint 13g via the fourth on-off valve 15d.

[0285] The outlet of the seventh three-way joint 13g is connected to the inlet side of the cooling expansion valve 14d. The outlet of the cooling expansion valve 14d is connected to the inlet side of the refrigerant passage of the chiller 19a. The outlet of the refrigerant passage of the chiller 19a is connected to the other inlet side of the sixth three-way joint 13f. The cooling expansion valve 14d and chiller 19a in this embodiment have the same configuration as the cooling expansion valve 14c and chiller 19 described in the first embodiment.

[0286] Therefore, in this embodiment, the refrigerant flow path from the other outlet of the fifth three-way joint 13e to one inlet of the seventh three-way joint 13g becomes a refrigerant bypass passage that, in the indoor air adsorption heating mode, guides the refrigerant flowing out from the receiver 22 to the suction port side of the compressor 11, bypassing the indoor evaporator 18. The other configurations of the heat pump cycle 10a are the same as those of the heat pump cycle 10 described in the first embodiment.

[0287] Next, the low-temperature side heat transfer medium circuit 30a will be described. The low-temperature side heat transfer medium circuit 30a of this embodiment has a first low-temperature side heat transfer medium three-way valve 32a and a second low-temperature side heat transfer medium three-way valve 32b. The first low-temperature side heat transfer medium three-way valve 32a has the same configuration as the low-temperature side heat transfer medium three-way valve 32a described in the second embodiment. The basic configuration of the second low-temperature side heat transfer medium three-way valve 32b is the same as that of the first low-temperature side heat transfer medium three-way valve 32a.

[0288] In the low-temperature side heat transfer medium circuit 30a of this embodiment, the inlet side of the second low-temperature side heat transfer medium three-way valve 32b is connected to the outlet of the heat transfer medium passage of the chiller 19a. The inlet side of the cooling water passage 80a of the battery 80 is connected to one outlet of the second low-temperature side heat transfer medium three-way valve 32b. The inlet side of the second heat transfer medium three-way joint 33b is connected to the outlet of the cooling water passage 80a of the battery 80.

[0289] The other outlet of the second low-temperature side heat transfer medium three-way valve 32b is connected to the other inlet side of the second heat transfer medium three-way connector 33b via a battery bypass passage 35b. The outlet of the second heat transfer medium three-way connector 33b is connected to the inlet of the first low-temperature side heat transfer medium three-way valve 32a. The other configurations are the same as those of the low-temperature side heat transfer medium circuit 30a in the first embodiment.

[0290] In the low-temperature side heat transfer circuit 30a, the chiller 19a can exchange heat between the low-pressure refrigerant, which has been depressurized by the cooling expansion valve 14d, and the heat transfer medium. Furthermore, the low-temperature side radiator 34a exchanges heat between the heat transfer medium and the outside air. In other words, the chiller 19a can indirectly exchange heat between the refrigerant and the outside air via the heat transfer medium.

[0291] Therefore, the chiller 19a of the heat pump cycle 10a becomes the refrigerant-to-outside air heat exchange section. Furthermore, the cooling expansion valve 14d becomes the outside air side pressure reduction section, which reduces the pressure of the refrigerant flowing into the refrigerant passage of the chiller 19, which is the refrigerant-to-outside air heat exchange section.

[0292] Next, the high-temperature side heat transfer fluid circuit 30b will be described. The high-temperature side heat transfer fluid circuit 30b is a circuit that circulates the heat transfer fluid. In the high-temperature side heat transfer fluid circuit 30b, the same type of fluid as in the low-temperature side heat transfer fluid circuit 30a is circulated as the heat transfer fluid. The high-temperature side heat transfer fluid circuit 30b is equipped with a high-temperature side heat transfer fluid pump 31b, a heat transfer fluid passage of the water-refrigerant heat exchanger 121, a high-temperature side heat transfer fluid three-way valve 32c, a heater core 36, a high-temperature side radiator 34b, and the like.

[0293] The high-temperature side heat transfer pump 31b is a heat transfer pumping unit that pressurizes the high-temperature side heat transfer fluid that has flowed out from the third heat transfer fluid three-way joint 33c to the heat transfer fluid passage of the water refrigerant heat exchanger 121. The basic configuration of the high-temperature side heat transfer pump 31b is the same as that of the low-temperature side heat transfer pump 31a.

[0294] The outlet of the heat transfer medium passage of the water refrigerant heat exchanger 121 is connected to the inlet side of the high-temperature side heat transfer medium three-way valve 32c. The basic configuration of the high-temperature side heat transfer medium three-way valve 32c is the same as that of the first low-temperature side heat transfer medium three-way valve 32a. One outlet of the high-temperature side heat transfer medium three-way valve 32c is connected to the heat transfer medium inlet side of the heater core 36. The other outlet of the high-temperature side heat transfer medium three-way valve 32c is connected to the heat transfer medium inlet side of the high-temperature side radiator 34b.

[0295] The heater core 36 is located inside the air conditioning case 51 of the indoor air conditioning unit 50, similar to the indoor condenser 12 described in the first embodiment. The heater core 36 is a high-temperature side air heat exchange section that exchanges heat between the heat transfer medium that has flowed out of the water refrigerant heat exchanger 121 and the blown air that has passed through the indoor evaporator 18. In the heater core 36, the heat contained in the heat transfer medium that has flowed out of the water refrigerant heat exchanger 121 is released into the blown air, thereby heating the blown air. One inlet side of the third heat transfer medium three-way joint 33c is connected to the heat transfer medium outlet of the heater core 36.

[0296] The high-temperature side radiator 34b is a high-temperature side heat exchanger that exchanges heat between the heat transfer medium flowing out from the high-temperature side heat transfer medium three-way valve 32c and outside air blown by an outside air fan (not shown). The high-temperature side radiator 34b is located on the front side of the drive unit cabin. Therefore, when the vehicle is running, the airflow from the vehicle can be directed onto the low-temperature side radiator 34a. The high-temperature side radiator 34b may be integrally formed with the low-temperature side radiator 34a and the outdoor heat exchanger 16.

[0297] The outlet of the high-temperature side radiator 34b is connected to the other inlet side of the third heat transfer fluid three-way joint 33c. The outlet of the third heat transfer fluid three-way joint 33c is connected to the suction side of the high-temperature side heat transfer fluid pump 31b.

[0298] In the high-temperature-side heat medium circuit 30b, in the water-cooled medium heat exchanger 121, the refrigerant discharged from the compressor 11 can be heat-exchanged with the high-temperature-side heat medium to heat the high-temperature-side heat medium. Further, in the heater core 36, the high-temperature-side heat medium heated by the water-cooled medium heat exchanger 121 can be heat-exchanged with the blown air to heat the blown air.

[0299] Therefore, each component device arranged in the water-cooled medium heat exchanger 121 and the high-temperature-side heat medium circuit 30b of the present embodiment is a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source.

[0300] Next, the electric control unit of the vehicle air conditioner 1a will be described. In the present embodiment, as sensors for control connected to the control device 70, a low-temperature-side heat medium temperature sensor 73a and a high-temperature-side heat medium temperature sensor 73b are added.

[0301] The low-temperature-side heat medium temperature sensor 73a is a low-temperature-side heat medium temperature detection unit that detects the low-temperature-side heat medium temperature TWL, which is the temperature of the low-temperature-side heat medium flowing into the cooling water passage 80a of the battery 80. The high-temperature-side heat medium temperature sensor 73b is a high-temperature-side heat medium temperature detection unit that detects the high-temperature-side heat medium temperature TWH, which is the temperature of the high-temperature-side heat medium flowing into the heater core 36. Other configurations are the same as those of the vehicle air conditioner 1 of the first embodiment.

[0302] Next, the operation of the vehicle air conditioner 1a of the present embodiment will be described. In the vehicle air conditioner 1a, various operation modes can be switched. Specifically, in the vehicle air conditioner 1a, the cooling mode and the heating mode can be switched.

[0303] Furthermore, in the control program of the present embodiment, under the same conditions as in the first embodiment, as the cooling mode, the single cooling mode and the cooling-cooling mode are selected. As the heating mode, the desorption heating mode, the internal air adsorption heating mode, and the low-temperature adsorption heating mode are selected. Hereinafter, each operation mode will be described.

[0304] (a-1) Single cooling mode In the standalone cooling mode heat pump cycle 10a, the control device 70 throttles the cooling expansion valve 14b and fully closes the cooling expansion valve 14d. The control device 70 also closes the fourth on-off valve 15d and opens the fifth on-off valve 15e.

[0305] Therefore, in the standalone cooling mode heat pump cycle 10a, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: refrigerant passage of the water refrigerant heat exchanger 121, receiver 22, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, and the intake side of the compressor 11.

[0306] Furthermore, the control device 70 controls the operation of the cooling expansion valve 14b so that the superheat SH of the suction refrigerant drawn into the compressor 11 approaches a predetermined reference superheat KSH (5°C in this embodiment). The control device 70 detects the superheat SH based on the evaporator temperature Tefin and the chiller-side refrigerant pressure Pc.

[0307] In the low-temperature side heat transfer medium circuit 30a in standalone cooling mode, the control device 70 operates the low-temperature side heat transfer medium pump 31a to achieve a predetermined reference pumping capacity. The control device 70 also controls the operation of the first low-temperature side heat transfer medium three-way valve 32a and the second low-temperature side heat transfer medium three-way valve 32b so that the low-temperature side heat transfer medium temperature TWL detected by the low-temperature side heat transfer medium temperature sensor 73a approaches a predetermined reference low-temperature side heat transfer medium temperature KTWL.

[0308] In the high-temperature side heat transfer medium circuit 30b of the standalone cooling mode, the control device 70 operates the high-temperature side heat transfer medium pump 31b to exert a predetermined standard pumping capacity. The control device 70 also controls the operation of the high-temperature side heat transfer medium three-way valve 32c so that the high-temperature side heat transfer medium temperature TWH detected by the high-temperature side heat transfer medium temperature sensor 73b approaches a predetermined standard high-temperature side heat transfer medium temperature KTWH.

[0309] In the indoor air conditioning unit 50 in standalone cooling mode, the control device 70 controls the operation of each controlled device, similar to the standalone cooling mode described in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices, similar to the standalone cooling mode described in the first embodiment.

[0310] Therefore, in the standalone cooling mode heat pump cycle 10a, a vapor compression type refrigeration cycle is configured in which the water refrigerant heat exchanger 121 functions as a condenser and the indoor evaporator 18 functions as an evaporator.

[0311] In the water refrigerant heat exchanger 121, the heat contained in the refrigerant is released to the high-temperature side heat transfer medium. This heats up the high-temperature side heat transfer medium. In the indoor evaporator 18, the refrigerant absorbs heat from the blown air and evaporates. This cools the blown air.

[0312] In the low-temperature heat transfer medium circuit 30a of the standalone cooling mode, similar to the first embodiment, the low-temperature heat transfer medium pumped from the low-temperature heat transfer medium pump 31a flows into the heat transfer medium passage of the chiller 19. Since no refrigerant is circulating in the refrigerant passage, the heat transfer medium that has flowed into the heat transfer medium passage of the chiller 19 flows out of the chiller 19 without any temperature change.

[0313] The heat transfer fluid discharged from the chiller 19 flows into the cooling water passage 80a of the battery 80, depending on the opening degree of the second low-temperature side heat transfer fluid three-way valve 32b. This cools the battery 80. The flow of the low-temperature side heat transfer fluid discharged from the cooling water passage 80a and the flow of the low-temperature side heat transfer fluid discharged from the battery bypass passage 35b merge at the second heat transfer fluid three-way joint 33b.

[0314] The heat transfer fluid that flows out from the second heat transfer fluid three-way joint 33b flows into the low-temperature side radiator 34a in accordance with the opening degree of the first low-temperature side heat transfer fluid three-way valve 32a. As a result, the heat contained in the low-temperature side heat transfer fluid is dissipated to the outside air, similar to the first embodiment. The flow of the low-temperature side heat transfer fluid that flows out from the low-temperature side radiator 34a and the flow of the low-temperature side heat transfer fluid that flows out from the radiator bypass passage 35a merge at the first heat transfer fluid three-way joint 33a.

[0315] The heat transfer fluid that flows out from the first heat transfer fluid three-way joint 33a is drawn into the low-temperature side heat transfer fluid pump 31a and pumped under pressure towards the heat transfer fluid passage of the chiller 19.

[0316] In the high-temperature heat transfer medium circuit 30b of the standalone cooling mode, the high-temperature heat transfer medium pumped from the high-temperature heat transfer medium pump 31b flows into the heat transfer medium passage of the water refrigerant heat exchanger 121. The high-temperature heat transfer medium that flows into the water refrigerant heat exchanger 121 is heated by heat exchange with the refrigerant flowing through the refrigerant passage. The high-temperature heat transfer medium that flows out of the water refrigerant heat exchanger 121 flows into the heater core 36 and the high-temperature radiator 34b according to the opening degree of the high-temperature heat transfer medium three-way valve 32c.

[0317] The high-temperature heat transfer fluid that flows into the heater core 36 releases heat into the blown air. This heats the blown air. The high-temperature heat transfer fluid that flows into the high-temperature radiator 34b releases heat into the outside air. The flow of high-temperature heat transfer fluid that flows out of the heater core 36 and the flow of high-temperature heat transfer fluid that flows out of the high-temperature radiator 34b merge at the third heat transfer fluid three-way joint 33c.

[0318] The heat transfer fluid that flows out from the third heat transfer fluid three-way joint 33c is drawn into the high-temperature side heat transfer fluid pump 31b and pumped under pressure towards the heat transfer fluid passage of the water refrigerant heat exchanger 121.

[0319] In the standalone cooling mode of the indoor air conditioning unit 50, similar to the standalone cooling mode of the first embodiment, the temperature-adjusted air in the mixing space 56 is blown out to appropriate locations within the vehicle interior. This achieves cooling within the vehicle interior.

[0320] (a-2) Cooling mode In the cooling mode heat pump cycle 10a, the control device 70 throttles the cooling expansion valve 14b and the cooling expansion valve 14d. The control device 70 also closes the fourth on-off valve 15d and opens the fifth on-off valve 15e.

[0321] Therefore, in the cooling mode heat pump cycle 10a, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: refrigerant passage of the water refrigerant heat exchanger 121, receiver 22, cooling expansion valve 14b, indoor evaporator 18, evaporation pressure regulating valve 20, and the suction side of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: refrigerant passage of the water refrigerant heat exchanger 121, receiver 22, cooling expansion valve 14d, refrigerant passage of the chiller 19, and the suction side of the compressor 11. In other words, in the cooling mode, the indoor evaporator 18 and chiller 19 are switched to a refrigerant circuit that is connected in parallel with respect to the refrigerant flow.

[0322] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14d so that it becomes a throttle opening predetermined for the cooling mode. In addition, the control device 70 controls the operation of other controlled equipment, similar to the standalone cooling mode.

[0323] Therefore, in the cooling mode heat pump cycle 10a, a vapor compression type refrigeration cycle is configured in which the water refrigerant heat exchanger 121 functions as a condenser and the indoor evaporator 18 and chiller 19 function as evaporators.

[0324] In the water refrigerant heat exchanger 121, the high-temperature side heat transfer medium is heated, similar to the standalone cooling mode. In the indoor evaporator 18, the blown air is cooled, similar to the standalone cooling mode. Furthermore, in the chiller 19, the refrigerant absorbs heat from the low-temperature side heat transfer medium and evaporates. This cools the low-temperature side heat transfer medium.

[0325] In the cooling mode, the low-temperature heat transfer medium circuit 30a flows into the heat transfer medium passage of the chiller 19, pressurized by the low-temperature heat transfer medium pump 31a. The low-temperature heat transfer medium that flows into the heat transfer medium passage of the chiller 19 is cooled by the refrigerant absorbing heat. The low-temperature heat transfer medium cooled by the chiller 19 flows into the cooling water passage 80a of the battery 80. This cools the battery 80. Other operations are the same as in the standalone cooling mode.

[0326] Therefore, in cooling mode, the vehicle interior can be cooled in the same way as in standalone cooling mode. Furthermore, in cooling mode, the battery 80 can be cooled by utilizing the cooling capacity of the heat pump cycle 10a.

[0327] (c-1) Detachable heating mode In the detachable heating mode heat pump cycle 10a, the control device 70 throttles the cooling expansion valve 14b and the cooling expansion valve 14d. The control device 70 also opens the fourth on-off valve 15d and closes the fifth on-off valve 15e.

[0328] Therefore, in the detachable heating mode heat pump cycle 10a, as shown by the black arrows in Figure 12, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: refrigerant passage of the water refrigerant heat exchanger 121, receiver 22, cooling expansion valve 14b, indoor evaporator 18, cooling expansion valve 14d, refrigerant passage of the chiller 19, and the intake side of the compressor 11.

[0329] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14b so that the evaporator temperature Tefin approaches the reference desorption temperature KTe1. The control device 70 also controls the operation of the cooling expansion valve 14d so that the superheat SH of the suction refrigerant drawn into the compressor 11 approaches a predetermined reference superheat KSH (5°C in this embodiment). The control device 70 detects the superheat SH based on the chiller-side refrigerant temperature Tc and chiller-side refrigerant pressure Pc.

[0330] In the detachable heating mode, the low-temperature heat transfer fluid circuit 30a and the high-temperature heat transfer fluid circuit 30b are controlled by the control device 70 in the same way as in the cooling mode. In the heating mode, the high-temperature heat transfer fluid circuit 30b is controlled to ensure that the high-temperature heat transfer fluid flows into the heater core 36, and the operation of the high-temperature heat transfer fluid three-way valve 32c is controlled accordingly.

[0331] In the indoor air conditioning unit 50 in detachable heating mode, the control device 70 controls the operation of each controlled device in the same manner as described in the detachable heating mode in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices in the same manner as described in the detachable heating mode in the first embodiment.

[0332] Therefore, in the detachable heating mode heat pump cycle 10a, a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 121 and the indoor evaporator 18 function as condensers, and the chiller 19 function as an evaporator.

[0333] In the water refrigerant heat exchanger 121, the high-temperature side heat transfer medium is heated, similar to the standalone cooling mode. In the indoor evaporator 18, the temperature of the adsorbent 18a rises, and the moisture adsorbed on the adsorbent 18a is desorbed, similar to the desorption heating mode described in the first embodiment. In the chiller 19, the low-temperature side heat transfer medium is cooled, similar to the cooling mode.

[0334] In the detachable heating mode, the low-temperature side heat transfer fluid circuit 30a and the high-temperature side heat transfer fluid circuit 30b operate in the same manner as in the cooling mode. Other operations are the same as in the detachable heating mode described in the first embodiment.

[0335] Therefore, in the detachable heating mode, the vehicle interior can be heated while the adsorbent 18a is being attached and detached. Furthermore, in the detachable heating mode of this embodiment, the battery 80 can be cooled by utilizing the cooling capacity of the heat pump cycle 10a.

[0336] (c-2) Internal air adsorption heating mode In the heat pump cycle 10a of the internal air adsorption heating mode, the control device 70 closes the cooling expansion valve 14b completely and throttles the cooling expansion valve 14d. The control device 70 also closes the fourth on-off valve 15d and the fifth on-off valve 15e.

[0337] Therefore, in the internal air adsorption heating mode heat pump cycle 10a, as shown by the black arrows in Figure 13, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: refrigerant passage of the water refrigerant heat exchanger 121, receiver 22, cooling expansion valve 14d, refrigerant passage of the chiller 19, and the intake side of the compressor 11.

[0338] Furthermore, similar to the detachable heating mode, the control device 70 controls the operation of the cooling expansion valve 14d so that the superheat SH of the suction refrigerant drawn into the compressor 11 approaches a predetermined reference superheat KSH (5°C in this embodiment).

[0339] In the low-temperature side heat transfer medium circuit 30a and the high-temperature side heat transfer medium circuit 30b of the internal air adsorption heating mode, the control device 70 controls the operation of each controlled device in the same manner as in the cooling mode.

[0340] In the indoor air conditioning unit 50 operating in the internal air adsorption heating mode, the control device 70 controls the operation of each controlled device, similar to the internal air adsorption heating mode described in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices, similar to the cooling internal air adsorption heating mode described in the first embodiment.

[0341] Therefore, in the internal air adsorption heating mode heat pump cycle 10a, a vapor compression type refrigeration cycle is configured in which the water refrigerant heat exchanger 121 functions as a condenser and the chiller 19 functions as an evaporator.

[0342] In the water refrigerant heat exchanger 121, the high-temperature side heat transfer medium is heated, similar to the standalone cooling mode. In the chiller 19, the low-temperature side heat transfer medium is cooled, similar to the cooling mode.

[0343] In the internal air adsorption heating mode, the low-temperature side heat transfer fluid circuit 30a and the high-temperature side heat transfer fluid circuit 30b operate in the same manner as in the cooling mode. Other operations are the same as in the internal air adsorption heating mode described in the first embodiment.

[0344] Therefore, in the internal air adsorption heating mode, moisture contained in the internal air is adsorbed onto the adsorbent 18a, enabling dehumidification and heating of the vehicle interior. Furthermore, in the internal air adsorption heating mode, similar to the cooling mode, the cooling capacity of the heat pump cycle 10a can be used to cool the battery 80.

[0345] (c-3) Low-temperature adsorption heating mode In the low-temperature adsorption heating mode heat pump cycle 10a, the control device 70 throttles the cooling expansion valve 14b and the cooling expansion valve 14d. The control device 70 also closes the fourth on-off valve 15d and opens the fifth on-off valve 15e.

[0346] Therefore, in the low-temperature adsorption heating mode heat pump cycle 10a, the refrigerant circuit is switched to one similar to that of the cooling mode, as shown by the black-filled arrow in Figure 14. In other words, in the low-temperature adsorption heating mode, the indoor evaporator 18 and chiller 19 are switched to a refrigerant circuit in which they are connected in parallel with respect to the refrigerant flow.

[0347] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14b so that the evaporator temperature Tefin approaches the internal temperature Tr.

[0348] In the low-temperature adsorption heating mode, the low-temperature side heat transfer fluid circuit 30a and the high-temperature side heat transfer fluid circuit 30b are controlled by the control device 70 in the same manner as in the detachable heating mode.

[0349] In the indoor air conditioning unit 50 operating in low-temperature adsorption heating mode, the control device 70 controls the operation of each controlled device, similar to the low-temperature adsorption heating mode described in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices, similar to the cooling low-temperature adsorption heating mode described in the first embodiment.

[0350] Therefore, in the low-temperature adsorption heating mode heat pump cycle 10a, a vapor compression type refrigeration cycle is configured in which the water refrigerant heat exchanger 121 functions as a condenser and the indoor evaporator 18 and chiller 19 function as evaporators.

[0351] In the water refrigerant heat exchanger 121, the high-temperature side heat transfer medium is heated, similar to the standalone cooling mode. In the indoor evaporator 18, the adsorbent 18a is cooled so that it approaches the indoor temperature Tr. Furthermore, in the chiller 19, the refrigerant absorbs heat from the low-temperature side heat transfer medium and evaporates. This cools the low-temperature side heat transfer medium.

[0352] In the low-temperature adsorption heating mode, the low-temperature side heat transfer fluid circuit 30a and the high-temperature side heat transfer fluid circuit 30b operate in the same manner as in the cooling mode. Other operations are the same as in the cooling low-temperature adsorption heating mode described in the first embodiment.

[0353] Therefore, in the low-temperature adsorption heating mode, the amount of adsorption by the adsorbent 18a can be increased compared to the internal air adsorption heating mode, enabling dehumidifying and heating of the vehicle interior. Furthermore, in the low-temperature adsorption heating mode, the battery 80 can be cooled by utilizing the cooling capacity of the heat pump cycle 10a, similar to the cooling and refrigeration mode.

[0354] As described above, the vehicle air conditioning system 1a of this embodiment makes it possible to achieve comfortable air conditioning in the vehicle cabin and appropriate temperature control of the battery 80, which is an in-vehicle device, by switching the operating mode. Furthermore, the heating mode of the vehicle air conditioning system 1a of this embodiment can obtain the same effects as in the first embodiment.

[0355] In other words, in the internal air adsorption heating mode and the low-temperature adsorption heating mode, internal air at a higher temperature than the outside air is introduced as the blown air, thus reducing the energy consumed to heat the blown air in the heating unit. Furthermore, in the internal air adsorption heating mode, energy is not consumed to introduce a low-temperature refrigerant into the indoor evaporator 18.

[0356] Therefore, according to the vehicle air conditioning system 1a of this embodiment, the energy consumed when heating the vehicle interior while dehumidifying the blown air can be sufficiently reduced.

[0357] (Third embodiment) In this embodiment, the vehicle air conditioning system 1b shown in the overall configuration diagram of Figure 15 will be described. The vehicle air conditioning system 1b includes a heat pump cycle 10b, a low-temperature side heat transfer medium circuit 30a, a high-temperature side heat transfer medium circuit 30b, an indoor air conditioning unit 50, etc. Note that in Figure 15, the indoor air conditioning unit 50 is omitted for clarity of illustration.

[0358] In the heat pump cycle 10b, the receiver 22, cooling expansion valve 14d, fourth on-off valve 15d, fifth on-off valve 15e, indoor evaporator 18, etc., are eliminated compared to the heat pump cycle 10a described in the second embodiment.

[0359] Therefore, in the heat pump cycle 10b, the inlet side of the refrigerant passage of the water-refrigerant heat exchanger 121 is connected to the discharge port of the compressor 11. The inlet side of the cooling expansion valve 14c is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 121. Accordingly, the cooling expansion valve 14c in this embodiment is a refrigerant pressure reduction unit that reduces the pressure of the refrigerant that has flowed out of the water-refrigerant heat exchanger 121, which is the high-temperature side heat transfer medium heat exchange section.

[0360] The outlet of the cooling expansion valve 14c is connected to the inlet side of the accumulator 21. The outlet of the gas phase refrigerant of the accumulator 21 is connected to the suction side of the compressor 11.

[0361] Furthermore, the high-temperature side heat transfer medium circuit 30b and the low-temperature side heat transfer medium circuit 30a of this embodiment are configured to be connectable via the high-temperature side heat transfer medium passage 35c and the low-temperature side heat transfer medium passage 35d.

[0362] Therefore, in the low-temperature side heat transfer medium circuit 30a of this embodiment, compared to the second embodiment, the inlet side of the second heat transfer medium three-way joint 33b is connected to the outlet of the heat transfer medium passage of the chiller 19. The inlet side of the heat transfer medium of the low-temperature side radiator 34a is connected to one outlet of the second heat transfer medium three-way joint 33b. The inlet side of the first heat transfer medium three-way joint 33a is connected to the heat transfer medium outlet of the low-temperature side radiator 34a.

[0363] The inlet side of the first heat transfer medium flow rate control valve 39a is connected to the outlet of the second heat transfer medium three-way joint 33b. The first heat transfer medium flow rate control valve 39a adjusts the flow rate of the refrigerant flowing from the second heat transfer medium three-way joint 33b side to the fifth heat transfer medium three-way joint 33e side. The basic configuration of the first heat transfer medium flow rate control valve 39a is the same as that of the cooling expansion valve 14c for the refrigerant. The first heat transfer medium flow rate control valve 39a has a fully open function and a fully closed function.

[0364] Furthermore, the vehicle air conditioning system 1b of this embodiment is equipped with a second heat transfer medium flow rate control valve 39b, as will be described later. The basic configuration of the second heat transfer medium flow rate control valve 39b is the same as that of the first heat transfer medium flow rate control valve 39a.

[0365] Therefore, the first heat transfer medium flow rate control valve 39a and the second heat transfer medium flow rate control valve 39b can switch the circuit configuration of the heat transfer medium circuit by exhibiting a fully closed function. Accordingly, the cooling expansion valve 14b and the cooling expansion valve 14c also function as heat transfer medium circuit switching units.

[0366] Of course, the first heat transfer medium flow rate control valve 39a and the second heat transfer medium flow rate control valve 39b may be formed by combining a variable throttling mechanism that does not have a fully closing function with an on-off valve that opens and closes the throttling passage. In this case, the on-off valve becomes the heat transfer medium circuit switching unit.

[0367] One inlet side of the fifth heat transfer medium three-way joint 33e is connected to the outlet of the first heat transfer medium flow control valve 39a. The inlet side of the cooler core 38 is connected to the outlet of the fifth heat transfer medium three-way joint 33e.

[0368] The cooler core 38 is located inside the air conditioning case 51 of the indoor air conditioning unit 50, similar to the indoor evaporator 18 described in the first embodiment. The cooler core 38 is a heat transfer air heat exchange unit that exchanges heat between the heat transfer medium flowing out from at least one of the water refrigerant heat exchanger 121 and the chiller 19 and the air blown in from the blower 52.

[0369] In this embodiment, a tank-and-tube type heat exchanger is used as the cooler core 38. A solid layer of adsorbent 18a, similar to that in the first embodiment, is arranged in the heat exchange core portion of the cooler core 38. In other words, the cooler core 38 has an adsorption portion. The inlet side of the low-temperature side heat transfer medium three-way valve 32a is connected to the heat transfer medium outlet of the cooler core 38.

[0370] One outlet of the low-temperature side heat transfer medium three-way valve 32a is connected to the other inlet side of the first heat transfer medium three-way joint 33a. The other outlet of the low-temperature side heat transfer medium three-way valve 32a is connected to the inlet of the low-temperature side heat transfer medium passage 35d. One inlet of the sixth heat transfer medium three-way joint 33f is connected to the outlet of the low-temperature side heat transfer medium passage 35d.

[0371] Furthermore, in the high-temperature side heat transfer fluid circuit 30b of this embodiment, compared to the second embodiment, the inlet side of the high-temperature side heat transfer fluid three-way valve 32c is connected to the discharge port of the high-temperature side heat transfer fluid pump 31b. Also, one inlet of the heat transfer fluid four-way joint 33x is connected to the heat transfer fluid outlet of the heater core 36. In addition, another inlet of the heat transfer fluid four-way joint 33x is connected to the heat transfer fluid outlet of the high-temperature side radiator 34b.

[0372] The basic configuration of the heat transfer medium four-way joint 33x is the same as that of the refrigerant four-way joint 13x. One outlet of the heat transfer medium four-way joint 33x is connected to the inlet side of the heat transfer medium passage of the water refrigerant heat exchanger 121. Another outlet of the heat transfer medium four-way joint 33x is connected to the inlet of the high-temperature side heat transfer medium passage 35c. The outlet of the high-temperature side heat transfer medium passage 35c is connected to the other inlet of the fifth heat transfer medium three-way joint 33e.

[0373] The outlet of the heat transfer medium passage of the water refrigerant heat exchanger 121 is connected to the other inlet side of the sixth heat transfer medium three-way joint 33f. The outlet of the sixth heat transfer medium three-way joint 33f is connected to the suction side of the high-temperature side heat transfer medium pump 31b.

[0374] A second heat transfer fluid flow control valve 39b and a first heat transfer fluid check valve 37a are located in the high-temperature side heat transfer fluid passage 35c. The first heat transfer fluid check valve 37a allows the heat transfer fluid to flow from the heat transfer fluid four-way joint 33x side to the heat transfer fluid three-way joint 33e side, and prohibits the heat transfer fluid to flow from the heat transfer fluid three-way joint 33e side to the heat transfer fluid four-way joint 33x side.

[0375] A second heat transfer medium check valve 37b is positioned in the low-temperature side heat transfer medium passage 35d, which connects the other outlet of the low-temperature side heat transfer medium three-way valve 32a to the other inlet of the sixth heat transfer medium three-way joint 33f. The second heat transfer medium check valve 37b allows the heat transfer medium to flow from the low-temperature side heat transfer medium three-way valve 32a side to the sixth heat transfer medium three-way joint 33f side, and prevents the heat transfer medium from flowing from the sixth heat transfer medium three-way joint 33f side to the low-temperature side heat transfer medium three-way valve 32a side.

[0376] In this embodiment, the vehicle air conditioning system 1b does not have a temperature control function for in-vehicle equipment. Therefore, the cooling water passage 80a of the battery 80 is not connected to the low-temperature side heat transfer medium circuit 30a of this embodiment.

[0377] Next, the electrical control unit of the vehicle air conditioning system 1b will be described. In this embodiment, as shown in Figure 16, a high-temperature side heat transfer medium temperature sensor 73b and a cooler core temperature sensor 73c are added as control sensors connected to the control device 70.

[0378] The cooler core temperature sensor 73c is a cooler core temperature detection unit that detects the cooler core temperature Tcfin, which is the temperature of the cooler core 38. Specifically, the cooler core temperature sensor 73c detects the temperature of the heat exchange fins of the cooler core 38. Therefore, the same detection unit as the evaporator temperature sensor 72f can be used for the cooler core temperature sensor 73c.

[0379] Furthermore, the high-pressure side refrigerant temperature and pressure sensor 72b of this embodiment detects the temperature and pressure of the refrigerant flowing out of the water-refrigerant heat exchanger 121 and into the cooling expansion valve 14c. The other configurations are the same as those of the vehicle air conditioning system 1 of the first embodiment.

[0380] Next, the operation of the vehicle air conditioning system 1b of this embodiment will be described. The vehicle air conditioning system 1b can switch between various operating modes. Specifically, the vehicle air conditioning system 1b can switch between a cooling mode and a heating mode. Furthermore, in the control program of this embodiment, under the same conditions as in the first embodiment, the detachable heating mode, the internal air adsorption heating mode, and the low-temperature adsorption heating mode are selected as the heating mode. Each operating mode will be described below.

[0381] (a) Cooling mode In the cooling mode heat pump cycle 10b, the refrigerant discharged from the compressor 11 circulates in the following order: through the refrigerant passage of the water refrigerant heat exchanger 121, through the cooling expansion valve 14c, through the refrigerant passage of the chiller 19, through the accumulator 21, and finally back to the intake side of the compressor 11.

[0382] Furthermore, the control device 70 controls the refrigerant discharge capacity of the compressor 11 so that the chiller-side refrigerant temperature Tc approaches the target chiller temperature TCO. The target chiller temperature TCO is determined based on the target discharge temperature TAO by referring to a control map pre-stored in the control device 70. In the control map, the target chiller temperature TCO is increased as the target discharge temperature TAO increases.

[0383] Furthermore, the control device 70 controls the throttle opening of the cooling expansion valve 14c so that the degree of subcooling SC1 of the refrigerant flowing into the cooling expansion valve 14c approaches the target degree of subcooling SCO1 determined in the same manner as in the first embodiment.

[0384] In the cooling mode, on the low-temperature side heat transfer medium circuit 30a, the control device 70 operates the low-temperature side heat transfer medium pump 31a to achieve a predetermined standard pumping capacity. The control device 70 also sets the first heat transfer medium flow rate control valve 39a to a flow rate control state. Furthermore, the control device 70 controls the operation of the low-temperature side heat transfer medium three-way valve 32a so that the entire flow rate of heat transfer medium that has entered the circuit flows out towards the first heat transfer medium three-way joint 33a.

[0385] In the cooling mode, on the high-temperature side heat transfer medium circuit 30b, the control device 70 operates the high-temperature side heat transfer medium pump 31b to achieve a predetermined standard pumping capacity. The control device 70 also controls the operation of the high-temperature side heat transfer medium three-way valve 32c so that the high-temperature side heat transfer medium temperature TWH approaches a predetermined standard high-temperature side heat transfer medium temperature KTWH. In addition, the control device 70 closes the second heat transfer medium flow rate control valve 39b completely.

[0386] Therefore, in the cooling mode, the low-temperature side heat transfer medium circuit 30a and the high-temperature side heat transfer medium circuit 30b are switched to a heat transfer medium circuit in which the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a circulates in the following order: heat transfer medium passage of chiller 19, cooler core 38, and the inlet side of low-temperature side heat transfer medium pump 31a. At the same time, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a is switched to a heat transfer medium circuit in which the heat transfer medium circulates in the following order: heat transfer medium passage of chiller 19, low-temperature side radiator 34a, and the inlet side of low-temperature side heat transfer medium pump 31a.

[0387] Furthermore, the heat transfer medium pumped from the high-temperature side heat transfer medium pump 31b is switched to a heat transfer medium circuit that circulates in the following order: at least one of the heater core 36 and the high-temperature side radiator 34b, the heat transfer medium passage of the water refrigerant heat exchanger 121, and the suction port side of the high-temperature side heat transfer medium pump 31b.

[0388] Furthermore, the control device 70 adjusts the opening degree of the first heat transfer medium flow rate control valve 39a so that the cooler core temperature Tcfin becomes the target cooler core temperature TCO1. The target cooler core temperature TCO1 is determined by referring to a control map pre-stored in the control device 70 based on the target discharge temperature TAO. In the control map, the target cooler core temperature TCO1 is increased as the target discharge temperature TAO increases.

[0389] In the indoor air conditioning unit 50 in cooling mode, the control device 70 controls the operation of each controlled device, similar to the standalone cooling mode described in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices, similar to the standalone cooling mode described in the first embodiment.

[0390] Therefore, in the cooling mode heat pump cycle 10b, a vapor compression type refrigeration cycle is configured in which the water refrigerant heat exchanger 121 functions as a condenser and the chiller 19 functions as an evaporator.

[0391] In the water-refrigerant heat exchanger 121, the heat contained in the refrigerant is released into the heat transfer medium. This heats the heat transfer medium flowing through the water-refrigerant heat exchanger 121. In the chiller 19, the refrigerant absorbs heat from the heat transfer medium and evaporates. This cools the heat transfer medium flowing through the chiller 19.

[0392] In the cooling mode, on the low-temperature side heat transfer medium circuit 30a, the heat transfer medium flowing out from the first heat transfer medium three-way joint 33a is drawn into the low-temperature side heat transfer medium pump 31a. The heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a flows into the heat transfer medium passage of the chiller 19 and is cooled. The heat transfer medium flowing out from the heat transfer medium passage of the chiller 19 flows into the cooler core 38 and the low-temperature side radiator 34a according to the opening degree of the first heat transfer medium flow rate control valve 39a.

[0393] The heat transfer fluid that flows into the cooler core 38 exchanges heat with the blown air, thereby cooling the blown air. The heat transfer fluid that flows into the low-temperature side radiator 34a absorbs heat from the outside air. In cooling mode, the entire flow rate of the heat transfer fluid that flows into the low-temperature side heat transfer fluid three-way valve 32a flows out to the first heat transfer fluid three-way joint 33a.

[0394] The flow of heat transfer fluid discharged from the cooler core 38 and the flow of heat transfer fluid discharged from the low-temperature side radiator 34a merge at the first heat transfer fluid three-way joint 33a.

[0395] In the cooling mode, on the high-temperature side heat transfer medium circuit 30b, the heat transfer medium heated in the water refrigerant heat exchanger 121 is drawn into the high-temperature side heat transfer medium pump 31b. The heat transfer medium pumped from the high-temperature side heat transfer medium pump 31b flows into the heater core 36 and the high-temperature side radiator 34b according to the opening degree of the high-temperature side heat transfer medium three-way valve 32c.

[0396] The heat transfer fluid that flows into the heater core 36 releases heat into the blown air. This heats the blown air. The heat transfer fluid that flows into the high-temperature side radiator 34b releases heat into the outside air. The flow of heat transfer fluid that flows out from the heater core 36 and the flow of heat transfer fluid that flows out from the high-temperature side radiator 34b merge at the heat transfer fluid four-way joint 33x.

[0397] In cooling mode, the second heat transfer fluid flow control valve 39b is fully closed, so the heat transfer fluid that flows out from the heat transfer fluid four-way joint 33x flows into the heat transfer fluid passage of the water refrigerant heat exchanger 121 and is heated.

[0398] In the cooling mode of the indoor air conditioning unit 50, similar to the standalone cooling mode of the first embodiment, the temperature-adjusted air in the mixing space 56 is blown out to appropriate locations within the vehicle interior. This achieves cooling of the vehicle interior.

[0399] (c-1) Detachable heating mode In the detachable heating mode heat pump cycle 10b, as shown by the black arrows in Figure 17, the refrigerant discharged from the compressor 11 circulates in the following order, similar to the cooling mode: through the refrigerant passage of the water refrigerant heat exchanger 121, through the cooling expansion valve 14c, through the refrigerant passage of the chiller 19, through the accumulator 21, and finally to the intake side of the compressor 11.

[0400] Furthermore, the control device 70 controls the refrigerant discharge capacity of the compressor 11 so that the discharged refrigerant pressure Pd approaches the target high pressure PDO, similar to the detachable heating mode of the first embodiment. The control device 70 also controls the throttle opening of the cooling expansion valve 14c so that the degree of subcooling SC1 of the refrigerant flowing into the cooling expansion valve 14c approaches the target degree of subcooling SCO1.

[0401] In the detachable heating mode, on the low-temperature side heat transfer fluid circuit 30a side, the control device 70 controls the operation of the low-temperature side heat transfer fluid pump 31a, similar to the cooling mode. The control device 70 also closes the first heat transfer fluid flow rate adjustment valve 39a completely. Furthermore, the control device 70 controls the operation of the low-temperature side heat transfer fluid three-way valve 32a so that the entire flow rate of heat transfer fluid that has entered the circuit flows out to the sixth heat transfer fluid three-way joint 33f side.

[0402] In the detachable heating mode, on the high-temperature side heat transfer medium circuit 30b side, the control device 70 controls the operation of the high-temperature side heat transfer medium pump 31b and the high-temperature side heat transfer medium three-way valve 32c, similar to the cooling mode. In heating mode, the control device 70 controls the operation of the high-temperature side heat transfer medium three-way valve 32c so that the heat transfer medium flows into at least the heater core 36. The control device 70 also sets the second heat transfer medium flow rate adjustment valve 39b to the flow rate adjustment state.

[0403] Therefore, in the low-temperature side heat transfer medium circuit 30a and the high-temperature side heat transfer medium circuit 30b of the detachable heating mode, as shown by the dashed arrows in Figure 17, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a is switched to a heat transfer medium circuit that circulates in the following order: through the heat transfer medium passage of the chiller 19, the low-temperature side radiator 34a, and the suction port side of the low-temperature side heat transfer medium pump 31a.

[0404] Furthermore, the heat transfer medium pumped from the high-temperature side heat transfer medium pump 31b is switched to a heat transfer medium circuit that circulates in the order of at least the heater core 36, the heat transfer medium passage of the water-refrigerant heat exchanger 121, and the suction port side of the high-temperature side heat transfer medium pump 31b. At the same time, the heat transfer medium pumped from the high-temperature side heat transfer medium pump 31b is switched to a heat transfer medium circuit that circulates in the order of at least the heater core 36, the cooler core 38, and the suction port side of the high-temperature side heat transfer medium pump 31b. In other words, in the detachable heating mode, the heat transfer medium heated in the heat transfer medium passage of the water-refrigerant heat exchanger 121 is switched to a heat transfer medium circuit that flows into both the heater core 36 and the cooler core 38 in that order.

[0405] Furthermore, the control device 70 controls the opening degree of the second heat transfer medium flow rate control valve 39b so that the cooler core temperature Tcfin approaches the reference desorption temperature KTe1 (50°C in this embodiment).

[0406] In the indoor air conditioning unit 50 in detachable heating mode, the control device 70 controls the operation of each controlled device, similar to the detachable heating mode described in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices, similar to the detachable heating mode described in the first embodiment.

[0407] Therefore, in the detachable heating mode heat pump cycle 10b, a vapor compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 121 functions as a condenser and the chiller 19 functions as an evaporator.

[0408] In the water-refrigerant heat exchanger 121, the heat transfer medium flowing through the water-refrigerant heat exchanger 121 is heated, similar to the cooling mode. In the chiller 19, the heat transfer medium flowing through the chiller 19 is cooled, similar to the cooling mode.

[0409] In the detachable heating mode, on the low-temperature side heat transfer medium circuit 30a, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a flows into the heat transfer medium passage of the chiller 19 and is cooled. The heat transfer medium that flows out of the heat transfer medium passage of the chiller 19 flows into the low-temperature side radiator 34a and absorbs heat from the outside air. The heat transfer medium that flows out of the low-temperature side radiator 34a is drawn into the low-temperature side heat transfer medium pump 31a.

[0410] In the detachable heating mode, on the high-temperature side heat transfer medium circuit 30b, the heat transfer medium that flows into the heater core 36 releases heat into the blown air. This heats the blown air. In addition, the heat transfer medium that flows into the high-temperature side radiator 34b releases heat into the outside air.

[0411] Furthermore, in the desorption heating mode, the second heat transfer medium flow rate control valve 39b is in a flow rate control state. As a result, the heat transfer medium that flows out from the water refrigerant heat exchanger 121 flows into the cooler core 38 via at least the heater core 36 and the high-temperature side heat transfer medium passage 35c. This causes the temperature of the adsorbent 18a in the cooler core 38 to rise towards the reference desorption temperature KTe1, and the moisture adsorbed on the adsorbent 18a is desorbed.

[0412] The heat transfer fluid that flows out from the cooler core 38 is drawn into the high-temperature side heat transfer fluid pump 31b via the low-temperature side heat transfer fluid passage 35d. Other operations are the same as those of the detachable heating mode described in the first embodiment.

[0413] Therefore, in the detachable heating mode, the vehicle interior can be heated while the adsorbent 18a is being detached.

[0414] (c-2) Internal air adsorption heating mode In the heat pump cycle 10b of the internal air adsorption heating mode, as shown by the black arrows in Figure 18, the refrigerant discharged from the compressor 11 circulates in the following order, similar to the cooling mode: through the refrigerant passage of the water refrigerant heat exchanger 121, through the cooling expansion valve 14c, through the refrigerant passage of the chiller 19, through the accumulator 21, and finally to the intake side of the compressor 11.

[0415] Furthermore, the control device 70 controls the operation of the compressor 11 and the cooling expansion valve 14c, similar to the detachable heating mode.

[0416] In the internal air adsorption heating mode, on the low-temperature side heat transfer medium circuit 30a side, the control device 70 controls the operation of the low-temperature side heat transfer medium pump 31a, similar to the detachable heating mode. The control device 70 also closes the second heat transfer medium flow rate adjustment valve 39b completely.

[0417] In the internal air adsorption heating mode, on the high-temperature side heat transfer fluid circuit 30b side, the control device 70 controls the operation of the high-temperature side heat transfer fluid pump 31b and the high-temperature side heat transfer fluid three-way valve 32c, similar to the detachable heating mode. The control device 70 also closes the second heat transfer fluid flow rate control valve 39b completely.

[0418] Therefore, in the low-temperature side heat transfer medium circuit 30a and the high-temperature side heat transfer medium circuit 30b of the internal air adsorption heating mode, as shown by the dashed arrows in Figure 18, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a is switched to a heat transfer medium circuit in which it circulates in the following order: through the heat transfer medium passage of the chiller 19, through the low-temperature side radiator 34a, and through the intake side of the low-temperature side heat transfer medium pump 31a. In other words, in the internal air adsorption heating mode, the heat transfer medium is switched to a heat transfer medium circuit that flows the heat transfer medium cooled in the heat transfer medium passage of the chiller 19 into the low-temperature side radiator 34a.

[0419] Furthermore, the heat transfer medium pumped from the high-temperature side heat transfer medium pump 31b is switched to a heat transfer medium circuit that circulates in the order of at least the heater core 36, the heat transfer medium passage of the water-refrigerant heat exchanger 121, and the suction port side of the high-temperature side heat transfer medium pump 31b. In other words, in the internal air adsorption heating mode, the heat transfer medium is switched to a heat transfer medium circuit that flows the heat transfer medium heated in the heat transfer medium passage of the water-refrigerant heat exchanger 121 into the heater core 36.

[0420] In the indoor air conditioning unit 50 operating in the internal air adsorption heating mode, the control device 70 controls the operation of each controlled device, similar to the internal air adsorption heating mode described in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices, similar to the standalone internal air adsorption heating mode described in the first embodiment.

[0421] Therefore, in the internal air adsorption heating mode heat pump cycle 10b, a vapor compression type refrigeration cycle is configured in which the water refrigerant heat exchanger 121 functions as a condenser and the chiller 19 functions as an evaporator.

[0422] In the water-refrigerant heat exchanger 121, the heat transfer medium flowing through the water-refrigerant heat exchanger 121 is heated, similar to the detachable heating mode. In the chiller 19, the heat transfer medium flowing through the chiller 19 is cooled, similar to the detachable heating mode.

[0423] In the internal air adsorption heating mode, on the high-temperature side heat transfer medium circuit 30b, similar to the detachable heating mode, the heat transfer medium that flows into the heater core 36 releases heat into the blown air. This heats the blown air. Also, the heat transfer medium that flows into the high-temperature side radiator 34b releases heat into the outside air, similar to the detachable heating mode.

[0424] In the low-temperature side heat transfer medium circuit 30a of the internal air adsorption heating mode, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a is cooled by the chiller 19, similar to the detachable heating mode. The heat transfer medium cooled by the chiller 19 flows into the low-temperature side radiator 34a and absorbs heat from the outside air. Other operations are the same as those of the internal air adsorption heating mode described in the first embodiment.

[0425] Therefore, in the internal air adsorption heating mode, moisture contained in the internal air is adsorbed onto the adsorbent 18a, enabling dehumidification and heating of the vehicle interior.

[0426] (c-3) Low-temperature adsorption heating mode In the low-temperature adsorption heating mode heat pump cycle 10b, as shown by the black arrows in Figure 19, the refrigerant discharged from the compressor 11 circulates in the following order, similar to the cooling mode: through the refrigerant passage of the water refrigerant heat exchanger 121, through the cooling expansion valve 14c, through the refrigerant passage of the chiller 19, through the accumulator 21, and finally to the intake side of the compressor 11.

[0427] Furthermore, the control device 70 controls the operation of the compressor 11 and the cooling expansion valve 14c, similar to the detachable heating mode.

[0428] In the low-temperature adsorption heating mode, on the low-temperature side heat transfer medium circuit 30a side, the control device 70 controls the operation of the low-temperature side heat transfer medium pump 31a, similar to the detachable heating mode. The control device 70 also sets the first heat transfer medium flow rate adjustment valve 39a to the flow rate adjustment state.

[0429] In the low-temperature adsorption heating mode, on the high-temperature side heat transfer fluid circuit 30b side, the control device 70 controls the operation of the high-temperature side heat transfer fluid pump 31b and the high-temperature side heat transfer fluid three-way valve 32c, similar to the detachable heating mode. The control device 70 also sets the second heat transfer fluid flow rate control valve 39b to the flow rate control state.

[0430] Furthermore, the control device 70 controls the operation of the low-temperature heat transfer medium three-way valve 32a so that the heat transfer medium that has flowed into the interior flows out to both the first heat transfer medium three-way joint 33a side and the low-temperature heat transfer medium passage 35d side.

[0431] Therefore, in the low-temperature adsorption heating mode, the high-temperature side heat transfer medium circuit 30b and the low-temperature side heat transfer medium circuit 30a are switched to a heat transfer medium circuit in which the heat transfer medium pumped from the high-temperature side heat transfer medium pump 31b circulates in the order of at least the heater core 36, the heat transfer medium passage of the water refrigerant heat exchanger 121, and the suction port side of the high-temperature side heat transfer medium pump 31b. At the same time, similar to the detachable heating mode, the heat transfer medium pumped from the high-temperature side heat transfer medium pump 31b is switched to a heat transfer medium circuit in which the heat transfer medium circulates in the order of at least the heater core 36, the cooler core 38, and the suction port side of the high-temperature side heat transfer medium pump 31b.

[0432] Furthermore, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a is switched to a heat transfer medium circuit that circulates in the following order: through the heat transfer medium passage of the chiller 19, through the cooler core 38, and then to the suction side of the low-temperature side heat transfer medium pump 31a. Simultaneously, similar to the cooling mode, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a is switched to a heat transfer medium circuit that circulates in the following order: through the heat transfer medium passage of the chiller 19, through the low-temperature side radiator 34a, and then to the suction side of the low-temperature side heat transfer medium pump 31a. In other words, in the low-temperature adsorption heating mode, the heat transfer medium is heated in the heat transfer medium passage of the water refrigerant heat exchanger 121 and flows into the cooler core 38, while the heat transfer medium is cooled in the heat transfer medium passage of the chiller 19 and flows into the cooler core 38.

[0433] Furthermore, the control device 70 adjusts the opening ratio of the first heat medium flow control valve 39a and the second heat medium flow control valve 39b so that the cooler core temperature Tcfin approaches the internal temperature Tr. More specifically, the control device 70 increases the opening of the first heat medium flow control valve 39a and decreases the opening of the second heat medium flow control valve 39b as the value obtained by subtracting the internal temperature Tr from the cooler core temperature Tcfin increases.

[0434] Furthermore, the control device 70 controls the operation of the low-temperature side heat transfer medium three-way valve 32a according to the opening degree of the second heat transfer medium flow rate control valve 39b. More specifically, as the opening degree of the second heat transfer medium flow rate control valve 39b increases, the control device 70 decreases the flow rate of the heat transfer medium that flows out to the first heat transfer medium three-way joint 33a side and increases the flow rate of the heat transfer medium that flows out to the low-temperature side heat transfer medium passage 35d side.

[0435] In the indoor air conditioning unit 50 operating in low-temperature adsorption heating mode, the control device 70 controls the operation of each controlled device, similar to the low-temperature adsorption heating mode described in the first embodiment. Furthermore, the control device 70 controls the operation of other controlled devices, similar to the standalone low-temperature adsorption heating mode described in the first embodiment.

[0436] Therefore, in the low-temperature adsorption heating mode heat pump cycle 10b, a vapor compression type refrigeration cycle is configured in which the water refrigerant heat exchanger 121 functions as a condenser and the chiller 19 functions as an evaporator.

[0437] In the water-refrigerant heat exchanger 121, the heat transfer medium flowing through the water-refrigerant heat exchanger 121 is heated, similar to the detachable heating mode. In the chiller 19, the heat transfer medium flowing through the chiller 19 is cooled, similar to the detachable heating mode.

[0438] In the low-temperature adsorption heating mode, on the high-temperature side heat transfer medium circuit 30b, similar to the detachable heating mode, the heat transfer medium flowing into the heater core 36 releases heat into the blown air. This heats the blown air. Also, similar to the detachable heating mode, the heat transfer medium flowing into the high-temperature side radiator 34b releases heat into the outside air.

[0439] Furthermore, in the high-temperature side heat transfer medium circuit 30b of the low-temperature adsorption heating mode, the second heat transfer medium flow rate control valve 39b is in a flow rate control state. As a result, the heat transfer medium heated in the heat transfer medium passage of the water refrigerant heat exchanger 121 flows into one of the inlets of the fifth heat transfer medium three-way joint 33e via at least the heater core 36 and the high-temperature side heat transfer medium passage 35c, etc.

[0440] In the low-temperature adsorption heating mode, on the high-temperature side heat transfer medium circuit 30b, similar to the detachable heating mode, the heat transfer medium pumped from the low-temperature side heat transfer medium pump 31a is cooled by the chiller 19. The heat transfer medium cooled by the chiller 19 flows into the low-temperature side radiator 34a and absorbs heat from the outside air.

[0441] Furthermore, in the high-temperature side heat transfer fluid circuit 30b of the low-temperature adsorption heating mode, the first heat transfer fluid flow rate control valve 39a is in a flow rate control state. As a result, the heat transfer fluid cooled in the heat transfer fluid passage of the chiller 19 flows into the other inlet of the fifth heat transfer fluid three-way joint 33e.

[0442] In the fifth heat transfer fluid three-way joint 33e, the flow of heat transfer fluid from the water-refrigerant heat exchanger 121 side and the flow of refrigerant from the chiller 19 side merge, and the temperature of the heat transfer fluid approaches the internal temperature Tr. The merged heat transfer fluid, which has approached the internal temperature Tr, flows into the cooler core 38. The heat transfer fluid that flows into the cooler core 38 absorbs heat from the cooler core 38 and the adsorbent 18a.

[0443] As a result, the temperature of the deeper part of the adsorbent 18a (i.e., the part closer to the cooler core 38 than the outer surface) approaches the internal temperature Tr. The heat transfer fluid that flows out from the cooler core 38 flows out to both the first heat transfer fluid three-way joint 33a side and the low-temperature heat transfer fluid passage 35d side, depending on the opening degree of the low-temperature side heat transfer fluid three-way valve 32a. Other operations are the same as those of the low-temperature adsorption heating mode described in the first embodiment.

[0444] Therefore, in the low-temperature adsorption heating mode, the amount of adsorption by the adsorbent 18a can be increased compared to the internal air adsorption heating mode, enabling dehumidification and heating of the vehicle interior.

[0445] As described above, the vehicle air conditioning system 1b of this embodiment makes it possible to achieve comfortable air conditioning inside the vehicle by switching the operating mode. Furthermore, the heating mode of the vehicle air conditioning system 1b of this embodiment can obtain the same effects as in the first embodiment.

[0446] In other words, in the internal air adsorption heating mode and the low-temperature adsorption heating mode, internal air at a higher temperature than the outside air is introduced as the blown air, thus reducing the energy consumed to heat the blown air in the heating section. Furthermore, in the internal air adsorption heating mode, unnecessary energy is not consumed to introduce a low-temperature heat transfer medium into the cooler core 38.

[0447] Therefore, according to the vehicle air conditioning system 1b of this embodiment, the energy consumed when heating the vehicle interior while dehumidifying the blown air can be sufficiently reduced.

[0448] This disclosure is not limited to the embodiments described above, and can be modified in various ways without departing from the spirit of this disclosure, as follows.

[0449] In the embodiments described above, an example of applying the air conditioning system according to this disclosure to a vehicle was explained, but the application of the refrigeration cycle system according to this disclosure is not limited to vehicles. For example, it may be applied to a stationary air conditioning system with a temperature control function that adjusts the temperature of objects to be cooled (e.g., computers, server equipment, and other peripheral equipment) while providing air conditioning to the room.

[0450] Furthermore, in the first and second embodiments described above, the air conditioning system according to this disclosure was applied to an air conditioning system with an in-vehicle equipment temperature control function, and an example was described in which the temperature of the battery 80 was controlled as the in-vehicle equipment. However, the in-vehicle equipment is not limited to the battery 80. For example, it may be configured to control the temperature of an inverter, PCU, transaxle, ADAS control device, etc. Moreover, it may be configured to control the temperature of multiple in-vehicle equipment.

[0451] An inverter supplies power to motor generators and other components. A PCU is a power control unit that performs power transformation and distribution. A transaxle is a power transmission mechanism that integrates components such as the transmission and differential gear. An ADAS control unit is a control unit for advanced driver-assistance systems.

[0452] The configuration of the air conditioning system relating to this disclosure is not limited to the configuration disclosed in the embodiments described above.

[0453] In the above-described embodiment, an example in which an evaporation pressure regulating valve 20 is used was explained, but the invention is not limited thereto. Instead of the evaporation pressure regulating valve 20, a variable throttling mechanism configured with an electrical mechanism similar to that of the heating expansion valve 14a may be used. Furthermore, the fourth three-way joint 13d and the fifth three-way joint 13e described in the first embodiment may be integrated to form a four-way joint similar to the four-way joint 13x.

[0454] Furthermore, although the above-described embodiment described an example in which the first heat transfer medium flow rate control valve 39a is used as the heat transfer medium circuit switching unit, the invention is not limited to this. The first heat transfer medium flow rate control valve 39a may be abolished, and the second low-temperature side heat transfer medium three-way valve 32b may be installed in place of the second heat transfer medium three-way joint 33b or the fifth heat transfer medium three-way joint 33e.

[0455] Furthermore, the group of control sensors connected to the input side of the control device 70 is not limited to the detection unit disclosed in the above-described embodiment. Various detection units may be added or modified as needed. For example, in the above-described embodiment, an example was described in which a humidity sensor 76 was used as the window fogging detection unit, but the window fogging detection unit is not limited to this. A condensation sensor, an optical fogging sensor, or the like may be used as needed.

[0456] Similarly, in the above-described embodiment, an example was given in which a temperature detection unit for detecting the heat exchange fin temperature of the cooler core 38 was used as the cooler core temperature sensor 73c, but the invention is not limited to this. A temperature detection unit for detecting the cooler core side heat medium temperature TWC, which is the temperature of the heat medium flowing into the cooler core 38, may also be used as the cooler core temperature sensor 73c.

[0457] Furthermore, although the above-described embodiment described an example in which an adsorbent having isothermal adsorption characteristics equivalent to AQSOA(registered trademark) Z05 was used as the adsorbent 18a, the invention is not limited to this. For example, an adsorbent having isothermal adsorption characteristics equivalent to AQSOA(registered trademark) Z01 or Z02 may be used.

[0458] Furthermore, although the above embodiments described an example in which R1234yf was used as the refrigerant for the heat pump cycles 10, 10a, and 10b, the invention is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, R290, etc. may be used. Alternatively, a mixed refrigerant, which is a mixture of several of these refrigerants, may be used. Moreover, R744 may be used as the refrigerant to configure a supercritical refrigeration cycle in which the high-pressure side refrigerant pressure is equal to or greater than the critical pressure of the refrigerant.

[0459] Furthermore, although the above-described embodiment described an example in which PAG oil was used as the refrigeration oil, the invention is not limited to this. For example, POE (i.e., polyol ester) may also be used.

[0460] Furthermore, although the above-described embodiment described an example in which an aqueous ethylene glycol solution was used as the heat transfer medium for the low-temperature heat transfer medium circuit 30a and the high-temperature heat transfer medium circuit 30b, the invention is not limited to this. For example, a solution containing dimethylpolysiloxane or nanofluid, antifreeze, an aqueous liquid refrigerant containing alcohol, or a liquid medium containing oil may be used.

[0461] In the embodiments described above, vehicle air conditioning systems 1, 1a, and 1b capable of switching between multiple operating modes were described, but the switching of operating modes is not limited thereto.

[0462] If it is possible to switch between (c-1) detachable heating mode and (c-2) internal air adsorption heating mode as heating modes, the energy consumed when heating the air-conditioned space while dehumidifying the blown air can be reduced.

[0463] In addition, a parallel dehumidifying and heating mode may be implemented as another operating mode. For example, in the vehicle air conditioning units 1 and 1a, the refrigerant circuit and heat transfer fluid circuit can be configured in the same way as in the (c-3) low-temperature adsorption heating mode, and the parallel dehumidifying and heating mode can be implemented by lowering the refrigerant evaporation temperature in the indoor evaporator 18 to a level lower than the indoor temperature Tr.

[0464] Similarly, in the vehicle air conditioning system 1b, the heat transfer medium circuit is configured in the same way as the (c-3) low-temperature adsorption heating mode, and the parallel dehumidification heating mode can be executed by lowering the temperature of the heat transfer medium flowing into the cooler core 38 to the internal temperature Tr.

[0465] Furthermore, as an additional operating mode, a standalone cooling mode may be implemented to cool the in-vehicle equipment without providing air conditioning to the vehicle interior. For example, in the vehicle air conditioning system 1, the system switches to a refrigerant circuit in which the outdoor heat exchanger 16 of the heat pump cycle 10 functions as a condenser, and the chiller 19 functions as an evaporator without introducing refrigerant into the indoor evaporator 18. Then, the blower 52 is stopped.

[0466] Similarly, in the vehicle air conditioning system 1, the refrigerant circuit is switched to one in which the water-refrigerant heat exchanger 121 of the heat pump cycle 10 functions as a condenser, and the chiller 19 functions as an evaporator without introducing refrigerant into the indoor evaporator 18. Then, the blower 52 is stopped.

[0467] Furthermore, as an additional operating mode, a heating and cooling mode that provides heating to the vehicle interior and cooling to the in-vehicle equipment may also be available. For example, in the vehicle air conditioning system 1, the refrigerant flowing out from the heating unit is switched to a refrigerant circuit that circulates in the following order: heating expansion valve 14a, outdoor heat exchanger 16, cooling expansion valve 14c, chiller 19, and the intake side of the compressor 11. Then, the indoor condenser 12 is made to function as a condenser, and the outdoor heat exchanger 16 and chiller 19 are made to function as evaporators.

[0468] Furthermore, in the above-described embodiment, an example was explained in which the system switches to the low-temperature adsorption heating mode when the window fogging detection unit detects fogging of the window glass while the internal air adsorption heating mode is running. However, the system is not limited to this. For example, the system may switch to the low-temperature adsorption heating mode when it is determined that anti-fogging of the vehicle window glass is necessary after a predetermined reference time has elapsed since the start of the internal air adsorption heating mode.

[0469] The means disclosed in each of the above embodiments may be combined as appropriate to the extent that they are feasible. For example, the heating section of the first embodiment may be the same water-refrigerant heat exchanger 121 and high-temperature heat transfer medium circuit 30b as in the second embodiment.

[0470] The features of the air conditioning system disclosed herein are as follows: (Item 1) A compressor (11) that compresses and discharges the refrigerant, A heating unit (12, 121, 30b) that heats the air blown into the space to be air-conditioned using the refrigerant discharged from the compressor as a heat source, A refrigerant-air heat exchange unit (18) that exchanges heat between the refrigerant and the blown air before it is heated in the heating unit, A refrigerant-outside-air heat exchange unit (16, 19a) that exchanges heat between the refrigerant and the outside air outside the space to be air-conditioned, An outside air side pressure reduction section (14a, 14d) that reduces the pressure of the refrigerant flowing into the refrigerant outside air heat exchange section, A refrigerant circuit switching unit (15a~15e) that switches the refrigerant circuit through which the refrigerant circulates, It comprises at least an air blower (52) capable of drawing in indoor air from the space to be air-conditioned and blowing it towards the refrigerant air heat exchange unit as the blown air, The refrigerant air heat exchange unit has an adsorption unit (18a) that adsorbs moisture contained in the blown air, In the desorption heating mode, which heats the air-conditioned space and desorbs moisture adsorbed on the adsorption part, the refrigerant circuit switching unit switches to a circuit that circulates the refrigerant flowing out from the heating unit in the following order: the refrigerant-air heat exchange unit, the outside air side pressure reduction unit, the refrigerant-outside air heat exchange unit, and the compressor intake. In an indoor air adsorption heating mode in which the air-conditioned space is heated and moisture is adsorbed in the adsorption section, the refrigerant circuit switching section switches to a circuit in which the refrigerant flowing out from the heating section is circulated in the order of the outdoor air side pressure reduction section, the refrigerant outdoor air heat exchange section, and the compressor intake, while the blowing section blows the indoor air as the blown air toward the refrigerant air heat exchange section. (Item 2) The refrigerant air side pressure reduction section (14b) is provided to reduce the pressure of the refrigerant flowing into the refrigerant air heat exchange section, The air conditioning device according to item 1, which heats the space to be air-conditioned and, in a low-temperature adsorption heating mode that increases the amount of moisture adsorbed by the adsorption unit compared to the indoor air adsorption heating mode, the refrigerant circuit switching unit circulates the refrigerant flowing out from the heating unit in the order of the outdoor air side pressure reduction unit, the refrigerant outdoor air heat exchange unit, and the compressor inlet, and at the same time switches to a circuit that circulates the refrigerant flowing out from the heating unit in the order of the refrigerant air side pressure reduction unit, the refrigerant air heat exchange unit, and the compressor inlet, and the blower unit blows the indoor air as the blown air toward the refrigerant air heat exchange unit. (Item 3) The air conditioning device according to item 2, wherein in the low-temperature adsorption heating mode, the temperature of the refrigerant flowing into the refrigerant-air heat exchange unit is adjusted to approach the temperature of the indoor air (Tr), which is the temperature of the indoor air. (Item 4) A compressor (11) that compresses and discharges the refrigerant, A high-temperature side heat transfer fluid heat exchange section (121) that exchanges heat between the refrigerant discharged from the compressor and the heat transfer fluid, A refrigerant pressure reduction unit (14c) for reducing the pressure of the refrigerant that has flowed out from the high-temperature side heat transfer medium heat exchange unit, A low-temperature side heat transfer medium heat exchange unit (19) is provided for heat exchange between the refrigerant, which has been depressurized in the refrigerant depressurization unit, and the heat transfer medium. A high-temperature side air heat exchange unit (36) that exchanges heat between the heat medium that has flowed out from the high-temperature side heat medium heat exchange unit and the air supplied to the space to be air-conditioned, A heat medium and outside air heat exchange unit (34a) that exchanges heat between the heat medium that has flowed out from the low-temperature side heat medium heat exchange unit and the outside air outside the air-conditioned space, A heat transfer medium air heat exchange section (38) that exchanges heat between the heat transfer medium flowing out from at least one of the high-temperature side heat transfer medium heat exchange section and the low-temperature side heat transfer medium heat exchange section and the blown air before it is heated in the high-temperature side air heat exchange section, A heat transfer medium circuit switching unit (32a, 32b, 39a, 39b) that switches the heat transfer medium circuit in which the heat transfer medium circulates, It comprises at least an air blower (52) capable of drawing in indoor air from the space to be air-conditioned and blowing it toward the heat transfer medium air heat exchange unit, The heat transfer medium air heat exchange section has an adsorption section (18a) that adsorbs moisture contained in the blown air, In the desorption heating mode, which heats the air-conditioned space and desorbs moisture adsorbed on the adsorption part, the heat transfer medium circuit switching unit switches to a heat transfer medium circuit that allows the heat transfer medium that has flowed out of the high-temperature side heat transfer medium heat exchange unit to flow into the high-temperature side air heat exchange unit and the heat transfer medium air heat exchange unit. In an indoor air adsorption heating mode in which the air-conditioned space is heated and moisture is adsorbed in the adsorption section, the heat transfer medium circuit switching unit switches to a heat transfer medium circuit in which the heat transfer medium that has flowed out of the high-temperature side heat transfer medium heat exchange section flows into the high-temperature side air heat exchange section, and at the same time flows the heat transfer medium that has flowed out of the low-temperature side heat transfer medium heat exchange section into the heat transfer medium outside air heat exchange section, bypassing the heat transfer medium air heat exchange section, and the air blowing unit blows the indoor air toward the heat transfer medium air heat exchange section. (Item 5) The air conditioning device according to item 4, wherein the air conditioning device heats the space to be air-conditioned, and in a low-temperature adsorption heating mode in which the amount of moisture adsorbed by the adsorption unit is increased compared to the adsorption heating mode, the heat transfer medium circuit switching unit causes the heat transfer medium that has flowed out from the high-temperature side heat transfer medium heat exchange unit to flow into the high-temperature side air heat exchange unit, and at the same time causes the heat transfer medium that has flowed out from the low-temperature side heat transfer medium heat exchange unit to flow into the heat transfer medium air heat exchange unit, and the blowing unit blows the indoor air toward the heat transfer medium air heat exchange unit. (Item 6) The air conditioning device according to item 5, wherein in the low-temperature adsorption heating mode, the temperature of the heat medium flowing into the heat exchange unit is adjusted to approach the temperature of the indoor air (Tr), which is the temperature of the indoor air. (Item 7) An air conditioning system applied to a vehicle, The vehicle is equipped with a window fogging detection unit (76) for detecting fogging on the window glass, The air conditioning device according to any one of items 2, 3, 5, or 6, which switches to the low-temperature adsorption heating mode when the window fogging detection unit detects fogging of the window glass while the internal air adsorption heating mode is being executed. (Item 8) An air conditioning system according to any one of items 2, 3, 5, or 6, which switches to the low-temperature adsorption heating mode when the internal air adsorption heating mode is in operation and a predetermined reference time has elapsed. (Item 9) The air conditioning device described in any one of items 1 to 8, wherein the adsorption part employs one whose maximum relative pressure ratio Rmax satisfies the following formula 1. 0.05 ≤ Rmax ≤ 0.35 …(Equation 1) However, the maximum relative pressure ratio Rmax is the relative pressure ratio at which the increase in the amount of adsorption of the adsorption unit is maximized when the relative pressure ratio is increased by a predetermined amount. Furthermore, the relative pressure ratio is the ratio of the partial pressure of water vapor in the surrounding air to the saturated water vapor pressure at the temperature of the adsorption unit.

[0471] This disclosure is described in accordance with the embodiments, but it is understood that this disclosure is not limited to such embodiments or structures. This disclosure also includes various modifications and variations within the equivalence. In addition, various combinations and forms, as well as other combinations and forms that include only one, more, or fewer of those elements, fall within the scope and concept of this disclosure.

Claims

1. A compressor (11) that compresses and discharges the refrigerant, A heating unit (12, 121, 30b) that heats the air blown into the space to be air-conditioned using the refrigerant discharged from the compressor as a heat source, A refrigerant-air heat exchange unit (18) that exchanges heat between the refrigerant and the blown air before it is heated in the heating unit, A refrigerant-outside-air heat exchange unit (16, 19a) that exchanges heat between the refrigerant and the outside air outside the space to be air-conditioned, An outside air side pressure reduction section (14a, 14d) that reduces the pressure of the refrigerant flowing into the refrigerant outside air heat exchange section, A refrigerant circuit switching unit (15a to 15e) that switches the refrigerant circuit through which the refrigerant circulates, It comprises at least an air blower (52) capable of drawing in indoor air from the space to be air-conditioned and blowing it towards the refrigerant air heat exchange unit as the blown air, The refrigerant air heat exchange unit has an adsorption unit (18a) that adsorbs moisture contained in the blown air, In the desorption heating mode, which heats the air-conditioned space and desorbs moisture adsorbed on the adsorption part, the refrigerant circuit switching unit switches to a circuit that circulates the refrigerant flowing out from the heating unit in the following order: the refrigerant-air heat exchange unit, the outside air side pressure reduction unit, the refrigerant-outside air heat exchange unit, and the compressor intake. In an indoor air adsorption heating mode in which the air-conditioned space is heated and moisture is adsorbed in the adsorption section, the refrigerant circuit switching section switches to a circuit in which the refrigerant flowing out from the heating section is circulated in the order of the outdoor air side pressure reduction section, the refrigerant outdoor air heat exchange section, and the compressor intake, while the blowing section blows the indoor air as the blown air toward the refrigerant air heat exchange section.

2. The refrigerant air side pressure reduction section (14b) is provided to reduce the pressure of the refrigerant flowing into the refrigerant air heat exchange section, The air conditioning device according to claim 1, wherein the air conditioning device heats the space to be air-conditioned and, in a low-temperature adsorption heating mode in which the amount of moisture adsorbed by the adsorption unit is increased compared to the indoor air adsorption heating mode, the refrigerant circuit switching unit circulates the refrigerant flowing out from the heating unit in the order of the outdoor air side pressure reduction unit, the refrigerant outdoor air heat exchange unit, and the compressor inlet, and at the same time switches to a circuit in which the refrigerant flowing out from the heating unit circulates in the order of the refrigerant air side pressure reduction unit, the refrigerant air heat exchange unit, and the compressor inlet, and the blowing unit blows the indoor air as the blown air toward the refrigerant air heat exchange unit.

3. The air conditioning device according to claim 2, wherein in the low-temperature adsorption heating mode, the temperature of the refrigerant flowing into the refrigerant-air heat exchange unit is adjusted to approach the temperature of the indoor air (Tr).

4. A compressor (11) that compresses and discharges the refrigerant, A high-temperature side heat transfer fluid heat exchange section (121) that exchanges heat between the refrigerant discharged from the compressor and the heat transfer fluid, A refrigerant pressure reduction unit (14c) for reducing the pressure of the refrigerant that has flowed out from the high-temperature side heat transfer medium heat exchange unit, A low-temperature side heat transfer medium heat exchange unit (19) which exchanges heat between the refrigerant, which has been depressurized in the refrigerant depressurization unit, and the heat transfer medium, A high-temperature side air heat exchange unit (36) that exchanges heat between the heat medium that has flowed out from the high-temperature side heat medium heat exchange unit and the air supplied to the space to be air-conditioned, A heat medium and outside air heat exchange unit (34a) that exchanges heat between the heat medium that has flowed out from the low-temperature side heat medium heat exchange unit and the outside air outside the air-conditioned space, A heat transfer medium air heat exchange unit (38) which exchanges heat between the heat transfer medium that has flowed out from at least one of the high-temperature side heat transfer medium heat exchange unit and the low-temperature side heat transfer medium heat exchange unit and the blown air before it is heated in the high-temperature side air heat exchange unit, A heat transfer medium circuit switching unit (32a, 32b, 39a, 39b) that switches the heat transfer medium circuit in which the heat transfer medium circulates, It comprises at least an air blower (52) capable of drawing in indoor air from the space to be air-conditioned and blowing it toward the heat transfer medium air heat exchange unit, The heat transfer medium air heat exchange unit has an adsorption unit (18a) that adsorbs moisture contained in the blown air, In the desorption heating mode, which heats the air-conditioned space and desorbs moisture adsorbed on the adsorption part, the heat transfer medium circuit switching unit switches to a heat transfer medium circuit that allows the heat transfer medium that has flowed out of the high-temperature side heat transfer medium heat exchange unit to flow into the high-temperature side air heat exchange unit and the heat transfer medium air heat exchange unit. In an indoor air adsorption heating mode in which the air-conditioned space is heated and moisture is adsorbed in the adsorption section, the heat transfer medium circuit switching unit switches to a heat transfer medium circuit in which the heat transfer medium that has flowed out of the high-temperature side heat transfer medium heat exchange section flows into the high-temperature side air heat exchange section, and at the same time flows the heat transfer medium that has flowed out of the low-temperature side heat transfer medium heat exchange section into the heat transfer medium outside air heat exchange section, bypassing the heat transfer medium air heat exchange section, and the air blowing unit blows the indoor air toward the heat transfer medium air heat exchange section.

5. The air conditioning device according to claim 4, wherein in a low-temperature adsorption heating mode, which heats the space to be air-conditioned and increases the amount of moisture adsorbed by the adsorption unit compared to the indoor air adsorption heating mode, the heat transfer medium circuit switching unit causes the heat transfer medium that has flowed out from the high-temperature side heat transfer medium heat exchange unit to flow into the high-temperature side air heat exchange unit, and at the same time causes the heat transfer medium that has flowed out from the low-temperature side heat transfer medium heat exchange unit to flow into the heat transfer medium air heat exchange unit, and the blowing unit blows the indoor air toward the heat transfer medium air heat exchange unit.

6. The air conditioning device according to claim 5, wherein in the low-temperature adsorption heating mode, the temperature of the heat medium flowing into the heat exchange unit is adjusted to approach the temperature of the indoor air (Tr).

7. An air conditioning system applied to a vehicle, The vehicle is equipped with a window fogging detection unit (76) for detecting fogging on the window glass, The air conditioning device according to claim 2 or 5, which switches to the low-temperature adsorption heating mode when the window fogging detection unit detects fogging of the window glass while the internal air adsorption heating mode is being executed.

8. The air conditioning device according to claim 2 or 5, which switches to the low-temperature adsorption heating mode when the internal air adsorption heating mode is in operation and a predetermined reference time has elapsed.

9. The air conditioning device according to claim 1 or 4, wherein the adsorption part is one in which the maximum relative pressure ratio Rmax satisfies the following formula 1. 0.05 ≤ Rmax ≤ 0.35 ... (Equation 1) However, the maximum relative pressure ratio Rmax is the relative pressure ratio at which the increase in the amount of adsorption of the adsorption unit is maximized when the relative pressure ratio is increased by a predetermined amount. Furthermore, the relative pressure ratio is the ratio of the partial pressure of water vapor in the surrounding air to the saturated water vapor pressure at the temperature of the adsorption unit.

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