Refrigeration cycle device

Abstract

In a series dehumidification heating mode, the refrigeration cycle device is switched to a refrigerant circuit in which a refrigerant discharged from a compressor (11) circulates in the order of heating units (13, 40), an outdoor pressure reduction unit (14a), an outdoor heat exchange unit (15), an indoor pressure reduction unit (14b), an indoor evaporation unit (18), and a suction port of the compressor (11). Furthermore, in the hot-gas dehumidification heating mode, a refrigerant circuit in which the refrigerant discharged from the compressor (11) circulates in the order of an upstream-side branch part (12a), heating parts (13, 40), an indoor-side pressure reduction part (14b), an indoor evaporation part (18), merging parts (12g, 12h), and a suction port of the compressor (11) is switched. Circulation is performed in the order of the upstream-side branch section (12a), the heating sections (13, 40), the bypass-side pressure reduction section (14c), the merging sections (12g, 12h), and the suction port of the compressor (11), and circulation is performed in the order of the upstream-side branch section (12a), the bypass passage (21c), the merging sections (12g, 12h), and the suction port of the compressor (11).

Description

[0001] Cross-reference to related applications

[0002] This application is based on Japanese Patent Application No. 2022-142135 filed on September 7, 2022, and the contents thereof are incorporated herein by reference. Technical Field

[0003] The present disclosure relates to a refrigeration cycle device applied to an air-conditioning device. Background Art

[0004] Conventionally, Patent Document 1 discloses a refrigeration cycle device which is applied to a vehicle air conditioning device and is configured to be able to switch operation modes.

[0005] The refrigeration cycle device of Patent Document 1 includes a heat pump cycle for adjusting the temperature of the supply air blown into the vehicle interior as the air-conditioning target space. The heat pump cycle of Patent Document 1 is configured to be able to switch the refrigerant circuit according to the operation mode in order to continuously adjust the temperature of the supply air within a wide range. For example, when performing dehumidification and heating in the vehicle interior, the refrigerant circuit of the series dehumidification and heating mode and the refrigerant circuit of the parallel dehumidification and heating mode are switched.

[0006] More specifically, in the series dehumidification and heating mode, the refrigerant circuit is switched to one in which the outdoor heat exchanger is connected in series with the refrigerant flow upstream side of the indoor evaporator. The outdoor heat exchanger exchanges heat between the refrigerant and the outside air. The indoor evaporator exchanges heat between the refrigerant and the supply air. Then, in the series dehumidification and heating mode, while suppressing frost on the indoor evaporator, the heating capacity of the supply air in the heating unit is adjusted by adjusting the heat exchange amount between the refrigerant in the outdoor heat exchanger and the outside air.

[0007] In addition, in the parallel dehumidification and heating mode, the refrigerant circuit is switched to one in which the outdoor heat exchanger and the indoor evaporator are connected in parallel with respect to the refrigerant flow. In addition, while suppressing the frost formation of the indoor evaporator, the refrigerant evaporation temperature in the outdoor heat exchanger is made lower than the refrigerant evaporation temperature in the indoor evaporator. As a result, the amount of heat absorbed by the refrigerant from the outside air is increased, and the heating capacity of the supply air in the heating unit is improved compared with the series dehumidification and heating mode.

[0008] That is, in the vehicle air conditioning device of Patent Document 1, when performing dehumidification and heating in the vehicle interior, the refrigerant circuit of the series dehumidification and heating mode and the refrigerant circuit of the parallel dehumidification and heating mode are switched, and the temperature of the supply air can be continuously adjusted in a wide range.

[0009] Prior art literature

[0010] Patent Literature

[0011] Patent Document 1: Japanese Patent Application Publication No. 2012-225637

[0012] However, in the heat pump cycle of Patent Document 1, in the parallel dehumidification heating mode, an evaporation pressure regulating valve is arranged on the refrigerant flow downstream side of the indoor evaporator in order to make the refrigerant evaporation temperature in the outdoor heat exchanger lower than the refrigerant evaporation temperature in the indoor evaporator. The evaporation pressure regulating valve increases the pressure loss of the refrigerant circulating in the heat pump cycle, which causes the operation efficiency of the heat pump cycle to decrease. Summary of the invention

[0013] The present disclosure has been made in view of the above-mentioned points, and an object of the present disclosure is to provide a refrigeration cycle device capable of continuously adjusting the temperature of supply air within a wide range while suppressing a decrease in operating efficiency.

[0014] A refrigeration cycle device according to a first aspect of the present disclosure includes a compressor, an upstream branch portion, a heating portion, a heating portion side pressure reducing portion, an outdoor heat exchange portion, an indoor evaporating portion, a bypass passage, a bypass side flow rate regulating portion, a merging portion, and a refrigerant circuit switching portion.

[0015] The compressor compresses and discharges the refrigerant. The upstream branching section branches the flow of the refrigerant discharged from the compressor. The heating section uses the refrigerant flowing out of one outlet of the upstream branching section as a heat source to heat the supply air blown to the air-conditioned space. The heating section side pressure reducing section reduces the pressure of the refrigerant flowing out of the heating section. The outdoor heat exchange section exchanges heat between the refrigerant flowing out of the heating section side pressure reducing section and the outside air. The indoor evaporation section evaporates the refrigerant after the pressure reduction by the heating section side pressure reducing section, and cools the supply air before being heated by the heating section. The bypass passage guides the other refrigerant branched from the upstream branching section to the suction side of the compressor. The bypass side flow regulating section regulates the flow of the refrigerant flowing in the bypass passage. The confluence section causes the flow of the refrigerant flowing out of the heating section side pressure reducing section to merge with the flow of the refrigerant flowing out of the bypass side flow regulating section, and flows out to the suction side of the compressor. The refrigerant circuit switching section switches the refrigerant circuit.

[0016] The heating unit side pressure reducing unit includes an outdoor pressure reducing unit, an indoor pressure reducing unit, and a detour side pressure reducing unit. The outdoor pressure reducing unit depressurizes the refrigerant flowing into the outdoor heat exchange unit. The indoor pressure reducing unit depressurizes the refrigerant flowing into the indoor evaporation unit. The detour side pressure reducing unit depressurizes the refrigerant flowing around the outdoor heat exchange unit and the indoor evaporation unit.

[0017] As operation modes in which the supply air cooled by the indoor evaporation section is reheated by the heating section, there are a series dehumidification and heating mode and a hot gas dehumidification and heating mode.

[0018] In the series dehumidification and heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the indoor pressure reducing unit, the indoor evaporation unit, and the suction port of the compressor.

[0019] In addition, in the hot gas dehumidification heating mode, the refrigerant circuit switching unit is switched to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the indoor pressure reducing portion, the indoor evaporating portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

[0020] Thus, in the serial dehumidification and heating mode, by adjusting the throttling opening of at least one of the outdoor pressure reducing unit and the indoor pressure reducing unit, the heat exchange amount between the refrigerant in the outdoor heat exchange unit and the outside air can be adjusted while suppressing the frost on the indoor evaporation unit. Therefore, the heating capacity of the supply air in the heating unit can be continuously adjusted.

[0021] In the hot air dehumidification heating mode, the refrigerant with a relatively high enthalpy ratio is made to merge with the refrigerant with a relatively low enthalpy ratio flowing out of the decompression section on the detour side through the bypass passage. Thus, when the refrigerant discharge capacity of the compressor is increased, the heat dissipation of the refrigerant in the heating section can be increased without reducing the evaporation pressure of the refrigerant in the indoor evaporation section.

[0022] That is, in the hot gas dehumidification and heating mode, by increasing the refrigerant discharge capacity of the compressor, frost formation in the indoor evaporator can be suppressed, and the heating capacity of the supply air in the heating unit can be improved compared with the series dehumidification and heating mode.

[0023] Furthermore, in the hot air dehumidification heating mode, the increase in compression work when the refrigerant discharge capacity of the compressor is increased can be used as a heating source for the supply air. Therefore, when the heating capacity of the supply air in the heating unit is increased, the decrease in the operating efficiency can be suppressed.

[0024] As a result, according to the refrigeration cycle device of the first aspect of the present disclosure, by switching between the series dehumidification and heating mode and the hot gas dehumidification and heating mode, it is possible to continuously adjust the temperature of the supply air in a wide range while suppressing a decrease in operating efficiency.

[0025] In addition, a refrigeration cycle device according to a second aspect of the present disclosure includes a compressor, an upstream branch portion, a heating portion, a heating portion side pressure reducing portion, an outdoor heat exchange portion, a bypass passage, a bypass side flow rate adjusting portion, a merging portion, and a refrigerant circuit switching portion.

[0026] The compressor compresses and discharges the refrigerant. The upstream branching section branches the flow of the refrigerant discharged from the compressor. The heating section uses the refrigerant flowing out of one outlet of the upstream branching section as a heat source to heat the supply air blown to the air-conditioned space. The heating section side pressure reducing section reduces the pressure of the refrigerant flowing out of the heating section. The outdoor heat exchange section exchanges heat between the refrigerant flowing out of the heating section side pressure reducing section and the outside air. The bypass passage guides the other refrigerant discharged from the upstream branching section to the suction side of the compressor. The bypass side flow regulating section regulates the flow of the refrigerant flowing in the bypass passage. The confluence section causes the flow of the refrigerant flowing out of the heating section side pressure reducing section to merge with the flow of the refrigerant flowing out of the bypass side flow regulating section, and flows out to the suction side of the compressor. The refrigerant circuit switching section switches the refrigerant circuit.

[0027] The heating unit side pressure reducing unit includes an outdoor side pressure reducing unit and a bypass side pressure reducing unit. The outdoor side pressure reducing unit reduces the pressure of the refrigerant flowing into the outdoor heat exchange unit. The bypass side pressure reducing unit reduces the pressure of the refrigerant flowing around the outdoor heat exchange unit.

[0028] As operation modes for heating the supply air by the heating unit, there are an outdoor air heat absorption heating mode and a hot air heating mode.

[0029] In the outdoor heat absorption heating mode, the refrigerant circuit switching unit switches to a refrigerant circuit in which the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, and the suction port of the compressor.

[0030] In addition, in the hot air heating mode, the refrigerant circuit switching unit is switched to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream side branch portion, the heating portion, the detour side pressure reducing portion, the confluence portion, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream side branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

[0031] Thus, in the outdoor air heat absorption heating mode, the heating capacity of the supply air in the heating unit can be adjusted by adjusting at least one of the refrigerant discharge capacity of the compressor and the throttle opening degree of the outdoor pressure reducing unit.

[0032] In the hot air heating mode, the refrigerant with a relatively high enthalpy ratio merges with the refrigerant flowing out of the decompression section on the bypass side through the bypass passage. Thus, by increasing the refrigerant discharge capacity of the compressor, the cycle can be balanced even if the heating capacity of the supply air in the heating section is increased.

[0033] Furthermore, in the hot air heating mode, the increase in the compression workload when the refrigerant discharge capacity of the compressor is increased can be used as a heating source for the supply air. Therefore, when the heating capacity of the supply air in the heating unit is increased, a decrease in the operating efficiency can be suppressed.

[0034] As a result, according to the refrigeration cycle device of the second aspect of the present disclosure, by switching between the outdoor air heat absorption heating mode and the hot air heating mode, it is possible to suppress a decrease in operating efficiency and to continuously adjust the temperature of the supply air at a wide temperature range. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] The above-mentioned object and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the attached drawings.

[0036] Figure 1 It is a schematic overall configuration diagram of the vehicle air conditioning device according to the first embodiment.

[0037] Figure 2 This is a block diagram showing the electric control unit of the vehicle air conditioning system according to the first embodiment.

[0038] Figure 3 This is a flowchart showing a part of the control process of the control program of the first embodiment.

[0039] Figure 4 This is a flowchart showing another part of the control process of the control program of the first embodiment.

[0040] Figure 5 This is a flowchart showing another part of the control process of the control program of the first embodiment.

[0041] Figure 6 This is a flowchart showing another part of the control process of the control program of the first embodiment.

[0042] Figure 7 This is a flowchart showing another part of the control process of the control program of the first embodiment.

[0043] Figure 8 This is a control characteristic diagram for switching the operation mode in the control program of the first embodiment.

[0044] Fig. 9 This is another control characteristic diagram used for switching the operation mode in the control program of the first embodiment.

[0045] Fig.10 This is another control characteristic diagram used for switching the operation mode in the control program of the first embodiment.

[0046] Fig.11This is another control characteristic diagram used for switching the operation mode in the control program of the first embodiment.

[0047] Fig.12 This is another control characteristic diagram used for switching the operation mode in the control program of the first embodiment.

[0048] Fig.13 This is a flowchart showing the control process in the HG dehumidification and heating mode of the control routine of the first embodiment.

[0049] Fig.14 This is a schematic overall configuration diagram showing the flow of the refrigerant and the like in the HG dehumidification and heating mode and the cooling HG dehumidification and heating mode of the vehicle air conditioner according to the first embodiment.

[0050] Fig.15 This is a Mollier diagram showing changes in the state of the refrigerant in the HG dehumidification and heating mode of the heat pump cycle according to the first embodiment.

[0051] Fig.16 This is a flowchart showing the control process in the outdoor air heat absorption HG dehumidification and heating mode of the control program of the first embodiment.

[0052] Fig.17 This is a schematic overall configuration diagram showing the flow of the refrigerant and the like in the outside air heat absorption HG dehumidification and heating mode and the cooling outside air heat absorption HG dehumidification and heating mode of the vehicle air conditioner according to the first embodiment.

[0053] Fig.18 This is a Mollier diagram showing changes in the state of the refrigerant in the outdoor air heat absorption HG dehumidification and heating mode of the heat pump cycle according to the first embodiment.

[0054] Fig.19 This is a flowchart showing the control process in the HG heating mode of the control routine of the first embodiment.

[0055] Fig. 20 This is a schematic overall configuration diagram showing the flow of the refrigerant and the like in the HG heating mode and the cooling HG heating mode of the vehicle air conditioner according to the first embodiment.

[0056] Fig.21 This is a Mollier diagram showing changes in the state of the refrigerant in the HG heating mode of the heat pump cycle according to the first embodiment.

[0057] Fig. 22 This is a flowchart showing the control process in the cooling HG dehumidification and heating mode of the control program of the first embodiment.

[0058] Fig.23This is a Mollier diagram showing changes in the state of the refrigerant in the cooling HG dehumidification heating mode of the heat pump cycle according to the first embodiment.

[0059] Fig.24 This is a flowchart showing the control process in the cooling outside air heat absorption HG dehumidification and heating mode of the control program of the first embodiment.

[0060] Fig.25 This is a Mollier diagram showing changes in the state of the refrigerant in the cooling outside air absorbing heat HG dehumidification heating mode of the heat pump cycle of the first embodiment.

[0061] Fig.26 This is a flowchart showing the control process in the cooling HG heating mode of the control routine of the first embodiment.

[0062] Fig. 27 This is a Mollier diagram showing changes in the state of the refrigerant in the cooling HG heating mode of the heat pump cycle according to the first embodiment.

[0063] Fig.28 This is a flowchart showing the control process in the cooling outside air heat absorption HG heating mode of the control routine of the first embodiment.

[0064] Fig.29 This is a schematic overall configuration diagram showing the flow of the refrigerant and the like in the cooling outside air heat absorption HG heating mode of the vehicle air conditioner according to the first embodiment.

[0065] Fig.30 This is a Mollier diagram showing changes in the state of the refrigerant in the cooling HG heating mode of the heat pump cycle according to the first embodiment.

[0066] Fig.31 This is a control characteristic diagram showing the switching of the operation mode in the control program according to the second embodiment.

[0067] Fig.32 This is another control characteristic diagram used for switching the operation mode in the control program of the second embodiment.

[0068] Fig.33 It is a schematic overall configuration diagram of a vehicle air conditioning device according to a third embodiment.

[0069] Fig.34 It is a schematic overall configuration diagram showing the flow of the refrigerant and the like in the HG dehumidification and heating mode and the cooling HG dehumidification and heating mode of the vehicle air conditioner according to the third embodiment.

[0070] Fig.35This is a schematic overall configuration diagram showing the flow of refrigerant and the like in the outside air heat absorption HG dehumidification and heating mode and the cooling outside air heat absorption HG dehumidification and heating mode of the vehicle air conditioner according to the third embodiment.

[0071] Fig.36 It is a schematic overall configuration diagram showing the flow of the refrigerant and the like in the HG heating mode and the cooling HG heating mode of the vehicle air conditioner according to the third embodiment.

[0072] Fig.37 This is a schematic overall configuration diagram showing the flow of the refrigerant and the like in the cooling outside air heat absorption HG heating mode of the vehicle air conditioner according to the third embodiment. DETAILED DESCRIPTION

[0073] Hereinafter, a plurality of embodiments for implementing the present disclosure will be described with reference to the accompanying drawings. In each embodiment, the same reference symbols are marked on the parts corresponding to the matters described in the previous embodiment, and the repeated description is omitted. In the case of describing only a part of the structure in each embodiment, the other embodiments described can be applied to other parts of the structure. Not only can the parts that are explicitly indicated in each embodiment as being able to be specifically combined be combined with each other, but also the embodiments can be partially combined even if not explicitly indicated, as long as there is no particular obstacle to the combination.

[0074] (First Embodiment)

[0075] Hereinafter, the first embodiment of the refrigeration cycle device involved in the present disclosure will be described using the accompanying drawings. In this embodiment, the refrigeration cycle device involved in the present disclosure is applied to a vehicle air conditioning device 1 mounted on an electric vehicle. An electric vehicle is a vehicle that obtains driving force for traveling from an electric motor. The vehicle air conditioning device 1 of this embodiment performs air conditioning in a vehicle interior that is an air-conditioned space, and performs temperature regulation of vehicle-mounted equipment that is a cooling object. Therefore, the vehicle air conditioning device 1 is an air conditioning device with a vehicle-mounted equipment temperature regulation function.

[0076] In the vehicle air conditioning device 1, the temperature of the battery 70 is specifically regulated as a vehicle-mounted device. The battery 70 is a secondary battery that stores power supplied to a plurality of vehicle-mounted devices that operate by electricity. The battery 70 is a battery pack formed by electrically connecting a plurality of stacked battery cells 71 in series or in parallel. The battery cell 71 of this embodiment is a lithium-ion battery.

[0077] The battery 70 generates heat when in operation (i.e., during charging and discharging). The output of the battery 70 tends to decrease when the temperature is low, and the degradation tends to progress when the temperature is high. Therefore, it is necessary to maintain the temperature of the battery 70 within an appropriate temperature range (in this embodiment, 15° C. or higher and 55° C. or lower). Therefore, in the electric vehicle of this embodiment, the vehicle air conditioner 1 is used to adjust the temperature of the battery 70.

[0078] like Figure 1 As shown in the overall configuration diagram of FIG. 1 , the vehicle air conditioning device 1 includes a heat pump cycle 10 , an indoor air conditioning unit 30 , a high-temperature side heat medium circuit 40 , a low-temperature side heat medium circuit 50 , and the like.

[0079] The heat pump cycle 10 constitutes a vapor compression refrigeration cycle for adjusting the temperatures of the supply air blown into the vehicle interior, the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40, and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50. The heat pump cycle 10 is configured to be able to switch the refrigerant circuit according to various operation modes described later to perform air conditioning in the vehicle interior and temperature adjustment of vehicle-mounted equipment.

[0080] In the heat pump cycle 10, HFO refrigerant (specifically, R1234yf) is used as the refrigerant. In the heat pump cycle 10, a vapor compression subcritical refrigeration cycle is formed in which the pressure of the high-pressure refrigerant does not exceed the critical pressure of the refrigerant. The refrigeration oil for lubricating the compressor 11 is mixed with the refrigerant. The refrigeration oil of this embodiment is a PAG oil that is compatible with the liquid phase refrigerant. A part of the refrigeration oil circulates in the cycle together with the refrigerant.

[0081] The compressor 11 sucks, compresses, and discharges refrigerant in the heat pump cycle 10. The compressor 11 is an electric compressor that rotationally drives a fixed capacity type compression mechanism with a fixed discharge capacity by an electric motor. The refrigerant discharge capacity (i.e., rotation speed) of the compressor 11 is controlled by a control signal output from a control device 60 described later.

[0082] The compressor 11 is disposed in a drive device room formed on the front side of the vehicle cabin. The drive device room forms a space where at least a part of a device for generating and adjusting a driving force for driving the vehicle (eg, a driving motor) is disposed.

[0083] The discharge port of the compressor 11 is connected to the inlet side of the first three-way joint 12a. The first three-way joint 12a has three inlet and outlet ports that are connected to each other. As the first three-way joint 12a, a joint portion formed by joining a plurality of pipes or a joint portion formed by providing a plurality of refrigerant passages in a metal block or a resin block can be used.

[0084] As described later, the heat pump cycle 10 includes second to eighth three-way joints 12b to 12h. The basic structures of the second to eighth three-way joints 12b to 12h are the same as those of the first three-way joint 12a. In addition, the basic structures of the three-way joints described in the embodiments described later are also the same as those of the first three-way joint 12a.

[0085] These three-way joints branch the flow of the refrigerant when one of the three inflow and outflow ports is used as an inflow port and the remaining two are used as outflow ports. In addition, when two of the three inflow and outflow ports are used as inflow ports and the remaining one is used as an outflow port, the flow of the refrigerant is merged. The first three-way joint 12a is an upstream branching portion that branches the flow of the discharged refrigerant discharged from the compressor 11.

[0086] One outflow port of the first three-way joint 12a is connected to the inlet side of the refrigerant passage of the water-refrigerant heat exchanger 13. The other outflow port of the first three-way joint 12a is connected to one inflow port side of the seventh three-way joint 12g.

[0087] The refrigerant passage from the other outflow port of the first three-way joint 12a to one inflow port of the seventh three-way joint 12g is a bypass passage 21c. A bypass-side flow rate regulating valve 14d is disposed in the bypass passage 21c.

[0088] The bypass side flow control valve 14d is a bypass passage side pressure reducing unit that reduces the pressure of the discharged refrigerant flowing out of the other outflow port of the first three-way joint 12a (i.e., the other refrigerant branched from the first three-way joint 12a) in the hot gas dehumidification heating mode described later. In addition, the bypass side flow control valve 14d is a bypass side flow control unit that adjusts the flow rate (mass flow rate) of the refrigerant flowing through the bypass passage 21c.

[0089] The bypass flow control valve 14d is an electric variable throttling mechanism having a valve core that changes the throttling opening and an electric actuator that displaces the valve core. A stepping motor or a brushless motor can be used as the electric actuator. The operation of the bypass flow control valve 14d is controlled by a control signal output from the control device 60.

[0090] The bypass flow control valve 14d has a fully open function to function as a simple refrigerant passage without exerting a refrigerant decompression function and a flow control function by fully opening the throttle opening. The bypass flow control valve 14d has a fully closed function to close the refrigerant passage by fully closing the throttle opening.

[0091] As described later, the heat pump cycle 10 includes a heating expansion valve 14a, a cooling expansion valve 14b, and a cooling expansion valve 14c. The basic structures of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c are the same as those of the bypass flow control valve 14d.

[0092] The heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the bypass-side flow control valve 14d can switch the refrigerant circuit of the heat pump cycle 10 by performing the above-mentioned fully closed function. Therefore, the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the bypass-side flow control valve 14d also function as a refrigerant circuit switching unit.

[0093] Of course, a variable throttling mechanism without a full closing function and an on-off valve for opening and closing a throttling passage may be combined to form a heating expansion valve 14a, a cooling expansion valve 14b, a cooling expansion valve 14c and a bypass flow control valve 14d. In this case, each on-off valve becomes a refrigerant circuit switching unit.

[0094] The water refrigerant heat exchanger 13 is a high-temperature side heat exchange unit that performs heat exchange between the discharged refrigerant flowing out of one outflow port of the first three-way joint 12a (i.e., one refrigerant branched from the first three-way joint 12a) and the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40. The water refrigerant heat exchanger 13 is a refrigerant heat dissipation unit that dissipates heat of the discharged refrigerant to the high-temperature side heat medium, thereby heating the high-temperature side heat medium.

[0095] The outlet of the refrigerant passage of the water refrigerant heat exchanger 13 is connected to the inlet side of the second three-way joint 12b. One outlet of the second three-way joint 12b is connected to the refrigerant inlet side of the outdoor heat exchanger 15. The other outlet of the second three-way joint 12b is connected to one inlet side of the fourth three-way joint 12d.

[0096] The refrigerant passage from the other outflow port of the second three-way joint 12b to the one inflow port of the fourth three-way joint 12d is the high-pressure side passage 21a. A high-pressure side on-off valve 22a is disposed in the high-pressure side passage 21a.

[0097] The high-pressure side on-off valve 22a is an on-off valve that opens and closes the high-pressure side passage 21a. The high-pressure side on-off valve 22a is an electromagnetic valve whose opening and closing operation is controlled by a control voltage output from the control device 60. The high-pressure side on-off valve 22a can switch the refrigerant circuit by opening and closing the high-pressure side passage 21a. Therefore, the high-pressure side on-off valve 22a is a refrigerant circuit switching unit.

[0098] A heating expansion valve 14a is disposed in the refrigerant passage from one outlet of the second three-way joint 12b to the refrigerant inlet of the outdoor heat exchanger 15. The heating expansion valve 14a is an outdoor pressure reducing unit that reduces the pressure of the refrigerant flowing into the outdoor heat exchanger 15 in the outdoor air heat absorption heating mode described later. In addition, the heating expansion valve 14a is an outdoor flow rate regulating unit that regulates the flow rate (mass flow rate) of the refrigerant flowing into the outdoor heat exchanger 15.

[0099] The outdoor heat exchanger 15 is an outdoor heat exchange unit that exchanges heat between the refrigerant flowing out of the heating expansion valve 14a and the outside air blown by the outside air fan (not shown). The outdoor heat exchanger 15 is arranged on the front side of the drive device room. Therefore, when the vehicle is running, the running wind flowing into the drive device room through the grille can be blown to the outdoor heat exchanger 15.

[0100] The refrigerant outlet of the outdoor heat exchanger 15 is connected to the inlet side of the third three-way joint 12c. One outlet of the third three-way joint 12c is connected to the other inlet side of the fourth three-way joint 12d. The other outlet of the third three-way joint 12c is connected to one inlet side of the eighth three-way joint 12h.

[0101] The refrigerant passage from the other outlet of the third three-way joint 12c to one inlet of the eighth three-way joint 12h is a low-pressure passage 21b. A low-pressure on-off valve 22b and a first check valve 16a are disposed in the low-pressure passage 21b.

[0102] The low-pressure side on-off valve 22b is an on-off valve for opening and closing the low-pressure side passage 21b. The basic structure of the low-pressure side on-off valve 22b is the same as that of the high-pressure side on-off valve 22a. Therefore, the low-pressure side on-off valve 22b is a refrigerant circuit switching unit. The first check valve 16a allows the refrigerant to flow from the third three-way joint 12c side to the eighth three-way joint 12h side, and prohibits the refrigerant from flowing from the eighth three-way joint 12h side to the third three-way joint 12c side.

[0103] A second check valve 16b is disposed in the refrigerant passage from the outflow port on one side of the third three-way joint 12c to the inflow port on the other side of the fourth three-way joint 12d. The second check valve 16b allows the refrigerant to flow from the third three-way joint 12c side to the fourth three-way joint 12d side, and prohibits the refrigerant from flowing from the fourth three-way joint 12d side to the third three-way joint 12c side.

[0104] The outlet of the fourth three-way joint 12d is connected to the inlet side of the fifth three-way joint 12e. One outlet of the fifth three-way joint 12e is connected to the refrigerant inlet side of the indoor evaporator 18. The other outlet of the fifth three-way joint 12e is connected to the refrigerant inlet side of the refrigerator 20.

[0105] A cooling expansion valve 14b is disposed in the refrigerant passage from the outlet of one side of the fifth three-way joint 12e to the refrigerant inlet of the indoor evaporator 18. The cooling expansion valve 14b is an indoor pressure reducing unit that reduces the pressure of the refrigerant flowing out of the outlet of one side of the fifth three-way joint 12e in the case of the single cooling mode described later. In addition, the cooling expansion valve 14b is an indoor flow rate regulating unit that regulates the flow rate (mass flow rate) of the refrigerant flowing into the indoor evaporator 18.

[0106] The indoor evaporator 18 is arranged in an air conditioning casing 31 of an indoor air conditioning unit 30 described later. The indoor evaporator 18 is an air cooling heat exchanger that exchanges heat between the low-pressure refrigerant decompressed by the refrigeration expansion valve 14b and the supply air blown toward the vehicle interior from the indoor blower 32. The indoor evaporator 18 is an indoor evaporation unit that cools the supply air by evaporating the low-pressure refrigerant and absorbing heat.

[0107] The refrigerant outlet of the indoor evaporator 18 is connected to the inlet side of one side of the sixth three-way joint 12f. A third check valve 16c is arranged in the refrigerant passage from the refrigerant outlet of the indoor evaporator 18 to the inlet side of one side of the sixth three-way joint 12f. The third check valve 16c allows the refrigerant to flow from the indoor evaporator 18 side to the sixth three-way joint 12f side, and prohibits the refrigerant from flowing from the sixth three-way joint 12f side to the indoor evaporator 18 side.

[0108] In addition, a cooling expansion valve 14c is arranged in the refrigerant passage from the other outflow port of the fifth three-way joint 12e to the refrigerant inlet of the chiller 20. The cooling expansion valve 14c is a cooling-side pressure reducing unit that reduces the pressure of the refrigerant flowing out of the other outflow port of the fifth three-way joint 12e in the cooling mode described later. In addition, the cooling expansion valve 14c is a cooling-side flow rate regulating unit that regulates the flow rate (mass flow rate) of the refrigerant flowing into the chiller 20.

[0109] The cooling expansion valve 14c serves as a bypass pressure reducing unit that reduces the pressure of the refrigerant that flows around the outdoor heat exchanger 15 and the indoor evaporator 18 in a hot gas dehumidification heating mode described later.

[0110] The cold machine 20 is a low-temperature side heat exchange unit that exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 14c and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50. The cold machine 20 is a cooling evaporation unit that cools the low-temperature side heat medium by evaporating the low-pressure refrigerant to absorb heat.

[0111] The refrigerant outlet of the cold machine 20 is connected to the other inlet side of the sixth three-way joint 12f. The outlet of the sixth three-way joint 12f is connected to the other inlet side of the seventh three-way joint 12g. The outlet of the seventh three-way joint 12g is connected to the other inlet side of the eighth three-way joint 12h.

[0112] The outflow port of the eighth three-way joint 12h is connected to the inlet side of the accumulator 23. The accumulator 23 is a low-pressure gas-liquid separation unit that separates the gas-liquid phase of the refrigerant flowing into the inside and stores the separated liquid-phase refrigerant as the circulating surplus refrigerant. The gas-phase refrigerant outlet of the accumulator 23 is connected to the suction port side of the compressor 11.

[0113] As can be seen from the above description, the seventh three-way joint 12g and the eighth three-way joint 12h allow the flow of the refrigerant flowing out of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c to merge with the flow flowing out of the bypass-side flow control valve 14d, and form a confluence portion that allows the merged refrigerant to flow into the suction port side of the compressor 11.

[0114] Next, the high temperature side heat medium circuit 40 is described. The high temperature side heat medium circuit 40 is a heat medium circulation circuit that circulates the high temperature side heat medium. In this embodiment, ethylene glycol aqueous solution is used as the high temperature side heat medium. The high temperature side heat medium circuit 40 is configured with a heat medium passage of the water refrigerant heat exchanger 13, a high temperature side pump 41, a heater core 42, etc.

[0115] The high temperature side pump 41 is a high temperature side heat medium pressure feeding unit that pressure feeds the high temperature side heat medium to the inlet side of the heat medium passage of the water refrigerant heat exchanger 13. The high temperature side pump 41 is an electric water pump whose rotation speed (ie, pressure feeding capacity) is controlled by a control voltage outputted from the control device 60.

[0116] The outlet of the heat medium passage of the water refrigerant heat exchanger 13 is connected to the heat medium inlet side of the heater core 42. The heater core 42 is an air heating heat exchange unit that exchanges heat between the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 and the supply air that has passed through the indoor evaporator 18. The heater core 42 is a heat medium heat dissipation unit that dissipates the heat of the high-temperature side heat medium to the supply air to heat the supply air.

[0117] The heater core 42 is disposed in the air conditioning case 31 of the indoor air conditioning unit 30. The outlet of the heat medium passage of the heater core 42 is connected to the suction port side of the high temperature side pump 41.

[0118] Therefore, the components of the water refrigerant heat exchanger 13 and the high temperature side heat medium circuit 40 of the present embodiment are heating units that heat the supply air blown into the vehicle interior using the refrigerant flowing out of one outlet of the first three-way joint 12a as a heat source. Furthermore, the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c are all included in the heating unit side pressure reducing unit that reduces the pressure of the refrigerant flowing out of the water refrigerant heat exchanger 13 forming the heating unit.

[0119] Next, the low temperature side heat medium circuit 50 is described. The low temperature side heat medium circuit 50 is a heat medium circulation circuit that circulates the low temperature side heat medium. In this embodiment, as the low temperature side heat medium, the same type of fluid as the high temperature side heat medium is used. The low temperature side heat medium circuit 50 is configured with a heat medium passage of the cold machine 20, a low temperature side pump 51, a cooling water passage 70a of the battery 70, a heat medium three-way valve 53, a low temperature side radiator 54, etc.

[0120] The low temperature side pump 51 is a low temperature side heat medium pressure feeding unit that pressure feeds the low temperature side heat medium to the inlet side of the heat medium passage of the refrigerator 20. The basic structure of the low temperature side pump 51 is the same as that of the high temperature side pump 41.

[0121] The outlet of the heat medium passage of the chiller 20 is connected to the inlet side of the cooling water passage 70a of the battery 70. The cooling water passage 70a of the battery 70 cools the battery 70 by circulating the low-temperature side heat medium flowing out of the chiller 20. In other words, the cooling water passage 70a is a heat exchanger for battery cooling that cools the battery 70 by exchanging heat with the battery cells 71 through the low-temperature side heat medium flowing through the heat medium passage.

[0122] The cooling water passage 70a is formed inside a battery-specific housing that accommodates a plurality of stacked battery cells 71. The cooling water passage 70a has a passage structure in which a plurality of passages are connected in parallel inside the battery-specific housing. Thus, all battery cells 71 can be cooled evenly in the cooling water passage 70a.

[0123] The outlet of the cooling water passage 70a of the battery 70 is connected to the inlet side of the heat medium three-way valve 53. The heat medium three-way valve 53 has one inlet and two outlets, and is an electric three-way flow control valve that can continuously adjust the passage area ratio of the two outlets. The operation of the heat medium three-way valve 53 is controlled by a control signal output from the control device 60.

[0124] One outlet of the heat medium three-way valve 53 is connected to the heat medium inlet side of the low temperature side radiator 54. The other outlet of the heat medium three-way valve 53 is connected to one inlet side of the heat medium three-way joint 55. The basic structure of the heat medium three-way joint 55 is the same as that of the first three-way joint 12a for refrigerant.

[0125] The low temperature side radiator 54 is an outside air heat exchanger for heat medium that exchanges heat between the refrigerant flowing out of the cooling water passage 70a and the outside air blown by the outside air fan (not shown). The low temperature side radiator 54 is arranged on the front side of the drive device room. Therefore, when the vehicle is running, the running wind can be blown toward the low temperature side radiator 54. The low temperature side radiator 54 can also be formed integrally with the outdoor heat exchanger 15.

[0126] The heat medium outlet of the low temperature side radiator 54 is connected to the other inlet side of the heat medium three-way joint 55. The outlet of the heat medium three-way joint 55 is connected to the suction port side of the low temperature side pump 51.

[0127] Therefore, each component device of the chiller 20 and the low-temperature-side heat medium circuit 50 of the present embodiment is a cooling unit that cools the battery 70 as a cooling target object using the low-temperature-side heat medium flowing out of the heat medium passage of the chiller 20 .

[0128] In the cooling unit of this embodiment, the heat medium three-way valve 53 allows the low-temperature side heat medium flowing out of the cooling water passage 70a to flow into the heat medium passage of the cold machine 20. Thus, the heat absorbed from the battery 70 by the low-temperature side heat medium in the cooling water passage 70a can be absorbed by the cold machine 20 into the low-pressure refrigerant.

[0129] In the cooling unit of the present embodiment, the heat medium three-way valve 53 allows the low-temperature heat medium flowing out of the cooling water passage 70a to flow into the low-temperature radiator 54. Thus, the heat absorbed from the battery 70 by the low-temperature heat medium in the cooling water passage 70a can be dissipated to the outside air through the low-temperature radiator 54.

[0130] Next, the indoor air conditioning unit 30 is described. The indoor air conditioning unit 30 is a unit for air distribution that integrates a plurality of components in order to blow the supply air adjusted to an appropriate temperature for air conditioning the vehicle interior to an appropriate location in the vehicle interior. The indoor air conditioning unit 30 is arranged on the inner side of the instrument panel (instrument panel) at the frontmost part of the vehicle interior.

[0131] like Figure 1 As shown, the indoor air conditioning unit 30 is formed by accommodating an indoor blower 32, an indoor evaporator 18, a heater core 42, etc. in an air conditioning casing 31 forming an air passage for supplying air. The air conditioning casing 31 is formed by a resin (such as polypropylene) having a certain degree of elasticity and excellent strength.

[0132] An inside-outside air switching device 33 is disposed at the most upstream side of the air supply air flow of the air conditioning housing 31. The inside-outside air switching device 33 switches between introducing inside air (i.e., air inside the vehicle interior) and outside air (i.e., air outside the vehicle exterior) into the air conditioning housing 31. The operation of the inside-outside air switching device 33 is controlled by a control signal output from the control device 60.

[0133] The indoor blower 32 is arranged on the downstream side of the blown air flow of the indoor and outdoor air switching device 33. The indoor blower 32 is an indoor air supply unit that blows the air sucked in through the indoor and outdoor air switching device 33 toward the vehicle interior. The rotation speed (i.e., the air supply capacity) of the indoor blower 32 is controlled by the control voltage output from the control device 60.

[0134] The indoor evaporator 18 and the heater core 42 are arranged on the downstream side of the supply air flow of the indoor blower 32. The indoor evaporator 18 is arranged on the upstream side of the supply air flow compared with the heater core 42. A cold air bypass passage 35 is formed in the air conditioning casing 31 so that the supply air passing through the indoor evaporator 18 bypasses the heater core 42 and flows.

[0135] An air mix door 34 is disposed in the air conditioning case 31 on the downstream side of the indoor evaporator 18 in the blown air flow and on the upstream side of the heater core 42 and the cold air bypass passage 35 in the blown air flow.

[0136] The air mix door 34 is an air volume ratio adjustment unit that adjusts the air volume ratio of the air supply air passing through the heater core 42 side and the air supply air passing through the cold air bypass passage 35 in the air supply air after passing through the indoor evaporator 18. The operation of the actuator for driving the air mix door 34 is controlled by a control signal output from the control device 60.

[0137] A mixing space 36 is formed downstream of the heater core 42 and the cold air bypass passage 35 in the air conditioning case 31. The mixing space 36 is a space where the supply air heated by the heater core 42 and the supply air that has passed through the cold air bypass passage 35 and is not heated are mixed.

[0138] Therefore, in the interior air conditioning unit 30 , the air volume ratio is adjusted by the air mix door 34 , and the temperature of the supply air (ie, conditioned air) mixed in the mixing space 36 and blown into the vehicle interior is adjusted.

[0139] Further, an opening hole for blowing the supply air mixed in the mixing space and having its temperature adjusted into the vehicle interior is arranged at a downstream portion of the supply air flow of the air conditioning case 31 .

[0140] As opening holes, there are provided a face opening hole, a foot opening hole and a defrost opening hole (none of which is shown in the figure). The face opening hole is an opening hole for blowing air-conditioning air toward the upper body of the occupant in the vehicle. The foot opening hole is an opening hole for blowing air-conditioning air toward the feet of the occupant. The defrost opening hole is an opening hole for blowing air-conditioning air toward the inner side of the front window glass of the vehicle.

[0141] In addition, a face door, a foot door and a defroster door (none of which are shown in the figure) are respectively arranged on the upstream side of the air supply air flow of the face opening hole, the foot opening hole and the defroster opening hole. The face door adjusts the opening area of ​​the face opening hole. The foot door adjusts the opening area of ​​the foot opening hole. The defroster door adjusts the opening area of ​​the defroster opening hole.

[0142] The front door, the foot door and the defrost door are the blow-out mode switching parts for switching the blow-out mode. These doors are connected to the common electric actuator for driving the blow-out mode door via a connecting rod mechanism, etc., and are rotated in conjunction. The operation of the electric actuator for driving the blow-out mode door is controlled by a control signal output from the control device 60.

[0143] Therefore, in the interior air conditioning unit 30 , by switching the opening holes opened and closed by the outlet mode switching unit, the outlet mode is switched, and conditioned air adjusted to an appropriate temperature can be blown from the mixing space 36 to an appropriate location in the vehicle interior.

[0144] Next, the outline of the electric control unit of this embodiment is described. The control device 60 is composed of a well-known microcomputer including a CPU, a ROM, a RAM, etc. and its peripheral circuits. Then, various calculations and processes are performed according to the control program stored in the ROM to control the actions of various control target devices 11, 14a to 14d, 22a, 22b, 32, 41, 51, 53, etc. connected to the output side of the control device 60.

[0145] like Figure 2 As shown in the block diagram of FIG. 1 , a control sensor group is connected to the input side of the control device 60. Detection signals of the control sensor group are input to the control device 60. Each sensor will be described below.

[0146] The indoor air temperature sensor 61a is an indoor air temperature detection unit that detects the vehicle interior temperature (indoor air temperature) Tr. The outdoor air temperature sensor 61b is an outdoor air temperature detection unit that detects the vehicle exterior temperature (outdoor air temperature) Tam. The sunlight sensor 61c is a sunlight amount detection unit that detects the sunlight amount As irradiated into the vehicle interior.

[0147] The discharged refrigerant temperature and pressure sensor 62 a is a discharged refrigerant temperature and pressure detecting unit that detects a discharged refrigerant temperature Td and a discharged refrigerant pressure Pd of the discharged refrigerant discharged from the compressor 11 .

[0148] The high-pressure-side refrigerant temperature and pressure sensor 62 b is a high-pressure-side refrigerant temperature and pressure detection unit that detects the high-pressure-side refrigerant temperature T1 and the high-pressure-side refrigerant pressure P1 of the refrigerant flowing out of the water-refrigerant heat exchanger 13 .

[0149] The outdoor unit side refrigerant temperature and pressure sensor 62 c is an outdoor unit side refrigerant temperature and pressure detection unit that detects the outdoor unit side refrigerant temperature T2 and the outdoor unit side refrigerant pressure P2 of the refrigerant flowing out of the outdoor heat exchanger 15 .

[0150] The evaporator-side refrigerant temperature and pressure sensor 62 d is an evaporator-side refrigerant temperature and pressure detection unit that detects the evaporator-side refrigerant temperature Te and the evaporator-side refrigerant pressure Pe of the refrigerant flowing out of the indoor evaporator 18 .

[0151] The chiller-side refrigerant temperature and pressure sensor 62 e is a chiller-side refrigerant temperature and pressure detection unit that detects the chiller-side refrigerant temperature Tc and the chiller-side refrigerant pressure Pc of the refrigerant flowing out of the refrigerant passage of the chiller 20 .

[0152] In the present embodiment, a pressure detection unit and a temperature detection unit integrated as the refrigerant temperature and pressure sensor are used, but it is apparent that a pressure detection unit and a temperature detection unit constructed separately may be used.

[0153] The evaporator temperature sensor 62f 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 62f of the present embodiment detects the heat exchange fin temperature of the indoor evaporator 18.

[0154] The high temperature side heat medium temperature sensor 63 a is a high temperature side heat medium temperature detection unit that detects the temperature of the high temperature side heat medium flowing out of the heat medium passage of the water refrigerant heat exchanger 13 and flowing into the heater core 42 , that is, the high temperature side heat medium temperature TWH.

[0155] The first low-temperature side heat medium temperature sensor 64a is a first low-temperature side heat medium temperature detection unit that detects the temperature of the low-temperature side heat medium flowing into the cooling water passage 70a, that is, the first low-temperature side heat medium temperature TWL1. The second low-temperature side heat medium temperature sensor 64b is a second low-temperature side heat medium temperature detection unit that detects the temperature of the low-temperature side heat medium flowing out of the cooling water passage 70a, that is, the second low-temperature side heat medium temperature TWL2.

[0156] The battery temperature sensor 65 is a battery temperature detection unit that detects the temperature of the battery 70, that is, the battery temperature TB. The battery temperature sensor 65 has a plurality of temperature sensors and detects the temperatures of a plurality of locations of the battery 70. Therefore, the control device 60 can detect the temperature difference and temperature distribution of each battery cell forming the battery 70. In addition, as the battery temperature TB, the average value of the detection values ​​of the plurality of temperature sensors is used.

[0157] The conditioned air temperature sensor 66 detects the supply air temperature TAV which is the temperature of the supply air blown into the vehicle interior from the mixing space 36. The intake air temperature sensor 67 detects the intake air temperature Tin which is the temperature of the supply air flowing into the interior evaporator 18.

[0158] Moreover, if Figure 2 As shown in FIG. 1 , an operation panel 69 disposed near an instrument panel in the front portion of the vehicle interior is connected to the input side of the control device 60 . Operation signals from various operation switches provided on the operation panel 69 are input to the control device 60 .

[0159] Specific examples of the various operation switches provided on the operation panel 69 include an automatic switch, an air conditioning switch, an air volume setting switch, a temperature setting switch, and an outlet mode switch.

[0160] The automatic switch is an automatic control setting unit for setting or releasing the automatic control operation of the vehicle air conditioning device 1. The air conditioning switch is a cooling request unit for requesting cooling of the supply air by the indoor evaporator 18. The air volume setting switch is an air volume setting unit for manually setting the air volume of the indoor blower 32. The temperature setting switch is a temperature setting unit for setting the vehicle interior set temperature Tset. The outlet mode switch is an outlet mode setting unit for manually setting the outlet mode.

[0161] In addition, the control device 60 of this embodiment is a structure in which the control unit for controlling various control target devices connected to its output side is integrated. Therefore, the structure (hardware and software) for controlling the operation of each control target device constitutes the control unit for controlling the operation of each control target device.

[0162] For example, the control device 60 controls the rotation speed of the compressor 11 to form a discharge capacity control unit 60a. The control device 60 controls the operation of the refrigerant circuit switching unit such as the high-pressure on-off valve 22a and the low-pressure on-off valve 22b to form a refrigerant circuit switching control unit 60b.

[0163] Next, the operation of the present embodiment having the above configuration will be described. As described above, the vehicle air conditioner 1 of the present embodiment performs air conditioning in the vehicle cabin and also performs temperature control of the battery 70. Therefore, the vehicle air conditioner 1 can execute the following sixteen operation modes.

[0164] (1) Cooling Only Mode: The cooling only mode includes a cooling mode for cooling the vehicle interior by cooling the supply air and blowing it into the vehicle interior. The cooling only mode is an operation mode for cooling the vehicle interior without cooling the battery 70 .

[0165] (2) Series Dehumidification and Heating Mode: The series dehumidification and heating mode includes a dehumidification and heating mode in which the cooled and dehumidified supply air is reheated and blown into the vehicle interior to perform dehumidification and heating in the vehicle interior. The series dehumidification and heating mode is an operation mode in which the battery 70 is not cooled but dehumidification and heating in the vehicle interior is performed.

[0166] (3-1) Hot Gas Dehumidification and Heating Mode (hereinafter referred to as HG Dehumidification and Heating Mode): The HG Dehumidification and Heating Mode is included in the dehumidification and heating mode. The HG Dehumidification and Heating Mode is an operation mode in which the battery 70 is not cooled and dehumidification and heating is performed in the vehicle interior with a higher heating capacity than in the series dehumidification and heating mode.

[0167] (3-2) Outside air heat absorption hot gas dehumidification and heating mode (hereinafter referred to as outside air heat absorption HG dehumidification and heating mode): The outside air heat absorption HG dehumidification and heating mode is included in the dehumidification and heating mode. The outside air heat absorption HG dehumidification and heating mode is an operation mode in which the battery 70 is not cooled, but dehumidification and heating in the vehicle interior is performed with a higher heating capacity than the series dehumidification and heating mode and a higher operating efficiency than the HG dehumidification and heating mode.

[0168] (4-1) Outdoor Air Heating Mode: The outdoor air heating mode includes a heating mode for heating the vehicle interior by heating the supply air and blowing it into the vehicle interior. The outdoor air heating mode is an operation mode for heating the vehicle interior without cooling the battery 70 .

[0169] (4-2) Hot air heating mode (hereinafter referred to as HG heating mode): The HG heating mode is included in the heating mode. The HG heating mode is an operation mode in which the vehicle interior is heated with a higher heating capacity than the outdoor air absorption heating mode without cooling the battery 70 .

[0170] (5) Cooling and Refrigeration Mode: The cooling and refrigeration mode is included in the cooling and refrigeration mode. The cooling and refrigeration mode is an operation mode for cooling the battery 70 and also cooling the interior of the vehicle.

[0171] (6) Cooling series dehumidification and heating mode: The cooling series dehumidification and heating mode is included in the dehumidification and heating mode. The cooling series dehumidification and heating mode is an operation mode that cools the battery 70 and also performs dehumidification and heating in the vehicle interior.

[0172] (7-1) Cooling hot gas dehumidification and heating mode (hereinafter referred to as cooling HG dehumidification and heating mode): The cooling HG dehumidification and heating mode is included in the dehumidification and heating mode. The cooling HG dehumidification and heating mode is an operation mode that cools the battery 70 and also performs dehumidification and heating in the vehicle interior with a higher heating capacity than the cooling series dehumidification and heating mode.

[0173] (7-2) Cooling outside air heat absorption hot gas dehumidification and heating mode (hereinafter referred to as cooling outside air heat absorption HG dehumidification and heating mode): The cooling outside air heat absorption HG dehumidification and heating mode is included in the dehumidification and heating mode. The cooling outside air heat absorption HG dehumidification and heating mode is an operation mode that cools the battery 70 and also performs dehumidification and heating in the vehicle interior with a higher heating capacity than the cooling series dehumidification and heating mode and a higher operating efficiency than the cooling HG dehumidification and heating mode.

[0174] (8) Cooling device heat absorption heating mode: The cooling device heat absorption heating mode is included in the heating mode. The cooling device heat absorption heating mode is an operation mode in which the battery 70 is cooled and the vehicle interior is heated using waste heat absorbed by the refrigerant from the battery 70 .

[0175] (9) Cooling and heating mode: The cooling and heating mode is included in the heating mode. The cooling and heating mode is an operation mode for cooling the battery 70 and heating the vehicle interior by utilizing heat absorbed from the outside air by the refrigerant.

[0176] (10-1) Cooling hot air heating mode (hereinafter referred to as cooling HG heating mode): The cooling HG heating mode is included in the heating mode. The cooling HG heating mode is an operation mode that cools the battery 70 and heats the vehicle interior with a higher heating capacity than the cooling outside air endothermic heating mode.

[0177] (10-2) Cooling outside air heat absorption hot gas heating mode (hereinafter referred to as cooling outside air heat absorption HG heating mode): The cooling outside air heat absorption HG heating mode is included in the heating mode. The cooling outside air heat absorption HG heating mode is an operation mode that cools the battery 70 and also heats the vehicle interior with a higher heating capacity and a higher operating efficiency than the cooling outside air heat absorption heating mode.

[0178] (11) Cooling mode: This is an operation mode in which the air conditioning in the vehicle interior is not performed but the battery 70 is cooled.

[0179] (12) Air supply mode: This is an operation mode in which the air supply air is blown into the vehicle interior without cooling the battery 70 or adjusting the temperature of the air-conditioning air.

[0180] The switching of these operation modes is performed by executing a control program pre-stored in the control device 60. The control program is executed not only when the vehicle system is started by turning on the start switch (so-called ignition switch) of the vehicle system, but also when charging the battery 70 from an external power supply, etc. In the control program, when the automatic switch is turned on, the air conditioning in the vehicle interior is performed.

[0181] use Figure 3 etc., and explain the control procedure. Figure 3 Each control step described in the flowcharts of FIG. 1 and FIG. 2 is a unit for realizing various functions of the control device 60 .

[0182] First, in Figure 3 In step S10, the detection signal of the sensor group and the operation signal of the operation panel 69 are read. Then, in step S20, the target temperature of the supply air blown into the vehicle interior, that is, the target blowout temperature TAO, is determined based on the detection signal and the operation signal read in step S10. Therefore, step S20 is a target blowout temperature determination unit.

[0183] Specifically, the target outlet temperature TAO is calculated using the following mathematical formula F1.

[0184] TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×As+C…(F1)

[0185] Tset is the vehicle interior set temperature set by the temperature setting switch. Tr is the indoor air temperature detected by the indoor air temperature sensor 61a. Tam is the outdoor air temperature detected by the outdoor air temperature sensor 61b. As is the amount of sunlight detected by the sunlight sensor 61c. Kset, Kr, Kam, and Ks are control gains, and C is a constant for correction.

[0186] Next, in step S30, it is determined whether the air conditioner switch is on. As described above, the air conditioner switch is a cooling request unit that requests cooling of the blown air by the interior evaporator 18. Therefore, turning on the air conditioner switch means that the occupant requests cooling or dehumidification heating of the vehicle interior.

[0187] If it is determined in step S30 that the air conditioner switch is on, the process proceeds to step S40. If it is determined in step S30 that the air conditioner switch is not on, the process proceeds to step S200.

[0188] In step S40, it is determined whether the outside air temperature Tam is higher than a predetermined reference outside air temperature KA (0°C in this embodiment). The reference outside air temperature KA is set so that cooling of the supply air by the indoor evaporator 18 is effective for cooling or dehumidifying the air-conditioned space.

[0189] More specifically, in the present embodiment, in the operation mode in which the refrigerant is evaporated by the indoor evaporator 18, the evaporation temperature of the refrigerant in the indoor evaporator 18 is adjusted to be higher than the frost suppression temperature (1° C. in the present embodiment) which can suppress frost formation in the indoor evaporator 18. Therefore, in the indoor evaporator 18, the supply air cannot be cooled to a temperature lower than the frost suppression temperature.

[0190] That is, when the temperature of the supply air flowing into the indoor evaporator 18 is lower than the frost suppression temperature, it is ineffective to cool the supply air by the indoor evaporator 18. Therefore, the reference outdoor air temperature KA is set to a value lower than the frost suppression temperature, and when the outdoor air temperature Tam is lower than the reference outdoor air temperature KA, the supply air is not cooled by the indoor evaporator 18.

[0191] If it is determined in step S40 that the outside air temperature Tam is higher than the reference outside air temperature KA, the process proceeds to step S50. If it is determined in step S40 that the outside air temperature Tam is not higher than the reference outside air temperature KA, the process proceeds to step S200.

[0192] In step S50 , it is determined whether the target air temperature TAO is lower than the cooling reference temperature α1 . The cooling reference temperature α1 is a reference value for determining whether to cool the vehicle interior. The cooling reference temperature α1 is determined based on the outside air temperature Tam by referring to a control map pre-stored in the control device 60 .

[0193] In the control mapping of this embodiment, Figure 8 As shown in FIG. 1 , the cooling reference temperature α1 is determined so as to become a lower value as the outside air temperature Tam decreases. Figure 8 This is a control characteristic diagram for determining the operating mode when the air conditioner switch is turned on. The numbers in brackets in the diagram correspond to the above-mentioned operating modes. Fig. 9 , Fig.10 The same is true for the control characteristic diagram.

[0194] In step S50, when it is determined that the target air temperature TAO is lower than the cooling reference temperature α1, the process proceeds to step S60. In step S50, when it is determined that the target air temperature TAO is not lower than the cooling reference temperature α1, the process proceeds to step S90.

[0195] In step S60, it is determined whether it is necessary to cool the battery 70. Specifically, in the present embodiment, when the battery temperature TB detected by the battery temperature sensor 65 is higher than a predetermined reference cooling temperature KTB (35° C. in the present embodiment), it is determined that it is necessary to cool the battery 70. In addition, when the battery temperature TB is lower than the reference cooling temperature KTB, it is determined that it is not necessary to cool the battery 70.

[0196] Of course, when the battery temperature TB is in the process of rising, it may be determined that the battery 70 needs to be cooled when the battery temperature TB is higher than the reference cooling temperature KTB. Also, when the battery temperature TB is in the process of falling, it may be determined that the battery 70 does not need to be cooled when the battery temperature TB becomes lower than the low-temperature side reference cooling temperature KTBL.

[0197] If it is determined in step S60 that the battery 70 needs to be cooled, the process proceeds to step S70 and selects (5) the cooling mode as the operation mode. If it is determined in step S60 that the battery 70 does not need to be cooled, the process proceeds to step S80 and selects (1) the cooling mode alone as the operation mode.

[0198] In step S90, it is determined whether the target air outlet temperature TAO is lower than the dehumidification reference temperature β1. The dehumidification reference temperature β1 is a reference value for determining whether it is necessary to heat the supply air with a high heating capacity when performing dehumidification and heating in the vehicle interior.

[0199] The dehumidification reference temperature β1 is determined based on the outside air temperature Tam and with reference to a control map pre-stored in the control device 60. In the control map of the present embodiment, Figure 8 As shown, similarly to the cooling reference temperature α1, the dehumidification reference temperature β1 is determined to be lower as the outside air temperature Tam decreases. Furthermore, at the same outside air temperature Tam, the dehumidification reference temperature β1 is determined to be higher than the cooling reference temperature α1.

[0200] In step S90, when it is determined that the target air temperature TAO is lower than the dehumidification reference temperature β1, the process proceeds to step S100. In step S90, when it is determined that the target air temperature TAO is not lower than the dehumidification reference temperature β1, the process proceeds to step S130.

[0201] In step S100 , similarly to step S60 , it is determined whether cooling of battery 70 is necessary.

[0202] If it is determined in step S100 that the battery 70 needs to be cooled, the process proceeds to step S110, and (6) the cooling series dehumidification and heating mode is selected as the operation mode. If it is determined in step S100 that the battery 70 does not need to be cooled, the process proceeds to step S120, and (2) the series dehumidification and heating mode is selected as the operation mode.

[0203] In step S130, similarly to step S60, it is determined whether it is necessary to cool the battery 70. If it is determined in step S130 that it is necessary to cool the battery 70, the process proceeds to step S140. If it is determined in step S130 that it is not necessary to cool the battery 70, the process proceeds to step S170.

[0204] In step S140, if Figure 4 As shown, it is determined whether the refrigerant can properly absorb heat from the outdoor air by the outdoor heat exchanger 15. In step S140 of the present embodiment, it is determined whether outdoor air heat absorption is possible using the outdoor unit heat absorption possibility flag and the outlet temperature excess flag.

[0205] like Fig.11 As shown, the outdoor unit heat absorption permission flag is determined using the outdoor unit temperature difference ΔTO. The outdoor unit temperature difference ΔTO is a value obtained by subtracting the outdoor unit temperature Tout corresponding to the refrigerant temperature in the outdoor heat exchanger 15 from the outdoor air temperature Tam (Tam-Tout).

[0206] In step S140, the target evaporator temperature TEO is used as the outdoor unit temperature Tout. The target evaporator temperature TEO is a target value of the refrigerant evaporation temperature in the indoor evaporator 18. As in the dehumidification heating mode, in the refrigerant circuit in which the indoor evaporator 18 and the outdoor heat exchanger 15 are connected in parallel with respect to the refrigerant flow, the outdoor unit temperature Tout in the outdoor heat exchanger 15 is also close to the target evaporator temperature TEO.

[0207] And, if Fig.11 As shown, when the outdoor unit temperature difference ΔTO is in the process of increasing, when the outdoor unit temperature difference ΔTO is greater than the first reference temperature difference KΔTO1, the outdoor unit heat absorption possibility flag is set to "yes". When the outdoor unit heat absorption possibility flag is "yes", the refrigerant temperature in the outdoor heat exchanger 15 is sufficiently lower than the outdoor air temperature Tam, and the refrigerant can absorb heat from the outdoor air through the outdoor heat exchanger 15.

[0208] In addition, when the outdoor unit temperature difference ΔTO is in a decreasing process, when the outdoor unit temperature difference ΔTO is equal to or greater than the second reference temperature difference KΔTO2, the outdoor unit heat absorption permission flag is set to "not allowed". When the outdoor unit heat absorption permission flag is "not allowed", it means that the refrigerant temperature in the outdoor heat exchanger 15 is not sufficiently lower than the outdoor air temperature Tam, and the refrigerant cannot absorb heat from the outdoor air through the outdoor heat exchanger 15.

[0209] like Fig.12 As shown, the air outlet temperature excess flag is determined using the air outlet temperature difference ΔTAO. The air outlet temperature difference ΔTAO is a value obtained by subtracting the estimated air outlet temperature TAOA from the target air outlet temperature TAO (TAO-TAOA).

[0210] The estimated blown-out temperature TAOA is determined based on the outside air temperature Tam and the intake air temperature Tin detected by the intake air temperature sensor 67, and with reference to the control map stored in the control device 60. In the control map of the present embodiment, it is determined that the estimated blown-out temperature TAOA rises as the outside air temperature Tam rises. In addition, it is determined that the estimated blown-out temperature TAOA rises as the intake air temperature Tin rises.

[0211] And, if Fig.12 As shown, when the outlet temperature difference ΔTAO is in the increasing process, when the outlet temperature difference ΔTAO is greater than the first reference outlet temperature difference KΔTAO1, the outlet temperature excess flag is set to "normal". When the outlet temperature excess flag is "normal", the estimated outlet temperature TAOA is sufficiently lower than the target outlet temperature TAO, which means that the supply air can be heated by utilizing the heat absorbed by the refrigerant from the outside air.

[0212] In addition, when the outlet temperature difference ΔTAO is in a decreasing process, when the outlet temperature difference ΔTAO is less than the second reference outlet temperature difference KΔTAO2, the outlet temperature excess flag is set to "excess". When the outlet temperature excess flag is "excess", the estimated outlet temperature TAOA is close to the target outlet temperature TAO, which means that if the supply air is heated by the heat absorbed by the refrigerant from the outside air, the heating capacity of the supply air is excessive.

[0213] Therefore, in step S140 of the present embodiment, when the outdoor heat absorption flag is "yes" and the outlet temperature excess flag is "normal", it is determined that the refrigerant can appropriately absorb heat from the outdoor air through the outdoor heat exchanger 15. In other words, it is determined that the refrigerant can absorb heat from the outdoor air.

[0214] If it is determined in step S140 that the external air heat absorption is possible, Figure 4As shown, the process proceeds to step S150, and (7-2) cooling outside air heat absorption HG dehumidification and heating mode is selected as the operation mode. If it is determined in step S140 that outside air heat absorption is not possible, the process proceeds to step S160, and (7-1) cooling HG dehumidification and heating mode is selected as the operation mode.

[0215] In step S170, if Figure 5 As shown, it is determined whether or not the outdoor air heat absorption is possible in the same manner as in step S140. In step S170, the target evaporator temperature TEO is adopted as the outdoor unit temperature Tout.

[0216] If it is determined in step S170 that the outdoor air heat absorption is possible, the process proceeds to step S180, and (3-2) the outdoor air heat absorption HG dehumidification and heating mode is selected as the operation mode. If it is determined in step S170 that the outdoor air heat absorption is not possible, the process proceeds to step S190, and (3-1) the HG dehumidification and heating mode is selected as the operation mode.

[0217] Next, the case where the process of entering step S200 from step S30 or step S40 is described. In step S200, if Figure 6 As shown, it is determined whether the target air outlet temperature TAO is lower than the heating reference temperature γ. The heating reference temperature γ is a reference value for determining whether to heat the vehicle interior.

[0218] The heating reference temperature γ is determined based on the outside air temperature Tam and with reference to a control map pre-stored in the control device 60. In the control map of the present embodiment, Fig. 9 As shown in FIG. 1 , the heating reference temperature γ is determined to be a lower value as the outside air temperature Tam decreases. The heating reference temperature γ is set so that heating of the supply air by the heater core 42 forming the heating unit is effective for heating the air-conditioned space.

[0219] In step S200, if the target air blowing temperature TAO is determined to be lower than the heating reference temperature γ, it is not necessary to heat the supply air by the heater core 42, and the process proceeds to step S210. In step S200, if the target air blowing temperature TAO is determined to be not lower than the heating reference temperature γ, it is necessary to heat the supply air by the heater core 42, and the process proceeds to step S240.

[0220] In step S210 , similarly to step S60 , it is determined whether cooling of battery 70 is necessary.

[0221] If it is determined in step S210 that the battery 70 needs to be cooled, the process proceeds to step S220 and the (11) cooling mode is selected as the operation mode. If it is determined in step S210 that the battery 70 does not need to be cooled, the process proceeds to step S230 and the (12) air blowing mode is selected as the operation mode.

[0222] In step S240, it is determined whether the target air outlet temperature TAO is lower than the hot air reference temperature δ. The hot air reference temperature δ is a reference value for determining whether it is necessary to heat the supply air with a high heating capacity when heating the vehicle interior.

[0223] The hot gas reference temperature δ is determined based on the outside air temperature Tam and with reference to a control map pre-stored in the control device 60. In the control map of the present embodiment, Fig. 9 As shown in FIG. 1 , similarly to the heating reference temperature γ, the hot gas reference temperature δ is determined to be a lower value as the outside air temperature Tam decreases. Furthermore, the hot gas reference temperature δ is determined to be a higher value than the heating reference temperature γ.

[0224] If it is determined in step S240 that the target air blowing temperature TAO is lower than the hot air reference temperature δ, the process proceeds to step S250. If it is determined in step S240 that the target air blowing temperature TAO is not lower than the hot air reference temperature δ, the process proceeds to step S270.

[0225] In step S250 , similarly to step S60 , it is determined whether cooling of battery 70 is necessary.

[0226] If it is determined in step S250 that battery 70 needs to be cooled, the process proceeds to step S300. If it is determined in step S250 that battery 70 does not need to be cooled, the process proceeds to step S260, and (4-1) the outdoor air heat absorption heating mode is selected as the operation mode.

[0227] In step S270 , similarly to step S60 , it is determined whether cooling of battery 70 is necessary.

[0228] If it is determined in step S270 that battery 70 needs to be cooled, the process proceeds to step S300. If it is determined in step S270 that battery 70 does not need to be cooled, the process proceeds to step S280, and (4-2) the HG heating mode is selected as the operation mode.

[0229] Here, when it is determined in steps S250 and S270 that the battery 70 needs to be cooled and the process proceeds to step S300, it is necessary to heat the vehicle interior and cool the battery 70. Therefore, in the heat pump cycle 10, it is necessary to appropriately adjust the amount of heat dissipated by the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 13 and the amount of heat absorbed by the refrigerant from the low-temperature side heat medium in the refrigerator 20.

[0230] Therefore, in step S300, if Figure 7 As shown, it is determined whether the target air outlet temperature TAO is lower than the first cooling and heating reference temperature α2. The first cooling and heating reference temperature α2 is a reference value for determining whether it is necessary to heat the supply air with a high heating capacity when heating the vehicle interior.

[0231] The first cooling and heating reference temperature α2 is determined based on the outside air temperature Tam with reference to a control map pre-stored in the control device 60. In the control map of the present embodiment, Fig.10 As shown in FIG. 1 , the first cooling and heating reference temperature α2 is determined to be a lower value as the outside air temperature Tam decreases. Here, at the same outside air temperature Tam, the first cooling and heating reference temperature α2 is determined to be a higher value than the cooling reference temperature α1.

[0232] If it is determined in step S300 that the target air blowing temperature TAO is lower than the first cooling and heating reference temperature α2, the process proceeds to step S310, and (8) the cooling device heat absorption heating mode is selected as the operation mode. If it is determined in step S300 that the target air blowing temperature TAO is not lower than the first cooling and heating reference temperature α2, the process proceeds to step S320.

[0233] In step S320, it is determined whether the target air outlet temperature TAO is lower than the second cooling and heating reference temperature β2. The second cooling and heating reference temperature β2 is a reference value for determining whether it is necessary to heat the supply air with a higher heating capacity when heating the vehicle interior.

[0234] The second cooling and heating reference temperature β2 is determined based on the outside air temperature Tam and with reference to a control map pre-stored in the control device 60. In the control map of the present embodiment, Fig.10 As shown, similarly to the first cooling and heating reference temperature α2, the second cooling and heating reference temperature β2 is determined to be a lower value as the outside air temperature Tam decreases. Furthermore, at the same outside air temperature Tam, the second cooling and heating reference temperature β2 is determined to be a higher value than the dehumidification reference temperature β1.

[0235] If it is determined in step S320 that the target air blowing temperature TAO is lower than the second cooling and heating reference temperature β2, the process proceeds to step S330, and (9) the cooling outside air heat absorption heating mode is selected as the operation mode. If it is determined in step S320 that the target air blowing temperature TAO is not lower than the second cooling and heating reference temperature β2, the process proceeds to step S340.

[0236] In step S340, it is determined whether outdoor air heat absorption is possible. In step S340, the saturation temperature of the refrigerant at the target low pressure PSO is used as the outdoor unit temperature Tout. The target low pressure PSO is a target value for the temperature of the refrigerant sucked into the compressor 11. In the refrigerant circuit in the heating mode, the outdoor unit temperature Tout in the outdoor heat exchanger 15 is also close to the saturation temperature of the refrigerant at the target low pressure PSO. The rest is determined in the same manner as in step S140.

[0237] If it is determined in step S340 that the external air heat absorption is possible, the process proceeds to step S350, and the (10-2) cooling external air heat absorption HG heating mode is selected as the operation mode. If it is determined in step S340 that the external air heat absorption is not possible, the process proceeds to step S360, and the (10-1) cooling HG heating mode is selected as the operation mode.

[0238] In the control program of this embodiment, the operation mode is switched as described above. Furthermore, before the predetermined end condition of the control program is met, the control program such as reading the detection signal and the operation signal, calculating the target air outlet temperature TAO, selecting the operation mode, and controlling various control target devices corresponding to the operation mode is repeatedly performed according to each predetermined control cycle. The detailed actions of each operation mode are described below.

[0239] (1) Single cooling mode

[0240] In the cooling-only mode, the control device 60 executes a control flow for the cooling-only mode. In the control flow for the cooling-only mode, the control device 60 determines a target evaporator temperature TEO. The target evaporator temperature TEO is a target value of the refrigerant evaporation temperature in the indoor evaporator 18. Therefore, the control flow for the cooling-only mode includes a target evaporator temperature determination unit that determines the target evaporator temperature TEO.

[0241] In the target evaporator temperature determination unit, the target evaporator temperature TEO is determined based on the target air outlet temperature TAO and with reference to the control map pre-stored in the control device 60. In the control map of the single cooling mode, it is determined that the target evaporator temperature TEO increases as the target air outlet temperature TAO increases. In addition, the target evaporator temperature TEO is determined to be a temperature (in this embodiment, 1°C or more) at which frost does not form on the indoor evaporator 18.

[0242] Furthermore, the control device 60 determines the increase or decrease amount ΔIVO of the rotation speed of the compressor 11. The increase or decrease amount ΔIVO in the cooling alone mode is determined by a feedback control method so that the evaporator temperature Tefin approaches the target evaporator temperature TEO based on the deviation between the target evaporator temperature TEO and the evaporator temperature Tefin detected by the evaporator temperature sensor 62f.

[0243] In addition, the control device 60 determines a target degree of subcooling SCO2 of the refrigerant flowing out of the outdoor heat exchanger 15. The target degree of subcooling SCO2 is determined based on the outdoor air temperature Tam and with reference to a control map pre-stored in the control device 60. In the control map of the cooling mode alone, the target degree of subcooling SCO2 is determined so that the coefficient of performance (COP) of the cycle approaches a maximum value.

[0244] Furthermore, the control device 60 determines the increase or decrease amount ΔEVC of the throttling opening of the refrigeration expansion valve 14b. The increase or decrease amount ΔEVC in the single cooling mode is determined based on the deviation between the target supercooling degree SCO2 and the supercooling degree SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 15, etc., and is determined by a feedback control method so that the supercooling degree SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 15 is close to the target supercooling degree SCO2.

[0245] The degree of subcooling SC2 of the refrigerant on the outlet side of the outdoor heat exchanger 15 is calculated using the outdoor-side refrigerant temperature T2 and the outdoor-side refrigerant pressure P2 detected by the outdoor-side refrigerant temperature and pressure sensor 62c.

[0246] In addition, the control device 60 calculates the opening degree SW of the air mix door 34. Specifically, the opening degree SW is calculated by the following mathematical formula F2.

[0247] SW={TAO+(Te+C2)} / {TWH+(Te+C2)}×100(%)…(F2)

[0248] Te is the evaporator-side refrigerant temperature detected by the evaporator-side refrigerant temperature and pressure sensor 62d. TWH is the high-temperature-side heat medium temperature detected by the high-temperature-side heat medium temperature sensor 63a. C2 is a constant for control.

[0249] Furthermore, the control device 60 determines a control signal to be output to an actuator for driving the air mix door 34 based on the opening degree SW.

[0250] For example, when the opening SW=100%, the control signal is determined so that the air mix door 34 is moved to the so-called maximum heating position where the air passage on the heater core 42 side is fully opened and the cold air bypass passage 35 is fully closed. When the opening SW=0%, the control signal is determined so that the air mix door 34 is moved to the so-called maximum cooling position where the air passage on the heater core 42 side is fully closed and the cold air bypass passage 35 is fully opened.

[0251] In addition, the control device 60 determines the control signals to be outputted respectively so that the heating expansion valve 14a is in a fully open state, the cooling expansion valve 14b is in a throttling state to exert the refrigerant decompression effect, the cooling expansion valve 14c is in a fully closed state, and the bypass side flow control valve 14d is in a fully closed state. In addition, the control device 60 determines the control voltages to be outputted respectively so that the high-pressure side on-off valve 22a and the low-pressure side on-off valve 22b are closed.

[0252] Furthermore, the control device 60 appropriately determines the operating states of other controlled devices. For example, the control device 60 determines the control voltage output to the high temperature side pump 41 to stop the low temperature side pump 51 so as to achieve a predetermined reference pressure delivery capacity.

[0253] For example, the control device 60 determines the control voltage to be output to the indoor air blower 32 based on the target air blow temperature TAO and with reference to the control map pre-stored in the control device 60. In the control map of the present embodiment, the control voltage is determined in such a manner that the air supply volume of the indoor air blower 32 is maximized in the extremely low temperature region (maximum cooling region) and the extremely high temperature region (maximum heating region) of the target air blow temperature TAO, and the air supply volume is reduced as it approaches the intermediate temperature region.

[0254] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0255] Therefore, in the heat pump cycle 10 in the single cooling mode, the refrigerant circuit is switched as follows: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the fully opened heating expansion valve 14a, the outdoor heat exchanger 15, the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11.

[0256] Therefore, in the heat pump cycle 10 in the cooling-only mode, a vapor compression refrigeration cycle is constructed in which the water-refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers for condensing the refrigerant by dissipating heat, and the indoor evaporator 18 functions as an evaporator for evaporating the refrigerant.

[0257] The high temperature side heat medium is heated by the refrigerant transferring heat to the high temperature side heat medium in the water refrigerant heat exchanger 13. The supply air is cooled by the refrigerant absorbing heat from the supply air in the indoor evaporator 18.

[0258] In addition, in the high-temperature side heat medium circuit 40 in the cooling mode alone, the high-temperature side heat medium pumped from the high-temperature side pump 41 circulates in the order of the heat medium passage of the water-refrigerant heat exchanger 13, the heater core 42, and the suction port of the high-temperature side pump 41. Thus, the high-temperature side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42.

[0259] In addition, in the indoor air conditioning unit 30 in the cooling mode alone, the supply air blown from the indoor blower 32 is cooled by the indoor evaporator 18. The supply air cooled by the indoor evaporator 18 is heated by the heater core 42 according to the opening degree of the air mixing door 34. Then, the conditioned air, which has been temperature-regulated so as to be close to the target outlet temperature TAO, is blown into the vehicle interior. Thus, cooling of the vehicle interior is achieved.

[0260] (2) Series dehumidification and heating mode

[0261] In the series dehumidification and heating mode, the control device 60 executes the control flow for the series dehumidification and heating mode. In the control flow for the series dehumidification and heating mode, the control device 60 determines the target evaporator temperature TEO in the same manner as in the single cooling mode. Therefore, the control flow for the series dehumidification and heating mode has a target evaporator temperature determination unit. Moreover, the control device 60 determines the increase or decrease amount ΔIVO of the rotation speed of the compressor 11 in the same manner as in the single cooling mode.

[0262] The control device 60 determines the target high temperature side heat medium temperature TWHO so that the supply air can be sufficiently heated by the heater core 42. The target high temperature side heat medium temperature TWHO is a target value of the high temperature side heat medium temperature TWH detected by the high temperature side heat medium temperature sensor 63a.

[0263] The target high temperature side heat medium temperature TWHO is determined based on the target outlet temperature TAO and the efficiency of the heater core 42, with reference to a control map pre-stored in the control device 60. In the control map of the series dehumidification and heating mode, the target high temperature side heat medium temperature TWHO is determined to increase as the target outlet temperature TAO increases.

[0264] Furthermore, the control device 60 determines the change amount ΔKPN1 of the opening pattern KPN1 based on the target outlet temperature TAO and the target high temperature side heat medium temperature TWHO with reference to a control map pre-stored in the control device 60 .

[0265] The opening pattern KPN1 is a parameter for determining a combination of the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14b. The opening pattern KPN1 corresponds to the opening ratio of the throttle opening of the cooling expansion valve 14b to the throttle opening of the heating expansion valve 14a.

[0266] In the control map of the series dehumidification and heating mode, the opening pattern KPN1 is increased as the target air temperature TAO increases. That is, as the target air temperature TAO increases, the opening ratio of the throttling opening of the cooling expansion valve 14b to the throttling opening of the heating expansion valve 14a increases.

[0267] In addition, the control device 60 calculates the opening degree SW of the air mix door 34 in the same manner as in the cooling only mode.

[0268] In addition, the control device 60 determines the control signals to be outputted respectively so as to throttle the heating expansion valve 14a, throttle the cooling expansion valve 14b, fully close the cooling expansion valve 14c, and fully close the bypass flow control valve 14d. In addition, the control device 60 determines the control voltages to be outputted respectively so as to close the high-pressure side opening and closing valve 22a and close the low-pressure side opening and closing valve 22b.

[0269] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling only mode.

[0270] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0271] Therefore, in the heat pump cycle 10 in the series dehumidification and heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11.

[0272] Therefore, in the heat pump cycle 10 in the series dehumidification and heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 13 functions as a condenser and the indoor evaporator 18 functions as an evaporator.

[0273] Furthermore, in the heat pump cycle 10 in the series dehumidification heating mode, when the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is higher than the outside air temperature Tam, the outdoor heat exchanger 15 is made to function as a condenser. In addition, when the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is lower than the outside air temperature Tam, the outdoor heat exchanger 15 is made to function as an evaporator.

[0274] The high temperature side heat medium is heated by the refrigerant transferring heat to the high temperature side heat medium in the water refrigerant heat exchanger 13. Also, the supply air is cooled by the refrigerant absorbing heat from the supply air in the indoor evaporator 18.

[0275] In addition, in the high-temperature side heat medium circuit 40 in the series dehumidification and heating mode, similarly to the single cooling mode, the high-temperature side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0276] In addition, in the indoor air conditioning unit 30 in the series dehumidification and heating mode, the supply air blown from the indoor blower 32 is cooled and dehumidified by the indoor evaporator 18. The supply air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 according to the opening of the air mixing door 34. Then, the air-conditioned air with a temperature adjusted in a manner close to the target blowing temperature TAO is blown into the vehicle interior. In this way, dehumidification and heating in the vehicle interior are achieved.

[0277] (3-1) HG dehumidification and heating mode

[0278] In the HG dehumidification and heating mode, the control device 60 executes Fig.13 The control flow for HG dehumidification heating mode is shown.

[0279] First, in step S1901, the target high temperature side heat medium temperature TWHO of the high temperature side heat medium is determined. The target high temperature side heat medium temperature TWHO is determined based on the vehicle interior setting temperature Tset set by the temperature setting switch and with reference to the control map. In the control map of the HG dehumidification heating mode, in the vehicle interior setting temperature Tset within a predetermined range, it is determined that the target high temperature side heat medium temperature TWHO increases as the outside air temperature Tam decreases.

[0280] In step S1902, the increase or decrease amount ΔIVO of the rotation speed of the compressor 11 is determined. The increase or decrease amount ΔIVO in the HG dehumidification heating mode is determined by a feedback control method based on the deviation between the target high-temperature side heat medium temperature TWHO and the high-temperature side heat medium temperature TWH, so that the high-temperature side heat medium temperature TWH approaches the target high-temperature side heat medium temperature TWHO.

[0281] In step S1903, a target degree of superheat SHEO of the refrigerant at the outlet of the indoor evaporator 18 is determined. As the target degree of superheat SHEO, a preset constant (5° C. in the present embodiment) can be adopted.

[0282] In step S1904, the increase or decrease amount ΔEVC of the throttling opening of the cooling expansion valve 14b is determined. The increase or decrease amount ΔEVC in the HG dehumidification heating mode is determined by the feedback control method based on the deviation between the target superheat SHEO and the superheat SHE of the refrigerant on the outlet side of the indoor evaporator 18, so that the superheat SHE of the refrigerant on the outlet side of the indoor evaporator 18 is close to the target superheat SHEO.

[0283] The degree of superheat SHE of the refrigerant on the outlet side of the indoor evaporator 18 is calculated using the evaporator-side refrigerant temperature Te and the evaporator-side refrigerant pressure Pe detected by the evaporator-side refrigerant temperature and pressure sensor 62d.

[0284] In step S1905, a target degree of subcooling SCO1 of the refrigerant flowing out of the water-refrigerant heat exchanger 13 is determined. The target degree of subcooling SCO1 is determined based on the outside air temperature Tam with reference to a control map pre-stored in the control device 60. The target degree of subcooling SCO1 may be a constant value.

[0285] In step S1906, the increase or decrease amount ΔEVB of the throttling opening of the cooling expansion valve 14c is determined. The increase or decrease amount ΔEVB in the HG dehumidification heating mode is based on the deviation between the target supercooling degree SCO1 and the supercooling degree SC1 of the refrigerant flowing out of the water-refrigerant heat exchanger 13, etc., and is determined by a feedback control method so that the supercooling degree SC1 of the refrigerant flowing out of the water-refrigerant heat exchanger 13 is close to the target supercooling degree SCO1.

[0286] The degree of subcooling SC1 of the refrigerant flowing out of the water-refrigerant heat exchanger 13 is calculated using the high-pressure-side refrigerant temperature T1 and the high-pressure-side refrigerant pressure P1 detected by the high-pressure-side refrigerant temperature-pressure sensor 62 b .

[0287] In step S1907, the target low pressure PSO is determined as the target value of the sucked refrigerant sucked into the compressor 11. In the HG dehumidification and heating mode, the target low pressure PSO is determined so that the evaporation temperature of the refrigerant in the indoor evaporator 18 becomes a temperature that can dehumidify the supply air without causing frost on the indoor evaporator 18. Therefore, the saturation temperature of the refrigerant at the target low pressure PSO corresponds to the target evaporator temperature TEO. Therefore, in the HG dehumidification and heating mode, step S1907 is a target evaporator temperature determination unit.

[0288] In step S1908, the increase or decrease amount ΔEVHG of the opening of the bypass side flow control valve 14d is determined. The increase or decrease amount ΔEVHG in the HG dehumidification heating mode is determined by the feedback control method so that the chiller side refrigerant pressure Pc approaches the target low pressure PSO based on the deviation between the target low pressure PSO and the chiller side refrigerant pressure Pc detected by the chiller side refrigerant temperature and pressure sensor 62e.

[0289] In step S1909 , the opening degree SW of the air mix door 34 is calculated in the same manner as in the cooling only mode.

[0290] In step S1910, the control signals to be outputted are determined so that the heating expansion valve 14a is fully closed, the cooling expansion valve 14b is throttled, the cooling expansion valve 14c is throttled, and the bypass flow control valve 14d is throttled. In addition, the control voltages to be outputted are determined so that the high-pressure side on-off valve 22a is opened and the low-pressure side on-off valve 22b is closed.

[0291] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling only mode.

[0292] In step S1911, a control signal or a control voltage is output to each control target device to obtain the control state of each control target device determined as described above. Figure 3 and Fig.13 As shown in step Z, the control flow returns to step S10.

[0293] Therefore, in the heat pump cycle 10 in the HG dehumidification heating mode, Fig.14 As shown by the solid arrows, the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the high-pressure side passage 21a, the fifth three-way joint 12e, the cooling expansion valve 14b, the indoor evaporator 18, the sixth three-way joint 12f, the seventh three-way joint 12g, the accumulator 23, and the suction port of the compressor 11. Moreover, the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the high-pressure side passage 21a, the fifth three-way joint 12e, the cooling expansion valve 14c, the chiller 20, the sixth three-way joint 12f, the seventh three-way joint 12g, the accumulator 23, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched as follows: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the bypass side flow regulating valve 14d arranged in the bypass passage 21c, the seventh three-way joint 12g, the liquid storage tank 23, and the suction port of the compressor 11.

[0294] Therefore, in the heat pump cycle 10 in the HG dehumidification heating mode, the state of the refrigerant is as follows: Fig.15 The changes are as shown in the Mollier Line Chart.

[0295] The discharged refrigerant ( Fig.15 The refrigerant branched from the first three-way joint 12a flows into the water-refrigerant heat exchanger 13, and radiates heat to the high-temperature side heat medium (from Fig.15 As a result, the high temperature side heat medium is heated.

[0296] The refrigerant flowing out of the water-refrigerant heat exchanger 13 flows into the high-pressure side passage 21a. The flow of the refrigerant flowing out of the high-pressure side passage 21a is branched by the fifth three-way joint 12e. The refrigerant branched from the fifth three-way joint 12e flows into the refrigeration expansion valve 14b and is decompressed (from Fig.15 from point b15 to point e15).

[0297] The refrigerant decompressed by the cooling expansion valve 14b flows into the indoor evaporator 18. The refrigerant flowing into the indoor evaporator 18 absorbs heat from the blown air by the indoor blower 32 and evaporates (from Fig.15 The refrigerant flowing out of the indoor evaporator 18 flows into one inlet of the sixth three-way joint 12f via the third check valve 16c.

[0298] The other refrigerant branched from the fifth three-way joint 12e flows into the cooling expansion valve 14c and is decompressed (from Fig.15 The refrigerant after decompression by the cooling expansion valve 14c flows into the chiller 20. In the HG dehumidification and heating mode, since the low temperature side pump 51 is stopped, the refrigerant and the low temperature side heat medium do not exchange heat in the chiller 20. The refrigerant flowing out of the chiller 20 flows into the other inlet of the sixth three-way joint 12f.

[0299] In the sixth three-way joint 12f, the refrigerant flowing out of the indoor evaporator 18 merges and mixes with the refrigerant flowing out of the refrigerator 20. The refrigerant flowing out of the sixth three-way joint 12f flows into the other inlet of the seventh three-way joint 12g.

[0300] The other refrigerant branched from the first three-way joint 12a flows into the bypass passage 21c. The refrigerant flowing into the bypass passage 21c is flow-regulated by the bypass-side flow-regulating valve 14d and is decompressed (from Fig.15 The refrigerant decompressed by the bypass-side flow rate regulating valve 14d flows into one inlet of the seventh three-way joint 12g.

[0301] In the seventh three-way joint 12g, the refrigerant flowing out of the sixth three-way joint 12f and the refrigerant flowing out of the bypass passage 21c merge and mix. The refrigerant flowing out of the seventh three-way joint 12g flows into the accumulator 23 via the eighth three-way joint 12h. The refrigerant flowing into the accumulator 23 is more uniformly mixed ( Fig.15 The refrigerant flowing out of the accumulator 23 is sucked into the compressor 11 and compressed again.

[0302] In addition, in the high temperature side heat medium circuit 40 in the HG dehumidification heating mode, Fig.14 As shown by the solid arrows, similarly to the cooling-only mode, the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0303] In the HG dehumidification and heating mode, the indoor air conditioning unit 30 blows the conditioned air whose temperature is adjusted so as to approach the target outlet temperature TAO into the vehicle interior as in the series dehumidification and heating mode. Thus, dehumidification and heating of the vehicle interior are achieved.

[0304] In the HG dehumidification and heating mode, the refrigerant having a relatively high enthalpy ratio is merged with the refrigerant flowing out of the refrigerator 20 via the bypass passage 21 c.

[0305] Thus, when the refrigerant discharge capacity of the compressor 11 is increased, the refrigerant evaporation pressure of the indoor evaporator 18 is not decreased, and the heating capacity of the high-temperature side heat medium in the water-refrigerant heat exchanger 13 can be improved. That is, when the refrigerant discharge capacity of the compressor 11 is increased, the heating capacity of the high-temperature side heat medium in the water-refrigerant heat exchanger 13 can be improved without causing frost on the indoor evaporator 18.

[0306] Therefore, in the HG dehumidification and heating mode, the heating capacity of the supply air in the heating unit can be improved compared to the series dehumidification and heating mode.

[0307] (3-2) External air heat absorption HG dehumidification heating mode

[0308] In the outdoor air heat absorption HG dehumidification heating mode, the control device 60 executes Fig.16 The control flow for the outdoor air heat absorption HG dehumidification heating mode shown.

[0309] exist Fig.16 In steps S1801 to S1808, the HG dehumidification and heating mode Fig.13 Steps S1901 to S1908 of the same method determine the control states of various control target devices. Therefore, in the outdoor air heat absorption HG dehumidification and heating mode, step S1807 is a target evaporator temperature determination unit.

[0310] In step S1809, a target superheat SHO2 of the refrigerant at the outlet of the outdoor heat exchanger 15 is determined. As the target superheat SHO2, a preset constant (5°C in this embodiment) can be used, similarly to the target superheat SHEO of the refrigerant at the outlet of the indoor evaporator 18.

[0311] In step S1810, the increase or decrease amount ΔEVH of the throttling opening of the heating expansion valve 14a is determined. The increase or decrease amount ΔEVH in the outdoor air heat absorption HG dehumidification heating mode is determined by a feedback control method based on the deviation between the target superheat SHO2 and the superheat SH2 of the refrigerant on the outlet side of the outdoor heat exchanger 15, so that the superheat SH2 of the refrigerant on the outlet side of the outdoor heat exchanger 15 is close to the target superheat SHO2.

[0312] The degree of superheat SH2 of the refrigerant on the outlet side of the outdoor heat exchanger 15 is calculated using the outdoor-side refrigerant temperature T2 and the outdoor-side refrigerant pressure P2 detected by the outdoor-side refrigerant temperature and pressure sensor 62c.

[0313] In step S1811 , similarly to the cooling only mode, the opening degree SW of the air mix door 34 is calculated.

[0314] In step S1812, the control signals to be outputted are determined so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a throttling state, the cooling expansion valve 14c is in a throttling state, and the bypass flow control valve 14d is in a throttling state. In addition, the control voltages to be outputted are determined so that the high-pressure side on-off valve 22a and the low-pressure side on-off valve 22b are opened.

[0315] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling only mode.

[0316] In step S1813, a control signal or a control voltage is output to each control target device to obtain the control state of each control target device determined as described above. Figure 3 and Fig.16 As shown in step Z, the control flow returns to step S10.

[0317] Therefore, in the heat pump cycle 10 in the outdoor air heat absorption HG dehumidification heating mode, Fig.17As shown by the solid arrows, the refrigerant discharged from the compressor 11 flows in the same manner as in the HG dehumidification and heating mode. Furthermore, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the second three-way joint 12b, the heating expansion valve 14a, the outdoor heat exchanger 15, the low-pressure side passage 21b, the eighth three-way joint 12h, the accumulator 23, and the suction port of the compressor 11.

[0318] That is, the refrigerant circuit is switched to the following one: the indoor evaporator 18 and the outdoor heat exchanger 15 are connected in parallel with respect to the flow of the refrigerant flowing out of the water refrigerant heat exchanger 13. Therefore, in the heat pump cycle 10 in the HG dehumidification heating mode, Fig.18 As shown in the Mollier line diagram, the state of the refrigerant changes.

[0319] exist Fig.18 In Fig.15 The same symbols (letters) represent the same as those described in the HG dehumidification and heating mode. Fig.15 The Mollier diagram of FIG. 1 shows the state of the refrigerant in the same position in the cycle structure, with only the letter (number) changed to match the figure number. This is also the case with the following Mollier diagrams.

[0320] In the HG dehumidification and heating mode with heat absorption from the outside air, the flow of the refrigerant flowing out of the water-refrigerant heat exchanger 13 is branched by the second three-way joint 12b relative to the HG dehumidification and heating mode. The refrigerant flowing out of one outlet of the second three-way joint 12b flows into the heating expansion valve 14a and is decompressed (from Fig.18 from point b18 to point c18).

[0321] The refrigerant decompressed by the heating expansion valve 14a flows into the outdoor heat exchanger 15. The refrigerant flowing into the outdoor heat exchanger 15 absorbs heat from the outside air and evaporates (from Fig.18 The refrigerant flowing out of the outdoor heat exchanger 15 flows into one inlet of the eighth three-way joint 12h through the low-pressure side passage 21b.

[0322] In this embodiment, the target superheat degree SHEO of the refrigerant at the outlet of the indoor evaporator 18 and the target superheat degree SHO2 of the refrigerant at the outlet of the outdoor heat exchanger 15 are set to the same value. Fig.18 point d18) and the state of the refrigerant flowing out of the indoor evaporator 18 ( Fig.18 f18 point) are substantially the same.

[0323] In the eighth three-way joint 12h, the refrigerant flowing out of the outdoor heat exchanger 15 merges with the refrigerant flowing out of the seventh three-way joint 12g and mixes. The refrigerant flowing out of the eighth three-way joint 12h flows into the accumulator 23. The refrigerant flowing into the accumulator 23 is more uniformly mixed ( Fig.18 The refrigerant flowing out of the accumulator 23 is sucked into the compressor 11 and compressed again. The other actions are the same as those in the HG dehumidification and heating mode.

[0324] In addition, in the high temperature side heat medium circuit 40 in the outdoor air heat absorption HG dehumidification heating mode, as shown in FIG. Fig.17 As shown by the solid arrows, similarly to the cooling-only mode, the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0325] In the indoor air conditioning unit 30 in the outdoor air heat absorption HG dehumidification and heating mode, the conditioned air having a temperature adjusted to approach the target outlet temperature TAO is blown into the vehicle interior as in the series dehumidification and heating mode.

[0326] In the outside air heat absorption HG dehumidification and heating mode, similarly to the HG dehumidification and heating mode, the heating capacity of the supply air in the heating unit can be improved compared to the series dehumidification and heating mode. Moreover, in the outside air heat absorption HG dehumidification and heating mode, the supply air can be heated by using the heat absorbed from the outside air by the refrigerant in the outdoor heat exchanger 15. Therefore, in the outside air heat absorption HG dehumidification and heating mode, the operating efficiency of the heat pump cycle 10 can be improved compared to the HG dehumidification and heating mode.

[0327] (4-1) External air absorption heating mode

[0328] In the outdoor air heat absorption heating mode, the control device 60 executes the control flow for the outdoor air heat absorption heating mode. In the control flow for the outdoor air heat absorption heating mode, the control device 60 determines the target high temperature side heat medium temperature TWHO of the high temperature side heat medium in the same manner as in the HG dehumidification heating mode. Furthermore, the control device 60 determines the increase or decrease amount ΔIVO of the rotation speed of the compressor 11 in the same manner as in the HG dehumidification heating mode.

[0329] In addition, the control device 60 determines a target degree of subcooling SCO1 of the refrigerant flowing out of the water-refrigerant heat exchanger 13. The target degree of subcooling SCO1 of the outdoor air heat absorption heating mode is determined based on at least one of the intake air temperature Tin and the outdoor air temperature Tam, and with reference to a control map pre-stored in the control device 60. In the control map of the outdoor air heat absorption heating mode, the target degree of subcooling SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches a maximum value.

[0330] Furthermore, the control device 60 determines the increase or decrease amount ΔEVH of the throttling opening of the heating expansion valve 14a. The increase or decrease amount ΔEVH in the outdoor heat absorption heating mode is based on the deviation between the target supercooling degree SCO1 and the supercooling degree SC1 of the refrigerant flowing out of the water refrigerant heat exchanger 13, and is determined by a feedback control method so that the supercooling degree SC1 of the refrigerant flowing out of the water refrigerant heat exchanger 13 is close to the target supercooling degree SCO1.

[0331] In addition, the control device 60 calculates the opening degree SW of the air mix door 34 in the same manner as in the cooling only mode.

[0332] In addition, the control device 60 determines the control signals to be outputted respectively so that the heating expansion valve 14a is in the throttling state, the cooling expansion valve 14b is in the fully closed state, the cooling expansion valve 14c is in the fully closed state, and the bypass side flow control valve 14d is in the fully closed state. In addition, the control device 60 determines the control voltages to be outputted respectively so that the high-pressure side on-off valve 22a is closed and the low-pressure side on-off valve 22b is opened.

[0333] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling only mode.

[0334] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0335] Therefore, in the heat pump cycle 10 in the outdoor air heat absorption heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the low-pressure side passage 21b, the liquid storage tank 23, and the suction port of the compressor 11.

[0336] Therefore, in the heat pump cycle 10 in the outdoor air heat absorption heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 13 functions as a condenser and the outdoor heat exchanger 15 functions as an evaporator. In the water refrigerant heat exchanger 13, the refrigerant transfers heat to the high-temperature side heat medium, thereby heating the high-temperature side heat medium. In addition, in the outdoor heat exchanger 15, the refrigerant absorbs heat from the outdoor air and evaporates.

[0337] In the high temperature side heat medium circuit 40 in the outdoor air heat absorption heating mode, similarly to the cooling alone mode, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0338] In addition, in the indoor air conditioning unit 30 in the outdoor air absorption heating mode, the supply air blown from the indoor blower 32 passes through the indoor evaporator 18. The supply air after passing through the indoor evaporator 18 is heated by the heater core 42 according to the opening degree of the air mixing door 34. Then, the conditioned air after the temperature is adjusted so as to be close to the target blowing temperature TAO is blown into the vehicle interior. Thus, heating of the vehicle interior is achieved.

[0339] (4-2) HG heating mode

[0340] In the HG heating mode, the control device 60 executes Fig.19 The control flow for HG heating mode is shown.

[0341] First, in step S2801, the target high temperature side heat medium temperature TWHO of the high temperature side heat medium is determined in the same manner as in the HG dehumidification and heating mode. Then, in step S2802, the increase or decrease amount ΔIVO of the rotation speed of the compressor 11 is determined in the same manner as in the HG dehumidification and heating mode.

[0342] In step S2803, a target differential pressure ΔPO is determined. The target differential pressure ΔPO is a target value of the actual differential pressure ΔP of the heat pump cycle 10. The actual differential pressure ΔP can be calculated by subtracting the chiller-side refrigerant pressure Pc from the discharge refrigerant pressure Pd detected by the discharge refrigerant temperature pressure sensor 62a. The target differential pressure ΔPO is a value obtained by subtracting the target low pressure PSO from the target high pressure PDO, which is the target value of the discharge refrigerant pressure Pd.

[0343] The target high pressure PDO can be determined based on the target high temperature side heat medium temperature TWHO. The target low pressure PSO is determined so that the compression workload of the compressor 11 can ensure sufficient heat for heating the high temperature side heat medium to a desired temperature.

[0344] In step S2804, the amount of increase or decrease ΔEVHG of the opening of the bypass flow control valve 14d is determined. The amount of increase or decrease ΔEVHG in the HG heating mode is determined by feedback control based on the deviation between the target differential pressure ΔPO and the actual differential pressure ΔP so that the actual differential pressure ΔP approaches the target differential pressure ΔPO.

[0345] In step S2805, the target degree of subcooling SCO1 is determined in the same manner as in the HG dehumidification and heating mode. Then, in step S2806, the amount of increase or decrease ΔEVB of the throttle opening of the cooling expansion valve 14c is determined in the same manner as in the HG dehumidification and heating mode.

[0346] In step S2807, the opening degree SW of the air mix door 34 is calculated in the same manner as in the cooling only mode.

[0347] In step S2808, the control signals to be outputted are determined so that the heating expansion valve 14a is fully closed, the cooling expansion valve 14b is fully closed, the cooling expansion valve 14c is throttled, and the bypass flow control valve 14d is throttled. In addition, the control voltages to be outputted are determined so that the high-pressure side on-off valve 22a is opened and the low-pressure side on-off valve 22b is closed.

[0348] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling only mode.

[0349] In step S2809, a control signal or a control voltage is output to each control target device to obtain the control state of each control target device determined as described above. Figure 3 and Fig.19 As shown in step Z, the control flow returns to step S10.

[0350] Therefore, in the heat pump cycle 10 in the HG heating mode, if Fig. 20 As shown by the solid arrows, the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the high-pressure side passage 21a, the cooling expansion valve 14c, the chiller 20, the seventh three-way joint 12g, the accumulator 23, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the bypass-side flow control valve 14d arranged in the bypass passage 21c, the seventh three-way joint 12g, the accumulator 23, and the suction port of the compressor 11.

[0351] Therefore, in the heat pump cycle 10 in the HG heating mode, the state of the refrigerant is as follows: Fig.21 The changes are as shown in the Mollier Line Chart.

[0352] The discharged refrigerant ( Fig.21 The refrigerant branched from the first three-way joint 12a flows into the water-refrigerant heat exchanger 13, and radiates heat to the high-temperature side heat medium (from Fig.21 As a result, the high temperature side heat medium is heated.

[0353] The refrigerant flowing out of the water-refrigerant heat exchanger 13 flows into the high-pressure side passage 21a. The refrigerant flowing into the high-pressure side passage 21a flows into the cooling expansion valve 14c through the fifth three-way joint 12e and is decompressed (from Fig.21 from point b21 to point g21).

[0354] The refrigerant decompressed by the cooling expansion valve 14c flows into the chiller 20. In the HG heating mode, since the low-temperature side pump 51 is stopped, the refrigerant and the low-temperature side heat medium do not exchange heat in the chiller 20. The refrigerant flowing out of the chiller 20 flows into one inlet of the seventh three-way joint 12g via the sixth three-way joint 12f.

[0355] The other refrigerant branched from the first three-way joint 12a flows into the bypass passage 21c. The refrigerant flowing into the bypass passage 21c is flow-regulated by the bypass-side flow-regulating valve 14d and is decompressed (from Fig.21 The refrigerant decompressed by the bypass-side flow rate regulating valve 14d flows into one inlet of the seventh three-way joint 12g.

[0356] In the seventh three-way joint 12g, the refrigerant flowing out of the sixth three-way joint 12f merges with the refrigerant flowing out of the bypass passage 21c and mixes. The refrigerant flowing out of the seventh three-way joint 12g flows into the accumulator 23 via the eighth three-way joint 12h. The refrigerant flowing into the accumulator 23 is more uniformly mixed ( Fig.21 The refrigerant flowing out of the accumulator 23 is sucked into the compressor 11 and compressed again.

[0357] In addition, in the high temperature side heat medium circuit 40 in the HG heating mode, as shown in FIG. Fig. 20 As shown by the solid arrows, similarly to the cooling-only mode, the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0358] In the HG heating mode, the indoor air conditioning unit 30 blows the conditioned air whose temperature is adjusted so as to approach the target outlet temperature TAO into the vehicle interior, similarly to the outdoor air absorption heating mode.

[0359] In the HG heating mode, the refrigerant with a relatively high enthalpy ratio is merged with the refrigerant flowing out of the cooling side expansion valve 14c via the bypass passage 21c. Thus, by increasing the refrigerant discharge capacity of the compressor 11, the cycle can be balanced even if the heat dissipation of the refrigerant in the water-refrigerant heat exchanger 13 to the high temperature side heat medium is increased.

[0360] Therefore, in the HG heating mode, the heating capacity of the supply air in the heating unit can be improved compared to the outdoor air heat absorption heating mode.

[0361] (5) Cooling mode

[0362] In the cooling mode, the control device 60 executes the control flow for the cooling mode. In the control flow for the cooling mode, the control device 60 determines the target evaporator temperature TEO in the same manner as in the cooling mode alone. Furthermore, the control device 60 determines the increase or decrease amount ΔIVO of the rotation speed of the compressor 11 in the same manner as in the cooling mode alone.

[0363] In addition, the control device 60 determines the target degree of subcooling SCO2 of the refrigerant flowing out of the outdoor heat exchanger 15, similarly to the cooling only mode. Furthermore, the control device 60 determines the amount of increase or decrease ΔEVC of the throttle opening of the cooling expansion valve 14b, similarly to the cooling only mode.

[0364] Furthermore, the control device 60 determines a target degree of superheat SHCO of the refrigerant on the outlet side of the refrigerant passage of the chiller 20. As the target degree of superheat SHCO, a preset constant (5°C in the present embodiment) can be adopted.

[0365] Furthermore, the control device 60 determines the increase or decrease amount ΔEVB of the throttling opening of the cooling expansion valve 14c. The increase or decrease amount ΔEVB in the cooling mode is based on the deviation between the target superheat SHCO and the superheat SHC of the refrigerant flowing out of the refrigerant passage of the cold machine 20, and is determined by a feedback control method so that the superheat SHC of the refrigerant flowing out of the refrigerant passage of the cold machine 20 approaches the target superheat SHCO.

[0366] The degree of superheat SHC of the refrigerant flowing out of the refrigerant passage of the chiller 20 is calculated using the chiller-side refrigerant temperature Tc and the chiller-side refrigerant pressure Pc detected by the chiller-side refrigerant temperature and pressure sensor 62e.

[0367] The control device 60 also determines a target low-temperature heat medium temperature TWLO of the low-temperature heat medium flowing out of the heat medium passage of the chiller 20. The target low-temperature heat medium temperature TWLO is determined based on the calorific value of the battery 70 and the outside air temperature Tam, with reference to a control map pre-stored in the control device 60.

[0368] In the control map of the cooling mode, in order to achieve appropriate cooling of the battery 70, it is determined that the target low-temperature side heat medium temperature TWLO decreases as the heat amount of the battery 70 increases and the outside air temperature Tam rises. Furthermore, when the first low-temperature side heat medium temperature TWL1 is lower than the target low-temperature side heat medium temperature TWLO, the control device 60 sets the cooling expansion valve 14c to a fully closed state.

[0369] In addition, the control device 60 calculates the opening degree SW of the air mix door 34 in the same manner as in the cooling only mode.

[0370] In addition, the control device 60 determines the control signals to be outputted respectively so that the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is throttled, the cooling expansion valve 14c is throttled, and the bypass flow control valve 14d is fully closed. In addition, the control device 60 determines the control voltages to be outputted respectively so that the high-pressure side on-off valve 22a and the low-pressure side on-off valve 22b are closed.

[0371] Furthermore, the control device 60 appropriately determines the operating states of other control target devices. For example, the control device 60 determines the control voltages to be output to the high temperature side pump 41 and the low temperature side pump 51, respectively, so as to exert the preset reference pressure delivery capacity. For example, the control device 60 determines the operating state of the heat medium three-way valve 53 so that the first low temperature side heat medium temperature TWL1 detected by the first low temperature side heat medium temperature sensor 64a approaches the target low temperature side heat medium temperature TWLO.

[0372] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0373] Therefore, in the heat pump cycle 10 in the cooling mode, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a which is fully opened, the outdoor heat exchanger 15, the fifth three-way joint 12e, the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a which is fully opened, the outdoor heat exchanger 15, the fifth three-way joint 12e, the cooling expansion valve 14c, the chiller 20, the accumulator 23, and the suction port of the compressor 11.

[0374] That is, the refrigerant circuit is switched to a refrigerant circuit in which the indoor evaporator 18 and the chiller 20 are connected in parallel with respect to the flow of the refrigerant flowing out of the water-refrigerant heat exchanger 13 .

[0375] Therefore, in the heat pump cycle 10 in the cooling mode, a vapor compression refrigeration cycle is constructed in which the water refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers and the indoor evaporator 18 and the refrigerator 20 function as evaporators.

[0376] In the water-refrigerant heat exchanger 13, the high-temperature side heat medium is heated by the refrigerant transferring heat to the high-temperature side heat medium. In the indoor evaporator 18, the refrigerant absorbs heat from the supply air, and the supply air is cooled. In the refrigerator 20, the refrigerant absorbs heat from the low-temperature side heat medium, and the low-temperature side heat medium is cooled.

[0377] In the high temperature side heat medium circuit 40 in the cooling mode, similarly to the cooling alone mode, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0378] In the low-temperature side heat medium circuit 50 in the cooling mode, the low-temperature side heat medium cooled to a temperature close to the target low-temperature side heat medium temperature TWLO flows into the cooling water passage 70a of the battery 70. Then, the battery 70 is cooled by the low-temperature side heat medium flowing through the cooling water passage 70a of the battery 70.

[0379] In the interior air conditioning unit 30 in the cooling mode, the conditioned air having a temperature adjusted so as to approach the target outlet temperature TAO is blown into the vehicle interior as in the cooling mode alone, thereby cooling the vehicle interior.

[0380] (6) Cooling series dehumidification and heating mode

[0381] In the cooling series dehumidification and heating mode, the control device 60 executes the control flow for the cooling series dehumidification and heating mode. In the control flow for the cooling series dehumidification and heating mode, the control device 60 determines the target evaporator temperature TEO in the same manner as in the series dehumidification and heating mode. Therefore, the control flow of the series dehumidification and heating mode includes a target evaporator temperature determination unit. Moreover, the control device 60 determines the increase or decrease amount ΔIVO of the rotation speed of the compressor 11 in the same manner as in the series dehumidification and heating mode.

[0382] In addition, the control device 60 determines the target high temperature side heat medium temperature TWHO of the high temperature side heat medium in the same manner as in the series dehumidification and heating mode. In addition, the control device 60 determines the change amount ΔKPN1 of the opening pattern KPN1 in the same manner as in the series dehumidification and heating mode.

[0383] In addition, the control device 60 determines the target superheat SHCO of the refrigerant at the outlet side of the refrigerant passage of the refrigerator 20 as in the cooling mode. In addition, the control device 60 determines the increase or decrease amount ΔEVB of the throttle opening of the cooling expansion valve 14c as in the cooling mode.

[0384] In addition, the control device 60 determines the target low-temperature-side heat medium temperature TWLO in the same manner as in the cooling mode.

[0385] In addition, the control device 60 calculates the opening degree SW of the air mix door 34 in the same manner as in the cooling only mode.

[0386] In addition, the control device 60 determines the control signals to be outputted respectively so as to set the heating expansion valve 14a to the throttling state, the cooling expansion valve 14b to the throttling state, the cooling expansion valve 14c to the throttling state, and the bypass flow control valve 14d to the fully closed state. In addition, the control device 60 determines the control voltages to be outputted respectively so as to close the high-pressure side opening and closing valve 22a and close the low-pressure side opening and closing valve 22b.

[0387] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode.

[0388] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0389] Therefore, in the heat pump cycle 10 in the cooling series dehumidification heating mode, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the cooling expansion valve 14c, the chiller 20, the accumulator 23, and the suction port of the compressor 11.

[0390] That is, the refrigerant circuit is switched to a refrigerant circuit in which the indoor evaporator 18 and the cooling machine 20 are connected in parallel with respect to the flow of the refrigerant flowing out of the outdoor heat exchanger 15 .

[0391] Therefore, in the heat pump cycle 10 in the cooling series dehumidification heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 13 functions as a condenser and the indoor evaporator 18 and the refrigerator 20 function as evaporators.

[0392] Furthermore, in the heat pump cycle 10 in the cooling series dehumidification heating mode, when the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is higher than the outside air temperature Tam, the outdoor heat exchanger 15 is made to function as a condenser. In addition, when the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is lower than the outside air temperature Tam, the outdoor heat exchanger 15 is made to function as an evaporator.

[0393] In the water-refrigerant heat exchanger 13, the high-temperature side heat medium is heated by the refrigerant transferring heat to the high-temperature side heat medium. In addition, in the indoor evaporator 18, the refrigerant absorbs heat from the supply air, and the supply air is cooled. In addition, in the refrigerator 20, the refrigerant absorbs heat from the low-temperature side heat medium, and the low-temperature side heat medium is cooled.

[0394] In the high temperature side heat medium circuit 40 in the cooling series dehumidification heating mode, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 similarly to the cooling alone mode.

[0395] In the low-temperature side heat medium circuit 50 in the cooling series dehumidification heating mode, similarly to the cooling refrigeration mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0396] In the indoor air conditioning unit 30 in the cooling series dehumidification and heating mode, the conditioned air having a temperature adjusted so as to approach the target outlet temperature TAO is blown into the vehicle interior as in the series dehumidification and heating mode. Thus, dehumidification and heating of the vehicle interior are achieved.

[0397] (7-1) Cooling HG Dehumidification Heating Mode

[0398] In the cooling HG dehumidification heating mode, the control device 60 performs Fig. 22 The control flow for the cooling HG dehumidification heating mode is shown.

[0399] exist Fig. 22 In steps S1601 to S1609, the HG dehumidification and heating mode Fig.13 Steps S1901 to S1909 similarly determine the control states of various control target devices. Therefore, in the cooling HG dehumidification and heating mode, step S1607 is a target evaporator temperature determination unit.

[0400] In step S1610, the target low-temperature-side heat medium temperature TWLO is determined in the same manner as in the cooling mode.

[0401] In step S1611, a water temperature determination is performed. Specifically, it is determined whether or not the first low-temperature-side heat medium temperature TWL1 is higher than the target low-temperature-side heat medium temperature TWLO.

[0402] In step S1611, when it is determined that the first low temperature heat medium temperature TWL1 is higher than the target low temperature heat medium temperature TWLO, the process proceeds to step S1612. In step S1612, the control voltage output to the low temperature pump 51 is determined to achieve a preset reference pressure delivery capability, and the process proceeds to step S1614.

[0403] In step S1611, when it is determined that the first low-temperature-side heat medium temperature TWL1 is not higher than the target low-temperature-side heat medium temperature TWLO, the process proceeds to step S1613. In step S1613, it is determined to stop the low-temperature-side pump 51, and the process proceeds to step S1614.

[0404] In step S1614, the control signals to be outputted are determined so that the heating expansion valve 14a is fully closed, the cooling expansion valve 14b is throttled, the cooling expansion valve 14c is throttled, and the bypass flow control valve 14d is throttled. In addition, the control voltages to be outputted are determined so that the high-pressure side on-off valve 22a is opened and the low-pressure side on-off valve 22b is closed.

[0405] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode.

[0406] In step S1615, a control signal or a control voltage is output to each control target device to obtain the control state of each control target device determined as described above. Figure 3 and Fig. 22 As shown in step Z, the control flow returns to step S10.

[0407] Therefore, in the heat pump cycle 10 in the cooling HG dehumidification heating mode, as Fig.14 As shown by the solid arrows in , the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates in the same order as in the HG dehumidification and heating mode.

[0408] Therefore, in the heat pump cycle 10 in the cooling HG dehumidification heating mode, the state of the refrigerant is as follows: Fig.23 In the cooling HG dehumidification and heating mode, the refrigerant flowing into the refrigerator 20 absorbs heat from the low temperature side heat medium (from Fig.23 g23 point to h23 point). Thus, the low temperature side heat medium is cooled. The other operations of the heat pump cycle 10 are the same as those in the HG dehumidification heating mode.

[0409] In addition, in the high temperature side heat medium circuit 40 in the cooling HG dehumidification heating mode, as shown in FIG. Fig.14 As shown by the solid arrows, similarly to the cooling-only mode, the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0410] In addition, in the low temperature side heat medium circuit 50 in the cooling HG dehumidification heating mode, as shown in FIG. Fig.14 As shown by the dashed arrows, similarly to the cooling mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0411] In the interior air conditioning unit 30 in the cooling HG dehumidification and heating mode, the conditioned air having a temperature adjusted so as to approach the target outlet temperature TAO is blown into the vehicle interior as in the HG dehumidification and heating mode. Thus, dehumidification and heating of the vehicle interior are achieved.

[0412] In the cooling HG dehumidification and heating mode, the refrigerant discharge capacity of the compressor 11 can be increased similarly to the HG dehumidification and heating mode, and the heating capacity of the high-temperature side heat medium in the water-refrigerant heat exchanger 13 can be improved. Therefore, in the cooling HG dehumidification and heating mode, the battery 70 can be cooled, and the heating capacity of the supply air in the heating unit can be improved compared to the cooling series dehumidification and heating mode.

[0413] (7-2) Cooling the outside air to absorb heat HG dehumidification and heating mode

[0414] In the cooling outside air heat absorption HG dehumidification heating mode, the control device 60 executes Fig.24 The control flow for the cooling outside air heat absorption HG dehumidification heating mode shown.

[0415] exist Fig.24 In steps S1501 to S1511, the external air heat absorption HG dehumidification heating mode Fig.16 Steps S1801 to S1811 of the same method determine the control states of various control target devices. Therefore, in the cooling outside air heat absorption HG dehumidification heating mode, step S1507 is a target evaporator temperature determination unit.

[0416] Moreover, in Fig.24 In steps S1512 to S1515, the cooling HG dehumidification heating mode Fig.23 Steps S1610 to S1613 of the same procedure determine the target low-temperature-side heat medium temperature TWLO and the control state of the low-temperature-side pump 51 .

[0417] In step S1516, the control signals to be outputted are determined so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a throttling state, the cooling expansion valve 14c is in a throttling state, and the bypass flow control valve 14d is in a throttling state. In addition, the control voltages to be outputted are determined so that the high-pressure side on-off valve 22a is opened and the low-pressure side on-off valve 22b is closed.

[0418] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode.

[0419] In step S1517, a control signal or a control voltage is output to each control target device to obtain the control state of each control target device determined as described above. Figure 3 and Fig.24As shown in step Z, the control flow returns to step S10.

[0420] Therefore, in the heat pump cycle 10 in the dehumidification heating mode of cooling the outside air and absorbing heat HG, Fig.17 As shown by the solid arrows, the refrigerant circuit is switched to the following one: the refrigerant discharged from the compressor 11 circulates in the same order as the outdoor air heat absorption HG dehumidification and heating mode.

[0421] Therefore, in the heat pump cycle 10 in the dehumidification heating mode of cooling the outside air and absorbing heat HG, the state of the refrigerant is as follows: Fig.25 In the cooling outside air heat absorption HG dehumidification heating mode, the refrigerant flowing into the cold machine 20 absorbs heat from the low temperature side heat medium (from Fig.25 g25 point to h25 point). Thus, the low temperature side heat medium is cooled. The other operations of the heat pump cycle 10 are the same as those in the outdoor air absorption HG dehumidification heating mode.

[0422] In addition, in the high temperature side heat medium circuit 40 in the cooling outside air heat absorption HG dehumidification heating mode, as shown in FIG. Fig.17 As shown by the solid arrows, similarly to the cooling-only mode, the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0423] In addition, in the low temperature side heat medium circuit 50 in the cooling outside air heat absorption HG dehumidification heating mode, as shown in FIG. Fig.17 As shown by the dashed arrows, similarly to the cooling mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0424] In the indoor air conditioning unit 30 in the cooling and heating mode, the conditioned air is blown into the vehicle interior after being adjusted in temperature to be close to the target outlet temperature TAO, similarly to the heating mode.

[0425] In the cooling outside air heat absorption HG dehumidification and heating mode, while cooling the battery 70 as in the cooling HG dehumidification and heating mode, the heating capacity of the supply air in the heating unit can be improved compared to the cooling series dehumidification and heating mode.

[0426] Furthermore, in the cooling outside air heat absorption HG dehumidification and heating mode, the supply air can be heated by utilizing the heat absorbed from the outside air by the refrigerant in the outdoor heat exchanger 15. Therefore, in the cooling outside air heat absorption HG dehumidification and heating mode, the operation efficiency of the heat pump cycle 10 can be improved compared to the cooling HG dehumidification and heating mode.

[0427] (8) Cooling equipment heat absorption heating mode

[0428] In the cooling device heat absorption heating mode, the control device 60 executes a control flow for the cooling device heat absorption heating mode. In the control flow for the cooling device heat absorption heating mode, the control device 60 determines the target low temperature side heat medium temperature TWLO similarly to the cooling and cooling mode.

[0429] Furthermore, the control device 60 determines the increase or decrease amount ΔIVO of the rotation speed of the compressor 11. The increase or decrease amount ΔIVO in the cooling device heat absorption heating mode is determined by a feedback control method based on the deviation between the target low-temperature side heat medium temperature TWLO and the first low-temperature side heat medium temperature TWL1, so that the first low-temperature side heat medium temperature TWL1 approaches the target low-temperature side heat medium temperature TWLO.

[0430] In addition, the control device 60 determines the target degree of subcooling SCO2 of the refrigerant flowing out of the outdoor heat exchanger 15 in the same manner as in the cooling only mode.

[0431] Furthermore, the control device 60 determines the increase or decrease amount ΔEVB of the throttling opening of the cooling expansion valve 14c. The increase or decrease amount ΔEVB in the cooling device heat absorption heating mode is determined based on the deviation between the target supercooling degree SCO2 and the supercooling degree SC2 of the refrigerant flowing out of the outdoor heat exchanger 15, etc., and is determined by a feedback control method so that the supercooling degree SC2 of the refrigerant flowing out of the water-refrigerant heat exchanger 13 is close to the target supercooling degree SCO2.

[0432] In addition, the control device 60 calculates the opening degree SW of the air mix door 34 in the same manner as in the cooling only mode.

[0433] In addition, the control device 60 determines the control signals to be outputted respectively so as to fully open the heating expansion valve 14a, fully close the cooling expansion valve 14b, throttle the cooling expansion valve 14c, and fully close the bypass flow control valve 14d. In addition, the control device 60 determines the control voltages to be outputted respectively so as to close the high-pressure side on-off valve 22a and close the low-pressure side on-off valve 22b.

[0434] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode.

[0435] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0436] Therefore, in the heat pump cycle 10 of the cooling device heat absorption heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the fully opened heating expansion valve 14a, the outdoor heat exchanger 15, the cooling expansion valve 14c, the cold machine 20, the liquid storage tank 23, and the suction port of the compressor 11.

[0437] Therefore, in the heat pump cycle 10 in the cooling device heat absorption heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers and the refrigerator 20 functions as an evaporator.

[0438] In the water-refrigerant heat exchanger 13, the high-temperature side heat medium is heated by the refrigerant transferring heat to the high-temperature side heat medium. In the refrigerator 20, the low-temperature side heat medium is cooled by the refrigerant absorbing heat from the low-temperature side heat medium.

[0439] Furthermore, in the high temperature side heat medium circuit 40 in the cooling device heat absorption heating mode, similarly to the cooling alone mode, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0440] In the low-temperature side heat medium circuit 50 in the cooling device heat absorption heating mode, similarly to the cooling and refrigeration mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0441] In the cooling device heat absorption heating mode, the indoor air conditioning unit 30 blows the conditioned air whose temperature is adjusted so as to approach the target air outlet temperature TAO into the vehicle interior, similarly to the outdoor air heat absorption heating mode.

[0442] (9) Cooling external air heat absorption heating mode

[0443] In the cooling outside air heat absorption heating mode, the control device 60 executes a control flow for the cooling outside air heat absorption heating mode. In the control flow for the cooling outside air heat absorption heating mode, the control device 60 determines the target low temperature side heat medium temperature TWLO similarly to the cooling cooling mode.

[0444] Furthermore, the control device 60 determines the increase or decrease amount ΔIVO of the rotation speed of the compressor 11. The increase or decrease amount ΔIVO in the cooling outside air heat absorption heating mode is determined by a feedback control method based on the deviation between the target low-temperature side heat medium temperature TWLO and the first low-temperature side heat medium temperature TWL1, so that the first low-temperature side heat medium temperature TWL1 approaches the target low-temperature side heat medium temperature TWLO.

[0445] In addition, the control device 60 determines the target high temperature side heat medium temperature TWHO of the high temperature side heat medium in the same manner as in the series dehumidification and heating mode. Furthermore, the control device 60 determines the change amount ΔKPN2 of the opening pattern KPN2.

[0446] The opening pattern KPN2 is a parameter for determining a combination of the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14c. The opening pattern KPN2 corresponds to the opening ratio of the throttle opening of the cooling expansion valve 14c to the throttle opening of the heating expansion valve 14a.

[0447] In the control map of the cooling outdoor air endothermic heating mode, the opening pattern KPN2 is increased as the target air temperature TAO increases. That is, as the target air temperature TAO increases, the opening ratio of the throttle opening of the cooling expansion valve 14c to the throttle opening of the heating expansion valve 14a increases.

[0448] In addition, the control device 60 calculates the opening degree SW of the air mix door 34 in the same manner as in the cooling only mode.

[0449] In addition, the control device 60 determines the control signals to be outputted respectively so as to set the heating expansion valve 14a to the throttling state, the cooling expansion valve 14b to the fully closed state, the cooling expansion valve 14c to the throttling state, and the bypass flow control valve 14d to the fully closed state. In addition, the control device 60 determines the control voltages to be outputted respectively so as to close the high-pressure side opening and closing valve 22a and close the low-pressure side opening and closing valve 22b.

[0450] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode.

[0451] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0452] Therefore, in the heat pump cycle 10 of the cooling outdoor air heat absorption heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the cooling expansion valve 14c, the cold machine 20, the liquid storage tank 23, and the suction port of the compressor 11.

[0453] Therefore, in the heat pump cycle 10 in the cooling outside air heat absorption heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 13 functions as a condenser and the refrigerator 20 functions as an evaporator.

[0454] Furthermore, in the heat pump cycle 10 in the cooling outside air heat absorption heating mode, when the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is higher than the outside air temperature Tam, the outdoor heat exchanger 15 is made to function as a condenser. In addition, when the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is lower than the outside air temperature Tam, the outdoor heat exchanger 15 is made to function as an evaporator.

[0455] In the water-refrigerant heat exchanger 13, the high-temperature side heat medium is heated by the refrigerant transferring heat to the high-temperature side heat medium. In the refrigerator 20, the low-temperature side heat medium is cooled by the refrigerant absorbing heat from the low-temperature side heat medium.

[0456] In the high temperature side heat medium circuit 40 in the cooling outdoor air heat absorption heating mode, similarly to the cooling alone mode, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0457] In the low-temperature side heat medium circuit 50 in the cooling outdoor air heat absorption heating mode, similarly to the cooling refrigeration mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0458] In the indoor air conditioning unit 30 in the cooling outside air heat absorption heating mode, the conditioned air whose temperature is adjusted so as to approach the target air outlet temperature TAO is blown into the vehicle interior similarly to the outside air heat absorption heating mode.

[0459] (10-1) Cooling HG Heating Mode

[0460] In the cooling HG heating mode, the control device 60 performs Fig.26 The control flow for the cooling HG heating mode is shown.

[0461] exist Fig.26 In steps S3601 to S3602, the HG dehumidification and heating mode Fig.13 The target high temperature side heat medium temperature TWHO and the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 are determined in the same manner in steps S1901 to S1902. Fig.26 In steps S3603 to S3607, the HG dehumidification and heating mode Fig.13 Steps S1905 to S1909 similarly determine the control states of various control target devices. Therefore, in the cooling HG heating mode, step S3605 is a target evaporator temperature determination unit.

[0462] In step S3608, the control signals to be outputted are determined so that the heating expansion valve 14a is fully closed, the cooling expansion valve 14b is fully closed, the cooling expansion valve 14c is throttled, and the bypass flow control valve 14d is throttled. In addition, the control voltages to be outputted are determined so that the high-pressure side on-off valve 22a is opened and the low-pressure side on-off valve 22b is closed.

[0463] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode.

[0464] In step S3609, a control signal or a control voltage is output to each control target device to obtain the control state of each control target device determined as described above. Figure 3 and Fig.26 As shown in step Z, the control flow returns to step S10.

[0465] Therefore, in the heat pump cycle 10 in the cooling HG heating mode, as Fig. 20 As shown by the solid arrows in , the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates in the same order as in the HG heating mode.

[0466] Therefore, in the heat pump cycle 10 in the cooling HG heating mode, the state of the refrigerant is as follows: Fig. 27 In the cooling HG heating mode, the refrigerant flowing into the refrigerator 20 absorbs heat from the low temperature side heat medium (from Fig. 27 The heat medium on the low temperature side is thereby cooled. The other operations of the heat pump cycle 10 are the same as those in the HG heating mode.

[0467] In addition, in the high temperature side heat medium circuit 40 in the cooling HG heating mode, as shown in FIG. Fig. 20 As shown by the solid arrows, similarly to the cooling-only mode, the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0468] In addition, in the low temperature side heat medium circuit 50 in the cooling HG heating mode, as shown in FIG. Fig. 20 As shown by the dashed arrows, similarly to the cooling mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0469] In the interior air conditioning unit 30 in the cooling HG heating mode, the conditioned air having a temperature adjusted so as to approach the target air outlet temperature TAO is blown into the vehicle interior in the same manner as in the HG heating mode.

[0470] In the cooling HG heating mode, as in the HG heating mode, by increasing the refrigerant discharge capacity of the compressor 11, the cycle can be balanced even if the heating capacity of the high temperature side heat medium in the water refrigerant heat exchanger 13 is increased. Therefore, in the cooling HG heating mode, while cooling the battery 70, the heating capacity of the supply air in the heating unit can be increased compared to the cooling outside air heat absorption heating mode.

[0471] (10-2) Cooling the outside air and absorbing heat HG heating mode

[0472] In the cooling outside air heat absorption HG heating mode, the control device 60 executes Fig.28 The control flow for the cooling outside air heat absorption HG heating mode is shown.

[0473] exist Fig.28 In steps S3501 to S3506, the cooling HG heating mode Fig.26 Steps S3601 to S3606 of the same process determine the control states of various control target devices. Therefore, in the cooling outside air heat absorption HG heating mode, step S3505 is a target evaporator temperature determination unit.

[0474] In step S3507, a target degree of superheat SHO2 of the refrigerant on the outlet side of the outdoor heat exchanger 15 is determined. As the target degree of superheat SHO2, a preset constant (5°C in the present embodiment) can be adopted.

[0475] In step S3508, the increase or decrease amount ΔEVH of the throttling opening of the heating expansion valve 14a is determined. The increase or decrease amount ΔEVH in the cooling outside air heat absorption HG heating mode is based on the deviation between the target superheat SHO2 and the superheat SH2 of the refrigerant on the outlet side of the outdoor heat exchanger 15, and is determined by the feedback control method so that the superheat SH2 of the refrigerant on the outlet side of the outdoor heat exchanger 15 is close to the target superheat SHO2.

[0476] In step S3509, the opening degree SW of the air mix door 34 is calculated in the same manner as in the cooling only mode.

[0477] In step S3510, the control signals to be outputted are determined so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a fully closed state, the cooling expansion valve 14c is in a throttling state, and the bypass flow control valve 14d is in a throttling state. In addition, the control voltages to be outputted are determined so that the high-pressure side on-off valve 22a is opened and the low-pressure side on-off valve 22b is closed.

[0478] Furthermore, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode.

[0479] In step S3511, a control signal or a control voltage is output to each control target device to obtain the control state of each control target device determined as described above. Figure 3 and Fig.28 As shown in step Z, the control flow returns to step S10.

[0480] Therefore, in the heat pump cycle 10 in the heating mode of cooling the outside air and absorbing heat HG, Fig.29 As shown by the solid arrows, the refrigerant discharged from the compressor 11 circulates in the same order as in the HG heating mode. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the second three-way joint 12b, the heating expansion valve 14a, the outdoor heat exchanger 15, the low-pressure side passage 21b, the accumulator 23, and the suction port of the compressor 11.

[0481] That is, the outdoor heat exchanger 15 and the chiller 20 are connected in parallel with respect to the flow of the refrigerant flowing out of the water-refrigerant heat exchanger 13. Therefore, in the heat pump cycle 10 in the heating mode of cooling the outdoor air and absorbing heat HG, the state of the refrigerant is as follows: Fig.30 The changes are as shown in the Mollier Line Chart.

[0482] In the HG heating mode for cooling the outside air and absorbing heat, the flow of the refrigerant flowing out of the water-refrigerant heat exchanger 13 is branched by the second three-way joint 12b, as opposed to the HG heating mode. The refrigerant flowing out of one outlet of the second three-way joint 12b flows into the heating expansion valve 14a and is decompressed (from Fig.30 from point b30 to point c30).

[0483] The refrigerant decompressed by the heating expansion valve 14a flows into the outdoor heat exchanger 15. The refrigerant flowing into the outdoor heat exchanger 15 absorbs heat from the outside air and evaporates (from Fig.30 The refrigerant flowing out of the outdoor heat exchanger 15 flows into one inlet of the eighth three-way joint 12h via the low-pressure side passage 21b.

[0484] Furthermore, in the HG heating mode for cooling the outside air and absorbing heat, the refrigerant flowing into the refrigerator 20 absorbs heat from the low temperature side heat medium (from Fig.30 g30 point to h30 point). Thus, the low temperature side heat medium is cooled. The other operations of the heat pump cycle 10 are the same as those in the HG heating mode.

[0485] In addition, in the high temperature side heat medium circuit 40 in the cooling outside air heat absorption HG heating mode, as shown in FIG. Fig.29As shown by the solid arrows, similarly to the cooling-only mode, the high-temperature-side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 42 .

[0486] In addition, in the low temperature side heat medium circuit 50 in the cooling outside air heat absorption HG heating mode, as shown in FIG. Fig.29 As shown by the dashed arrows, similarly to the cooling mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0487] In the indoor air conditioning unit 30 in the cooling outside air heat absorption HG heating mode, similarly to the HG heating mode, the conditioned air whose temperature is adjusted so as to approach the target outlet temperature TAO is blown into the vehicle interior, thereby heating the vehicle interior.

[0488] In the cooling outside air heat absorption HG heating mode, while cooling the battery 70 as in the cooling HG heating mode, the heating capacity of the supply air in the heating unit can be improved compared to the cooling outside air heat absorption heating mode.

[0489] Furthermore, in the cooling outside air heat absorption HG heating mode, the supply air can be heated using the heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 15. Therefore, in the cooling outside air heat absorption HG heating mode, the operation efficiency of the heat pump cycle 10 can be improved compared with the cooling HG heating mode.

[0490] (11) Cooling mode

[0491] In the cooling mode, the control device 60 executes the control flow for the cooling mode. In the control flow for the cooling mode, the control device 60 determines the target low-temperature side heat medium temperature TWLO and the increase or decrease amount ΔIVO of the rotation speed of the compressor 11 in the same manner as in the cooling device heat absorption heating mode. In addition, the control device 60 determines the target degree of subcooling SCO2 and the increase or decrease amount ΔEVB of the throttle opening of the cooling expansion valve 14c in the same manner as in the cooling device heat absorption heating mode.

[0492] Furthermore, the control device 60 determines the opening degree SW of the air mix door 34 to be 0%. That is, the control device 60 determines the control signal to be output to the actuator for driving the air mix door 34 so that the air mix door 34 is displaced to the maximum cooling position.

[0493] In addition, the control device 60 determines the control signals to be outputted respectively so as to fully open the heating expansion valve 14a, fully close the cooling expansion valve 14b, throttle the cooling expansion valve 14c, and fully close the bypass flow control valve 14d. In addition, the control device 60 determines the control voltages to be outputted respectively so as to close the high-pressure side on-off valve 22a and close the low-pressure side on-off valve 22b.

[0494] Moreover, the control device 60 appropriately determines the operating states of other control target devices in the same manner as in the cooling mode. For example, the control device 60 stops the indoor air-sending device 32.

[0495] The control device 60 outputs control signals or control voltages to various control target devices to obtain the control states of various control target devices determined as described above. Figure 3 As shown in step Z, the control flow returns to step S10.

[0496] Therefore, in the heat pump cycle 10 in the cooling mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the fully opened heating expansion valve 14a, the outdoor heat exchanger 15, the cooling expansion valve 14c, the cold machine 20, the accumulator 23, and the suction port of the compressor 11.

[0497] Therefore, in the heat pump cycle 10 in the cooling mode, a vapor compression refrigeration cycle is configured in which the outdoor heat exchanger 15 functions as a condenser and the refrigerator 20 functions as an evaporator. In the cooling mode, the opening SW of the air mix door 34 is set to 0%. Therefore, when the temperature of the high-temperature side heat medium becomes the same as that of the refrigerant, heat exchange between the refrigerant and the high-temperature side heat medium is not performed in the water-refrigerant heat exchanger 13.

[0498] The heat of the refrigerant is dissipated to the outside air in the outdoor heat exchanger 15. In the refrigerator 20, the refrigerant absorbs heat from the low-temperature side heat medium, so that the low-temperature side heat medium is cooled.

[0499] In the low-temperature side heat medium circuit 50 in the cooling mode, similarly to the cooling mode, the battery 70 is cooled by the cooled low-temperature side heat medium flowing through the cooling water passage 70 a of the battery 70 .

[0500] (12) Air supply mode

[0501] In the air supply mode, the control device 60 stops the compressor 11. In addition, the control device 60 operates the indoor air-sending device 32 based on a setting signal set by the air volume setting switch.

[0502] In the indoor air conditioning unit 30 in the air-sending mode, the air sent from the indoor air-sending fan 32 is blown into the room.

[0503] As described above, in the vehicle air conditioning device 1 of the present embodiment, by switching the various operation modes, it is possible to realize comfortable air conditioning in the vehicle interior while appropriately adjusting the temperature of the battery 70 .

[0504] Moreover, in the vehicle air conditioning device 1 of the present embodiment, when performing dehumidification and heating in the vehicle interior, it is possible to suppress the decrease in the operating efficiency and continuously adjust the temperature of the supply air within a wide range. More specifically, in the vehicle air conditioning device 1 of the present embodiment, as dehumidification and heating modes, there are (2) a series dehumidification and heating mode and (3-1) an HG dehumidification and heating mode.

[0505] In the heat pump cycle 10 in the series dehumidification heating mode, by changing the opening pattern KPN1, the pressure of the refrigerant in the outdoor heat exchanger 15 can be changed while maintaining the refrigerant evaporation temperature in the indoor evaporator 18 at a temperature that can suppress frost formation in the indoor evaporator 18.

[0506] Thus, in the series dehumidification and heating mode, it is possible to suppress frost formation on the indoor evaporator 18 while adjusting the amount of heat exchange between the refrigerant and the outside air in the outdoor heat exchanger 15. Therefore, it is possible to adjust the amount of heat dissipated from the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 13, and continuously adjust the heating capacity of the supply air in the heater core 42.

[0507] In the heat pump cycle 10 in the HG dehumidification and heating mode, by increasing the refrigerant discharge capacity of the compressor 11, frost formation on the indoor evaporator 18 can be suppressed while improving the heating capacity of the supply air in the heater core 42 compared to the series dehumidification and heating mode.

[0508] Furthermore, in the heat pump cycle 10 in the HG dehumidification heating mode, the increase in compression work when the refrigerant discharge capacity of the compressor 11 is increased can be effectively used as a heating source for the supply air. Therefore, when the heating capacity of the supply air in the heating unit is increased, the decrease in the operating efficiency can be suppressed.

[0509] As a result, in the vehicle air conditioning device 1 of this embodiment, when performing dehumidification and heating in the vehicle interior, by switching between the series dehumidification and heating mode and the HG dehumidification and heating mode, the decrease in operation efficiency can be suppressed and the temperature of the supply air can be continuously adjusted within a wider range.

[0510] In addition, in the vehicle air conditioning device 1 of the present embodiment, Figure 3 As shown in step S90, when the target air outlet temperature TAO is lower than the dehumidification reference temperature β1, the HG dehumidification and heating mode can be switched to the series dehumidification and heating mode. In addition, when the target air outlet temperature TAO is higher than the dehumidification reference temperature β1, the series dehumidification and heating mode can be switched to the HG dehumidification and heating mode.

[0511] Thus, the HG dehumidification and heating mode and the series dehumidification and heating mode can be switched reliably through simple control.

[0512] In addition, the vehicle air conditioner 1 of the present embodiment has (3-2) an outside air heat absorption HG dehumidification and heating mode as a dehumidification and heating mode. In the outside air heat absorption HG dehumidification and heating mode, the supply air can be heated using the heat of the outside air. Therefore, compared with the HG dehumidification and heating mode, the power consumption of the compressor 11 can be reduced, and the decrease in the operating efficiency can be further suppressed.

[0513] In addition, in the vehicle air conditioning device 1 of the present embodiment, Figure 5 Steps S140, S170, Fig.11 As described in , the target evaporator temperature TEO is adopted as the outdoor unit temperature Tout. When the outdoor unit temperature difference ΔTO is equal to or greater than the first reference temperature difference KΔTO1, the HG dehumidification and heating mode is switched to the outdoor air heat absorption HG dehumidification and heating mode.

[0514] Thus, when the temperature of the refrigerant flowing into the outdoor heat exchanger 15 is lower than the outside air temperature Tam, the HG dehumidification and heating mode can be switched to the outside air heat absorption HG dehumidification and heating mode. That is, in the outdoor heat exchanger 15, when the refrigerant can reliably absorb the heat of the outside air, the HG dehumidification and heating mode can be switched to the outside air heat absorption HG dehumidification and heating mode.

[0515] Similarly, when the outdoor unit temperature difference ΔTO is greater than the first reference temperature difference KΔTO1, the cooling HG dehumidification heating mode is switched to the cooling outside air heat absorption HG dehumidification heating mode. Thus, in the outdoor heat exchanger 15, when the refrigerant can reliably absorb the heat of the outside air, it is possible to switch from the cooling HG dehumidification heating mode to the cooling outside air heat absorption HG dehumidification heating mode.

[0516] In addition, in the vehicle air conditioning device 1 of the present embodiment, as the dehumidification and heating mode, there are (6) a cooling series dehumidification and heating mode and (7-1) a cooling HG dehumidification and heating mode.

[0517] Therefore, in the vehicle air-conditioning device 1 of the present embodiment, when dehumidifying and heating the vehicle interior, by switching the cooling series dehumidification and heating mode and the cooling HG dehumidification and heating mode, the battery 70 can be cooled while suppressing the decrease in operating efficiency and continuously adjusting the temperature of the supply air within a wider range.

[0518] In addition, in the vehicle air conditioning device 1 of the present embodiment, when heating the vehicle interior, it is possible to suppress a decrease in the operating efficiency and continuously adjust the temperature of the supply air within a wide range. More specifically, in the vehicle air conditioning device 1 of the present embodiment, as heating modes, there are (4-1) an outside air heat absorption heating mode and (4-2) an HG heating mode.

[0519] In the heat pump cycle 10 in the heating mode, by adjusting at least one of the refrigerant discharge capacity of the compressor 11 and the throttling opening of the heating expansion valve 14a, the heat dissipation amount from the refrigerant to the high temperature side heat medium in the water refrigerant heat exchanger 13 can be adjusted. Therefore, the heating capacity of the supply air in the heater core 42 can be continuously adjusted.

[0520] Furthermore, in the heat pump cycle 10 in the HG heating mode, by increasing the refrigerant discharge capacity of the compressor 11 , the heating capacity of the supply air in the heater core 42 can be improved compared to the heating mode.

[0521] Furthermore, in the heat pump cycle 10 in the HG heating mode, the increase in compression work when the refrigerant discharge capacity of the compressor 11 is increased can be effectively used as a heating source for the supply air. Therefore, when the heating capacity of the supply air in the heating unit is increased, a decrease in the operating efficiency can be suppressed.

[0522] As a result, in the vehicle air conditioning device 1 of this embodiment, when heating the vehicle interior, by switching between the outdoor air heat absorption heating mode and the HG heating mode, it is possible to suppress a decrease in operating efficiency and continuously adjust the temperature of the supply air within a wide range.

[0523] In addition, in the vehicle air conditioning device 1 of the present embodiment, Figure 6 As shown in step S240, when the target air blowing temperature TAO is lower than the hot air reference temperature δ, the HG heating mode can be switched to the outdoor air heat absorption heating mode. In addition, when the target air blowing temperature TAO is higher than the hot air reference temperature δ, the outdoor air heat absorption heating mode can be switched to the HG heating mode.

[0524] Thus, the outdoor air heat absorption heating mode and the HG heating mode can be switched reliably through simple control.

[0525] Here, in the HG heating mode, the heating capacity of the heating unit can be adjusted within a wide range by adjusting the refrigerant discharge capacity of the compressor 11. In addition, in the outdoor heat absorption heating mode, since the supply air can be heated by using the heat absorbed by the refrigerant from the outdoor air, it is easy to improve the operation efficiency compared with the HG heating mode. Therefore, it is effective to suppress the decrease in operation efficiency by being able to reliably switch from the HG heating mode to the outdoor heat absorption heating mode.

[0526] In addition, in the vehicle air conditioning device 1 of the present embodiment, as described in step S340, the saturation temperature of the refrigerant at the target low pressure PSO is used as the outdoor unit temperature Tout, and when the outdoor unit temperature difference ΔTO is equal to or greater than the first reference temperature difference KΔTO1, the cooling HG heating mode is switched to the cooling outdoor air heat absorption HG heating mode.

[0527] Thus, when the temperature of the refrigerant flowing into the outdoor heat exchanger 15 is lower than the outside air temperature Tam, the cooling HG heating mode can be switched to the cooling outside air heat absorption HG heating mode. That is, in the outdoor heat exchanger 15, when the refrigerant can reliably absorb the heat of the outside air, the cooling HG heating mode can be switched to the cooling outside air heat absorption HG heating mode.

[0528] In addition, in the vehicle air conditioning device 1 of the present embodiment, as heating modes, there are (9) a cooling outside air heat absorption heating mode and (10-1) a cooling HG heating mode.

[0529] Therefore, in the vehicle air conditioning device 1 of the present embodiment, when heating the vehicle interior, by switching between the cooled outside air heat absorption heating mode and the cooled HG heating mode, the battery 70 can be cooled while suppressing the decrease in operating efficiency and continuously adjusting the temperature of the supply air within a wider range.

[0530] (Second Embodiment)

[0531] In the present embodiment, an example in which the control method related to the switching of the operation mode in the control program is changed from that in the first embodiment will be described.

[0532] In the control procedure of this embodiment, the Figure 3 to Figure 12 The control process selects the initial operation mode in the same manner. Then, the control procedures such as reading the detection signal and the operation signal, calculating the target air outlet temperature TAO, selecting the operation mode based on the currently selected operation mode, and controlling various control target devices corresponding to the operation mode are repeated every predetermined control cycle.

[0533] First, use Fig.31 Selection of the operation mode when the currently selected operation mode is (1) the cooling only mode will be described.

[0534] When the currently selected operation mode is (1) the cooling mode alone, if it is determined that the heating capacity of the supply air is insufficient, (2) the series dehumidification and heating mode is selected.

[0535] Specifically, during the execution of (1) the single cooling mode, when the opening SW of the air mix door 34 is above the reference upper limit opening KSW1 (95% in this embodiment) and the supply air temperature TAV is below the value obtained by subtracting the preset insufficient judgment reference value KTA1 from the target blow-out temperature TAO, it is determined that the heating capacity of the supply air is insufficient. Then, (2) the series dehumidification and heating mode is selected. The insufficient judgment reference value KTA1 is a positive value. In this embodiment, the insufficient judgment reference value KTA1 is set to 3°C.

[0536] Next, selection of the operation mode when the currently selected operation mode is (2) the tandem dehumidification and heating mode will be described.

[0537] When the currently selected operation mode is (2) the tandem dehumidification and heating mode, if it is determined that the heating capacity of the supply air is excessive, (1) the single cooling mode is selected.

[0538] Specifically, in the execution of (2) the series dehumidification and heating mode, when the opening pattern KPN1 becomes above the reference upper limit opening pattern KPN1H and the supply air temperature TAV becomes above the value obtained by adding the target blow-out temperature TAO to the pre-set excess judgment reference value KTA2, it is judged that the heating capacity of the supply air is excessive. Then, (1) the single cooling mode is selected. The excess judgment reference value KTA2 is a positive value. In this embodiment, the excess judgment reference value KTA2 is set to 3°C.

[0539] Furthermore, when the currently selected operation mode is (2) the tandem dehumidification and heating mode, if it is determined that the heating capacity of the supply air is insufficient, (3-1) the HG dehumidification and heating mode is selected.

[0540] Specifically, during the execution of the (2) series dehumidification and heating mode, when the opening pattern KPN1 becomes below the reference lower limit opening pattern KPN1L and the supply air temperature TAV becomes below the value obtained by subtracting the insufficient judgment reference value KTA1 from the target blowing temperature TAO, it is judged that the heating capacity of the supply air is insufficient, and the (3-1) HG dehumidification and heating mode is selected.

[0541] Next, use Fig.31 , Fig.32 Selection of the operation mode when the currently selected operation mode is (3-1) the HG dehumidification and heating mode will be described.

[0542] When the currently selected operation mode is (3-1) the HG dehumidification and heating mode, if it is determined that the dehumidification capacity of the supply air is insufficient, (2) the series dehumidification and heating mode is selected.

[0543] Specifically, when the opening of the bypass flow control valve 14d becomes lower than the reference opening and the evaporator temperature Tefin becomes higher than the value obtained by adding the target evaporator temperature TEO to the pre-set dehumidification judgment reference value KTE during the execution of the (3-1) HG dehumidification and heating mode, it is determined that the dehumidification capacity of the supply air is insufficient. Then, the (2) series dehumidification and heating mode is selected.

[0544] The dehumidification determination reference value KTE is a positive value. In the present embodiment, the dehumidification determination reference value KTE is set to 3° C. As the reference opening of the bypass flow rate control valve 14 d , the minimum opening that can be realized in the control of the bypass flow rate control valve 14 d may be adopted.

[0545] Furthermore, when the currently selected operation mode is (3-1) the HG dehumidification and heating mode, if it is determined that outdoor air heat absorption is possible as described in step S170 of the first embodiment, (3-2) the outdoor air heat absorption HG dehumidification and heating mode is selected.

[0546] Next, use Fig.32 Selection of the operation mode when the currently selected operation mode is (3-2) the outside air heat absorption HG dehumidification and heating mode will be described.

[0547] When the currently selected operation mode is (3-2) the outside air heat absorption HG dehumidification and heating mode, if it is determined that the dehumidification capacity of the supply air is insufficient, (3-1) the HG dehumidification and heating mode is selected.

[0548] Specifically, when the opening of the bypass flow control valve 14d is below the reference opening and the evaporator temperature Tefin is above the value obtained by adding the dehumidification determination reference value KTE to the target evaporator temperature TEO during the execution of the (3-2) outside air heat absorption HG dehumidification heating mode, it is determined that the dehumidification capacity of the supply air is insufficient. Then, the (3-1) HG dehumidification heating mode is selected.

[0549] In addition, when the currently selected operation mode is (3-2) the outside air heat absorption HG dehumidification heating mode, as described in steps S30 and S40 of the first embodiment, when it is determined that cooling of the supply air through the indoor evaporator 18 is not required, (4-1) the outside air heat absorption heating mode is selected.

[0550] Next, selection of the operation mode when the currently selected operation mode is (4-1) the outdoor air heat absorption heating mode will be described.

[0551] When the currently selected operation mode is (4-1) the outdoor air heat absorption heating mode, as described in steps S30 and S40 of the first embodiment, when it is determined that the supply air needs to be cooled by the indoor evaporator 18, the (3-2) outdoor air heat absorption HG dehumidification heating mode is selected.

[0552] Furthermore, when the currently selected operation mode is (4-1) the outdoor air heat absorption heating mode, if it is determined that the heating capacity of the supply air is insufficient, (4-2) the HG heating mode is selected.

[0553] Specifically, during the execution of the (4-1) outdoor air heat absorption heating mode, when the refrigerant discharge capacity (specifically, the rotation speed) of the compressor 11 is greater than the reference value and the supply air temperature TAV is less than the value obtained by subtracting the insufficient determination reference value KTA1 from the target outlet temperature TAO, it is determined that the heating capacity of the supply air is insufficient. Then, the (4-2) HG heating mode is selected.

[0554] As the reference value (specifically, reference rotation speed) of the compressor 11 , a maximum rotation speed determined by the durability of the compressor 11 or the like may be adopted.

[0555] Next, when the currently selected operation mode is (4-2) the HG heating mode, as described in step S240 of the first embodiment, when the target outlet temperature TAO is lower than the hot air reference temperature δ, (4-1) the outdoor air heat absorption heating mode is selected.

[0556] The control method related to the switching of other operation modes is the same as that of the first embodiment. Fig.31 , Fig.32 In the embodiment, regarding the control method related to the switching of the operation mode, the same parts as those of the first embodiment are indicated by dotted arrows. In addition, the structure and operation of the other parts of the vehicle air conditioner 1 are the same as those of the first embodiment.

[0557] In the vehicle air conditioning device 1 of the present embodiment, the operation mode is switched by detecting the heating capacity and the defrosting capacity of the blown air, so that more comfortable air conditioning of the vehicle interior can be achieved.

[0558] Specifically, during the execution of the series dehumidification and heating mode, when the supply air temperature TAV becomes less than the value obtained by subtracting the insufficient judgment reference value KTA1 from the target outlet temperature TAO, the mode is switched to the HG dehumidification and heating mode. In other words, at least when the supply air temperature TAV is lower than the target outlet temperature TAO, the mode is switched from the series dehumidification and heating mode to the HG dehumidification and heating mode.

[0559] This makes it possible to reliably detect that the heating capacity of the supply air is insufficient during execution of the tandem dehumidification and heating mode, and switch to the HG dehumidification and heating mode in which the heating capacity of the supply air is higher than that of the tandem dehumidification and heating mode.

[0560] In addition, during the execution of the HG dehumidification and heating mode, when the evaporator temperature Tefin becomes equal to or higher than the value obtained by adding the dehumidification determination reference value KTE to the target evaporator temperature TEO, the mode is switched to the series dehumidification and heating mode. In other words, at least when the evaporator temperature Tefin is higher than the target evaporator temperature TEO, the mode is switched from the HG dehumidification and heating mode to the series dehumidification and heating mode.

[0561] This makes it possible to reliably detect that the dehumidification capacity of the supply air is insufficient during the execution of the HG dehumidification and heating mode, and switch to the series dehumidification and heating mode in which the dehumidification capacity of the supply air is higher than that of the HG dehumidification and heating mode.

[0562] In addition, during the execution of the outdoor air heat absorption HG dehumidification heating mode, when the evaporator temperature Tefin becomes equal to or higher than the value obtained by adding the dehumidification determination reference value KTE to the target evaporator temperature TEO, the mode is switched to the HG dehumidification heating mode. In other words, at least when the evaporator temperature Tefin is higher than the target evaporator temperature TEO, the mode is switched from the outdoor air heat absorption HG dehumidification heating mode to the HG dehumidification heating mode.

[0563] This makes it possible to reliably detect that the dehumidification capacity of the supply air is insufficient during the execution of the outdoor air heat absorption HG dehumidification heating mode, and switch to the HG dehumidification heating mode in which the dehumidification capacity of the supply air is higher than that of the outdoor air heat absorption HG dehumidification heating mode.

[0564] In addition, during the execution of the outdoor air absorption heating mode, when the supply air temperature TAV becomes less than the value obtained by subtracting the insufficient judgment reference value KTA1 from the target outlet temperature TAO, the mode is switched to the HG heating mode. In other words, at least when the supply air temperature TAV is lower than the target outlet temperature TAO, the mode is switched from the outdoor air absorption heating mode to the HG heating mode.

[0565] This makes it possible to reliably detect that the heating capacity of the supply air is insufficient during the execution of the outdoor air heat absorption heating mode, and switch to the HG heating mode in which the dehumidification capacity of the supply air is higher than that in the outdoor air heat absorption heating mode.

[0566] In addition, the control method for switching from (1) the single cooling mode to (2) the series dehumidification and heating mode described in this embodiment can also be applied to switching from (5) the cooling and cooling mode to (6) the cooling and series dehumidification and heating mode. In addition, the control method for switching from (2) the series dehumidification and heating mode to (1) the single cooling mode can also be applied to switching from (6) the cooling and series dehumidification and heating mode to (5) the cooling and cooling mode.

[0567] In addition, the control method for switching from the (2) series dehumidification and heating mode to the (3-1) HG dehumidification and heating mode described in this embodiment can also be applied to switching from the (6) cooling series dehumidification and heating mode to the (7-1) cooling HG dehumidification and heating mode. The control method for switching from the (3-1) HG dehumidification and heating mode to the (2) series dehumidification and heating mode can also be applied to switching from the (7-1) cooling HG dehumidification and heating mode to the (6) cooling series dehumidification and heating mode.

[0568] In addition, the control method described in this embodiment when switching from (3-1) HG dehumidification and heating mode to (3-2) outside air heat absorption HG dehumidification and heating mode can also be applied when switching from (7-1) cooling HG dehumidification and heating mode to (7-2) cooling outside air heat absorption HG dehumidification and heating mode.

[0569] (Third Embodiment)

[0570] In this embodiment, the refrigeration cycle device involved in the present disclosure is applied to Fig.33 The vehicle air conditioning device 1a is described below with reference to an example of a vehicle air conditioning device 1a shown in the overall structure diagram. The vehicle air conditioning device 1a includes a heat pump cycle 10a. Fig.33 In order to clarify the illustration, the illustration of the sensor group for control is omitted.

[0571] In the heat pump cycle 10a, the accumulator 23 and the like are eliminated and the receiver 24 and the like are adopted in comparison with the heat pump cycle 10 described in the first embodiment.

[0572] In the heat pump cycle 10a, the other outlet of the second three-way joint 12b is connected to the inlet side of the accumulator 24. The refrigerant passage from the other outlet of the second three-way joint 12b to the inlet of the accumulator 24 is the inlet side passage 21d. The first inlet side on-off valve 22c and the fourth three-way joint 12d are arranged in the inlet side passage 21d.

[0573] The accumulator 24 is a high-pressure gas-liquid separator that separates the gas and liquid of the refrigerant flowing into the accumulator and stores the separated liquid-phase refrigerant as circulating excess refrigerant. The accumulator 24 allows a part of the separated liquid-phase refrigerant to flow out from the liquid-phase refrigerant outlet to the downstream side.

[0574] The first inlet-side on-off valve 22c is an on-off valve that opens and closes the inlet-side passage 21d. More specifically, the first inlet-side on-off valve 22c opens and closes the refrigerant passage in the inlet-side passage 21d from the other outlet of the second three-way joint 12b to the one inlet of the seventh three-way joint 12g. The first inlet-side on-off valve 22c is a refrigerant circuit switching unit.

[0575] In addition, the outflow port of one side of the second three-way joint 12b is connected to the inflow port side of one side of the ninth three-way joint 12i. A second inlet-side opening and closing valve 22d is arranged in the refrigerant passage from the outflow port of one side of the second three-way joint 12b to the inflow port of one side of the ninth three-way joint 12i. The second inlet-side opening and closing valve 22d opens and closes the refrigerant passage from the outflow port of one side of the second three-way joint 12b to the inflow port of one side of the eighth three-way joint 12h. The second inlet-side opening and closing valve 22d is a refrigerant circuit switching unit.

[0576] The basic structures of the first inlet-side on-off valve 22 c and the second inlet-side on-off valve 22 d are the same as those of the high-pressure-side on-off valve 22 a described in the first embodiment.

[0577] The liquid phase refrigerant outlet of the accumulator 24 is connected to the other inlet side of the ninth three-way joint 12i. The refrigerant passage from the outlet of the accumulator 24 to the other inlet of the ninth three-way joint 12i is the outlet side passage 21e. The thirteenth joint 12j and the fourth check valve 16d are arranged in the outlet side passage 21e.

[0578] The fourth check valve 16d allows the refrigerant to flow from the thirteenth joint 12j side to the ninth three-way joint 12i side, and prohibits the refrigerant from flowing from the ninth three-way joint 12i side to the thirteenth joint 12j side. The other outlet of the thirteenth joint 12j is connected to the inlet side of the fifth three-way joint 12e. The other structures of the vehicle air conditioner 1a are the same as those of the vehicle air conditioner 1 described in the first embodiment.

[0579] Next, the operation of the vehicle air conditioning device 1a of the present embodiment having the above structure will be described. In the vehicle air conditioning device 1a of the present embodiment, in order to perform air conditioning in the vehicle interior and temperature adjustment of the battery 70, various operation modes can be switched in the same manner as in the first embodiment. The detailed operation of each operation mode will be described below.

[0580] (1) Single cooling mode

[0581] In the heat pump cycle 10a in the single cooling mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is fully open, the cooling expansion valve 14b is throttling, the cooling expansion valve 14c is fully closed, and the bypass side flow regulating valve 14d is fully closed.

[0582] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , close the first inlet side on-off valve 22 c , and open the second inlet side on-off valve 22 d .

[0583] The control device 60 determines the operating state of the cooling expansion valve 14b so that the degree of superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference degree of superheat KSH (5°C in the present embodiment).

[0584] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0585] Therefore, in the heat pump cycle 10a in the single cooling mode, it is switched to the following refrigerant circuit: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a which is fully open, the outdoor heat exchanger 15, the accumulator 24, the cooling expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11.

[0586] Therefore, in the heat pump cycle 10a in the cooling-only mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers and the indoor evaporator 18 functions as an evaporator.

[0587] In addition, in the high temperature side heat medium circuit 40 in the cooling mode alone, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42, similarly to the first embodiment. In addition, in the indoor air conditioning unit 30 in the cooling mode alone, the temperature-adjusted air conditioning wind is blown into the vehicle interior, similarly to the first embodiment. Thus, the vehicle interior is cooled.

[0588] (2) Series dehumidification and heating mode

[0589] In the heat pump cycle 10a in the series dehumidification and heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a throttling state, the cooling expansion valve 14c is in a fully closed state, and the bypass side flow regulating valve 14d is in a fully closed state.

[0590] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , close the first inlet side on-off valve 22 c , and open the second inlet side on-off valve 22 d .

[0591] Furthermore, the control device 60 determines the operating states of the heating expansion valve 14a and the cooling expansion valve 14b so that the degree of superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference degree of superheat KSH.

[0592] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0593] Therefore, in the heat pump cycle 10a in the series dehumidification and heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the accumulator 24, the cooling expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11.

[0594] Therefore, in the heat pump cycle 10a in the series dehumidification and heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers and the indoor evaporator 18 functions as an evaporator.

[0595] In addition, in the high temperature side heat medium circuit 40 and the indoor air conditioning unit 30 in the series dehumidification and heating mode, the operations are performed in the same manner as in the cooling alone mode of the first embodiment.

[0596] In addition, in the high-temperature side heat medium circuit 40 in the series dehumidification and heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42, as in the first embodiment. In addition, in the indoor air conditioning unit 30 in the series dehumidification and heating mode, the air conditioning wind that has been dehumidified and temperature-adjusted is blown into the vehicle interior, as in the first embodiment. Thus, dehumidification and heating in the vehicle interior are achieved.

[0597] Here, the heat pump cycle 10a includes the accumulator 24. Therefore, the series dehumidification and heating mode is executed in a temperature range in which the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is higher than the outdoor air temperature Tam.

[0598] (3-1) HG dehumidification and heating mode

[0599] In the heat pump cycle 10a of the HG dehumidification heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a fully closed state, the cooling expansion valve 14b is in a throttling state, the cooling expansion valve 14c is in a throttling state, and the bypass side flow regulating valve 14d is in a throttling state.

[0600] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0601] The control device 60 determines the operating states of the compressor 11, the cooling expansion valve 14b, the cooling expansion valve 14c, and the bypass flow rate regulating valve 14d so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0602] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0603] Therefore, in the heat pump cycle 10a in the HG dehumidification heating mode, Fig.34 As shown by the solid arrows, the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the inlet-side passage 21d, the accumulator 24, the fifth three-way joint 12e, the cooling expansion valve 14b, the indoor evaporator 18, the sixth three-way joint 12f, the seventh three-way joint 12g, and the suction port of the compressor 11. Moreover, the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the inlet-side passage 21d, the accumulator 24, the fifth three-way joint 12e, the cooling expansion valve 14c, the chiller 20, the sixth three-way joint 12f, the seventh three-way joint 12g, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the bypass side flow control valve 14d arranged in the bypass passage 21c, the seventh three-way joint 12g, and the suction port of the compressor 11.

[0604] Therefore, in the heat pump cycle 10a in the HG dehumidification and heating mode, similarly to the first embodiment, the high temperature side heat medium is heated by the water refrigerant heat exchanger 13. Also, the supply air is cooled by the indoor evaporator 18.

[0605] Furthermore, in the high temperature side heat medium circuit 40 in the HG dehumidification and heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0606] In the low-temperature side heat medium circuit 50 in the HG dehumidification and heating mode, similarly to the first embodiment, the refrigerant and the low-temperature side heat medium do not exchange heat in the refrigerator 20 .

[0607] In the HG dehumidification and heating mode, the indoor air conditioning unit 30 blows the temperature-regulated air into the vehicle interior in the same manner as in the first embodiment, thereby achieving heating of the vehicle interior.

[0608] In the HG dehumidification and heating mode, similarly to the first embodiment, the heating capacity of the supply air in the heating unit can be improved compared to the series dehumidification and heating mode.

[0609] (3-2) External air heat absorption HG dehumidification heating mode

[0610] In the heat pump cycle 10a of the outdoor air heat absorption HG dehumidification heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in the throttling state, the cooling expansion valve 14b is in the throttling state, the cooling expansion valve 14c is in the throttling state, and the bypass side flow regulating valve 14d is in the throttling state.

[0611] In addition, the control device 60 determines the control voltages to be outputted so as to open the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0612] The control device 60 determines the operating states of the compressor 11, the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0613] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0614] Therefore, in the heat pump cycle 10a in the outdoor air heat absorption HG dehumidification heating mode, Fig.35 As shown by the solid arrows, the refrigerant discharged from the compressor 11 flows in the same manner as in the HG dehumidification and heating mode. Furthermore, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water refrigerant heat exchanger 13, the inlet side passage 21d, the accumulator 24, the outlet side passage 21e, the heating expansion valve 14a, the outdoor heat exchanger 15, the low-pressure side passage 21b, the eighth three-way joint 12h, and the suction port of the compressor 11.

[0615] Therefore, in the heat pump cycle 10a in the outdoor air heat absorption HG dehumidification heating mode, similarly to the first embodiment, the high temperature side heat medium is heated by the water refrigerant heat exchanger 13. In addition, the supply air is cooled by the indoor evaporator 18. In addition, in the outdoor heat exchanger 15, the refrigerant absorbs heat from the outdoor air.

[0616] In the high temperature side heat medium circuit 40 in the outdoor air heat absorption HG dehumidification and heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0617] In the low-temperature side heat medium circuit 50 in the outdoor air heat absorption HG dehumidification and heating mode, similarly to the first embodiment, in the refrigerator 20, the refrigerant and the low-temperature side heat medium do not exchange heat.

[0618] In the indoor air conditioning unit 30 in the outdoor air heat absorption HG dehumidification and heating mode, the temperature-regulated conditioned air is blown into the vehicle interior in the same manner as in the first embodiment. Thus, heating of the vehicle interior is achieved.

[0619] In the outdoor air heat absorption HG dehumidification and heating mode, as in the first embodiment, the heating capacity of the supply air in the heating unit can be improved compared to the series dehumidification and heating mode. In addition, in the outdoor air heat absorption HG dehumidification and heating mode, as in the first embodiment, the operation efficiency of the heat pump cycle 10a can be improved compared to the HG dehumidification and heating mode.

[0620] (4-1) External air absorption heating mode

[0621] In the heat pump cycle 10a of the outdoor air heat absorption heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a fully closed state, the cooling expansion valve 14c is in a fully closed state, and the bypass side flow regulating valve 14d is in a fully closed state.

[0622] In addition, the control device 60 determines the control voltages to be outputted so as to open the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0623] Furthermore, the control device 60 determines the operating state of the heating expansion valve 14a so that the degree of superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference degree of superheat KSH.

[0624] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0625] Therefore, in the heat pump cycle 10a of the outdoor air heat absorption heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the inlet side passage 21d, the accumulator 24, the outlet side passage 21e, the heating expansion valve 14a, the outdoor heat exchanger 15, the low-pressure side passage 21b, and the suction port of the compressor 11.

[0626] Therefore, in the heat pump cycle 10a in the outdoor air heat absorption heating mode, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 13 functions as a condenser and the outdoor heat exchanger 15 functions as an evaporator.

[0627] In addition, in the high-temperature side heat medium circuit 40 in the outdoor air heat absorption heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42, similarly to the first embodiment. In addition, in the indoor air conditioning unit 30 in the outdoor air heat absorption heating mode, the air-conditioned wind after temperature adjustment is blown into the vehicle interior, similarly to the first embodiment. Thus, heating of the vehicle interior is achieved.

[0628] (4-2) HG heating mode

[0629] In the heat pump cycle 10a of the outdoor air heat absorption heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a fully closed state, the cooling expansion valve 14b is in a fully closed state, the cooling expansion valve 14c is in a throttling state, and the bypass side flow regulating valve 14d is in a throttling state.

[0630] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0631] The control device 60 determines the operating states of the compressor 11, the cooling expansion valve 14c, and the bypass flow rate regulating valve 14d so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0632] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0633] Therefore, in the heat pump cycle 10a in the HG heating mode, Fig.36 As shown by the solid arrows, the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the inlet side passage 21d, the accumulator 24, the cooling expansion valve 14c, the chiller 20, the seventh three-way joint 12g, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the bypass side flow control valve 14d arranged in the bypass passage 21c, the seventh three-way joint 12g, and the suction port of the compressor 11.

[0634] Therefore, in the heat pump cycle 10 a in the HG dehumidification and heating mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 13 similarly to the first embodiment.

[0635] Furthermore, in the high temperature side heat medium circuit 40 in the HG heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0636] In the low-temperature side heat medium circuit 50 in the HG heating mode, similarly to the first embodiment, the refrigerant and the low-temperature side heat medium do not exchange heat in the refrigerator 20 .

[0637] In the HG heating mode, the indoor air conditioning unit 30 blows the temperature-regulated air into the vehicle interior in the same manner as in the first embodiment, thereby heating the vehicle interior.

[0638] In the HG heating mode, similarly to the first embodiment, the heating capacity of the supply air in the heating unit can be improved compared to the outdoor air heat absorption heating mode.

[0639] (5) Cooling mode

[0640] In the heat pump cycle 10a in the cooling mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is fully open, the cooling expansion valve 14b is throttling, the cooling expansion valve 14c is throttling, and the bypass side flow regulating valve 14d is fully closed.

[0641] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , close the first inlet side on-off valve 22 c , and open the second inlet side on-off valve 22 d .

[0642] Furthermore, the control device 60 determines the operating states of the cooling expansion valve 14b and the cooling expansion valve 14c so that the degree of superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference degree of superheat KSH.

[0643] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0644] Therefore, in the heat pump cycle 10a in the cooling and refrigeration mode, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a which is in a fully opened state, the outdoor heat exchanger 15, the accumulator 24, the fifth three-way joint 12e, the cooling expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a which is in a fully opened state, the outdoor heat exchanger 15, the accumulator 24, the fifth three-way joint 12e, the cooling expansion valve 14c, the chiller 20, and the suction port of the compressor 11.

[0645] That is, the refrigerant circuit is switched to a refrigerant circuit in which the indoor evaporator 18 and the cooling machine 20 are connected in parallel with respect to the flow of the refrigerant flowing out of the accumulator 24 .

[0646] Therefore, in the heat pump cycle 10a in the cooling mode, a vapor compression refrigeration cycle is constructed in which the water refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers and the indoor evaporator 18 and the refrigerator 20 function as evaporators.

[0647] Furthermore, in the high temperature side heat medium circuit 40 in the cooling mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0648] In the low-temperature side heat medium circuit 50 in the cooling and refrigeration mode, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. Thus, the battery 70 is cooled.

[0649] In the interior air conditioning unit 30 in the cooling mode, the temperature-regulated air is blown into the vehicle interior in the same manner as in the first embodiment, thereby heating the vehicle interior.

[0650] (6) Cooling series dehumidification and heating mode

[0651] In the heat pump cycle 10a of the cooling series dehumidification heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a throttling state, the cooling expansion valve 14c is in a throttling state, and the bypass side flow regulating valve 14d is in a fully closed state.

[0652] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , close the first inlet side on-off valve 22 c , and open the second inlet side on-off valve 22 d .

[0653] The control device 60 determines the operating states of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0654] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0655] Therefore, in the heat pump cycle 10a of the cooling series dehumidification heating mode, the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the accumulator 24, the fifth three-way joint 12e, the cooling expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the accumulator 24, the fifth three-way joint 12e, the cooling expansion valve 14c, the chiller 20, and the suction port of the compressor 11.

[0656] That is, the refrigerant circuit is switched to a refrigerant circuit in which the indoor evaporator 18 and the cooling machine 20 are connected in parallel with respect to the flow of the refrigerant flowing out of the accumulator 24 .

[0657] Therefore, in the heat pump cycle 10a in the cooling series dehumidification heating mode, a vapor compression refrigeration cycle is constructed in which the water refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers and the indoor evaporator 18 and the refrigerator 20 function as evaporators.

[0658] Furthermore, in the high temperature side heat medium circuit 40 in the cooling series dehumidification heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0659] In the low-temperature side heat medium circuit 50 in the cooling series dehumidification heating mode, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. Thus, the battery 70 is cooled.

[0660] In the indoor air conditioning unit 30 in the cooling series dehumidification and heating mode, similarly to the first embodiment, the conditioned air that has been dehumidified and temperature-controlled is blown into the vehicle interior, thereby achieving dehumidification and heating in the vehicle interior.

[0661] Here, the heat pump cycle 10a includes the accumulator 24. Therefore, the cooling series dehumidification and heating mode is executed in the temperature range where the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is higher than the outdoor air temperature Tam, similarly to the series dehumidification and heating mode.

[0662] (7-1) Cooling HG Dehumidification Heating Mode

[0663] In the heat pump cycle 10a of the cooling HG dehumidification heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a fully closed state, the cooling expansion valve 14b is in a throttling state, the cooling expansion valve 14c is in a throttling state, and the bypass side flow regulating valve 14d is in a throttling state.

[0664] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0665] The control device 60 determines the operating states of the compressor 11, the cooling expansion valve 14b, the cooling expansion valve 14c, and the bypass flow rate regulating valve 14d so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0666] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0667] Therefore, in the heat pump cycle 10a in the cooling HG dehumidification heating mode, Fig.34 As shown by the solid arrows in , the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates in the same order as in the HG dehumidification and heating mode.

[0668] Therefore, in the heat pump cycle 10a in the cooling HG dehumidification heating mode, similarly to the first embodiment, the high temperature side heat medium is heated by the water refrigerant heat exchanger 13. Also, the supply air is cooled by the indoor evaporator 18. Also, the low temperature side heat medium is cooled by the chiller 20.

[0669] Furthermore, in the high temperature side heat medium circuit 40 in the cooling HG dehumidification heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0670] In addition, in the low temperature side heat medium circuit 50 in the cooling HG dehumidification heating mode, as shown in FIG. Fig.34As shown by the dashed arrows, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. As a result, the battery 70 is cooled.

[0671] In the interior air conditioning unit 30 in the cooling HG dehumidification and heating mode, similarly to the first embodiment, the conditioned air that has been dehumidified and temperature-controlled is blown into the vehicle interior, thereby achieving dehumidification and heating in the vehicle interior.

[0672] In the cooling HG dehumidification and heating mode, similarly to the first embodiment, the heating capacity of the supply air in the heating unit can be improved compared to the cooling cascade dehumidification and heating mode.

[0673] (7-2) Cooling the outside air to absorb heat HG dehumidification and heating mode

[0674] In the heat pump cycle 10a of the cooling outside air heat absorption HG dehumidification heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in the throttling state, the cooling expansion valve 14b is in the throttling state, the cooling expansion valve 14c is in the throttling state, and the bypass side flow regulating valve 14d is in the throttling state.

[0675] In addition, the control device 60 determines the control voltages to be outputted so as to open the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0676] The control device 60 determines the operating states of the compressor 11, the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0677] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0678] Therefore, in the heat pump cycle 10a of the dehumidification heating mode of cooling the outside air and absorbing heat HG, Fig.35 As shown by the solid arrows, the refrigerant circuit is switched to the following one: the refrigerant discharged from the compressor 11 circulates in the same order as the outdoor air heat absorption HG dehumidification and heating mode.

[0679] Therefore, in the heat pump cycle 10a of the dehumidification heating mode of cooling the outside air and absorbing heat HG, the high-temperature side heat medium is heated by the water-refrigerant heat exchanger 13 as in the first embodiment. In addition, the supply air is cooled by the indoor evaporator 18. In addition, the low-temperature side heat medium is cooled by the chiller 20. In addition, in the outdoor heat exchanger 15, the refrigerant absorbs heat from the outside air.

[0680] In the high temperature side heat medium circuit 40 in the cooling outside air heat absorption HG dehumidification heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0681] In addition, in the low temperature side heat medium circuit 50 in the cooling outside air heat absorption HG dehumidification heating mode, as shown in FIG. Fig.35 As shown by the dashed arrows, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. As a result, the battery 70 is cooled.

[0682] In the interior air conditioning unit 30 in the cooling HG dehumidification and heating mode, similarly to the first embodiment, the conditioned air that has been dehumidified and temperature-controlled is blown into the vehicle interior, thereby achieving dehumidification and heating in the vehicle interior.

[0683] In the cooling outside air heat absorption HG heating mode, as in the first embodiment, the heating capacity of the supply air in the heating unit can be improved compared to the cooling series dehumidification heating mode. Also, in the cooling outside air heat absorption HG heating mode, as in the first embodiment, the operation efficiency of the heat pump cycle 10a can be improved compared to the cooling HG dehumidification heating mode.

[0684] (8) Cooling equipment heat absorption heating mode

[0685] In the heat pump cycle 10a of the cooling device heat absorption heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is fully open, the cooling expansion valve 14b is fully closed, the cooling expansion valve 14c is throttling, and the bypass side flow regulating valve 14d is fully closed.

[0686] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , close the first inlet side on-off valve 22 c , and open the second inlet side on-off valve 22 d .

[0687] Furthermore, the control device 60 determines the operating state of the cooling expansion valve 14c so that the degree of superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference degree of superheat KSH.

[0688] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0689] Therefore, in the heat pump cycle 10a of the cooling device heat absorption heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the fully opened heating expansion valve 14a, the outdoor heat exchanger 15, the accumulator 24, the cooling expansion valve 14c, the cold machine 20, and the suction port of the compressor 11.

[0690] Therefore, in the heat pump cycle 10a in the cooling device heat absorption heating mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 13 as in the first embodiment. In addition, the refrigerant dissipates heat to the outside air in the outdoor heat exchanger 15. In addition, the low temperature side heat medium is cooled by the chiller 20.

[0691] Furthermore, in the high temperature side heat medium circuit 40 in the cooling device heat absorption heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0692] In the low-temperature side heat medium circuit 50 in the cooling device heat absorption heating mode, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. Thus, the battery 70 is cooled.

[0693] In the interior air conditioning unit 30 in the cooling device heat absorption heating mode, the temperature-regulated air conditioning wind is blown into the vehicle interior in the same manner as in the first embodiment. Thus, heating of the vehicle interior is achieved.

[0694] (9) Cooling external air heat absorption heating mode

[0695] In the heat pump cycle 10a of the cooling outside air heat absorption heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a fully closed state, the cooling expansion valve 14c is in a throttling state, and the bypass side flow regulating valve 14d is in a fully closed state.

[0696] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , close the first inlet side on-off valve 22 c , and open the second inlet side on-off valve 22 d .

[0697] Furthermore, the control device 60 determines the operating states of the heating expansion valve 14a and the cooling expansion valve 14c so that the degree of superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference degree of superheat KSH.

[0698] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0699] Therefore, in the heat pump cycle 10a of the cooling outdoor air heat absorption heating mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a, the outdoor heat exchanger 15, the accumulator 24, the cooling expansion valve 14c, the cold machine 20, and the suction port of the compressor 11.

[0700] Therefore, in the heat pump cycle 10a in the cooling outdoor air heat absorption heating mode, the high temperature side heat medium is heated by the water refrigerant heat exchanger 13 as in the first embodiment. In addition, the refrigerant dissipates heat to the outdoor air in the outdoor heat exchanger 15. In addition, the low temperature side heat medium is cooled by the chiller 20.

[0701] Furthermore, in the high-temperature side heat medium circuit 40 in the cooling outdoor air heat absorption heating mode, similarly to the first embodiment, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0702] In the low-temperature side heat medium circuit 50 in the cooling outside air heat absorption heating mode, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. Thus, the battery 70 is cooled.

[0703] In the indoor air conditioning unit 30 in the cooling outside air heat absorption heating mode, the temperature-regulated conditioned air is blown into the vehicle interior in the same manner as in the first embodiment. Thus, heating of the vehicle interior is achieved.

[0704] Here, the heat pump cycle 10a includes the accumulator 24. Therefore, the cooling device heat absorption heating mode is executed in a temperature range where the saturation temperature of the refrigerant in the outdoor heat exchanger 15 is higher than the outdoor air temperature Tam, similarly to the series dehumidification heating mode.

[0705] (10-1) Cooling HG Heating Mode

[0706] In the heat pump cycle 10a of the cooling HG heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a fully closed state, the cooling expansion valve 14b is in a fully closed state, the cooling expansion valve 14c is in a throttling state, and the bypass side flow regulating valve 14d is in a throttling state.

[0707] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0708] The control device 60 determines the operating states of the compressor 11, the cooling expansion valve 14c, and the bypass flow rate regulating valve 14d so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0709] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0710] Therefore, in the heat pump cycle 10a in the cooling HG heating mode, as Fig.36 As shown by the solid arrows in , the refrigerant circuit is switched to one in which the refrigerant discharged from the compressor 11 circulates in the same order as in the HG heating mode.

[0711] Therefore, in the heat pump cycle 10a in the cooling HG heating mode, the high-temperature side heat medium is heated by the water-refrigerant heat exchanger 13 as in the first embodiment. Also, the low-temperature side heat medium is cooled by the chiller 20.

[0712] Furthermore, in the high temperature side heat medium circuit 40 in the cooling HG heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0713] In addition, in the low temperature side heat medium circuit 50 in the cooling HG heating mode, as shown in FIG. Fig.36 As shown by the dashed arrows, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. As a result, the battery 70 is cooled.

[0714] In the interior air conditioning unit 30 in the cooling HG heating mode, the temperature-regulated air is blown into the vehicle interior in the same manner as in the first embodiment. Thus, heating of the vehicle interior is achieved.

[0715] In the HG heating mode, similarly to the first embodiment, while cooling the battery 70 , the heating capacity of the supply air in the heating unit can be improved compared to the cooling outside air heat absorption heating mode.

[0716] (10-2) Cooling the outside air and absorbing heat HG heating mode

[0717] In the heat pump cycle 10a of the cooling outside air heat absorption HG heating mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is in a throttling state, the cooling expansion valve 14b is in a fully closed state, the cooling expansion valve 14c is in a throttling state, and the bypass side flow regulating valve 14d is in a throttling state.

[0718] In addition, the control device 60 determines the control voltages to be outputted so as to open the low-pressure side on-off valve 22 b , open the first inlet side on-off valve 22 c , and close the second inlet side on-off valve 22 d .

[0719] The control device 60 determines the operating states of the compressor 11, the heating expansion valve 14a, the cooling expansion valve 14c, and the bypass flow rate regulating valve 14d so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference superheat KSH.

[0720] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0721] Therefore, in the heat pump cycle 10a in the heating mode of cooling the outside air and absorbing heat HG, Fig.37 As shown by the solid arrows, the refrigerant discharged from the compressor 11 flows in the same manner as in the cooling HG heating mode. At the same time, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the first three-way joint 12a, the water-refrigerant heat exchanger 13, the inlet side passage 21d, the accumulator 24, the outlet side passage 21e, the heating expansion valve 14a, the outdoor heat exchanger 15, the low-pressure side passage 21b, the eighth three-way joint 12h, and the suction port of the compressor 11.

[0722] Therefore, in the heat pump cycle 10a in the HG heating mode of cooling the outside air and absorbing heat, the high-temperature side heat medium is heated by the water-refrigerant heat exchanger 13 as in the first embodiment. In addition, the low-temperature side heat medium is cooled by the chiller 20. In addition, in the outdoor heat exchanger 15, the refrigerant absorbs heat from the outside air.

[0723] Furthermore, in the high temperature side heat medium circuit 40 in the cooling outside air heat absorption HG heating mode, similarly to the first embodiment, the high temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 42 .

[0724] In addition, in the low temperature side heat medium circuit 50 in the cooling outside air heat absorption HG heating mode, as shown in FIG. Fig.37 As shown by the dashed arrows, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. As a result, the battery 70 is cooled.

[0725] In the indoor air conditioning unit 30 in the cooling outside air heat absorption HG heating mode, the temperature-regulated conditioned air is blown into the vehicle interior in the same manner as in the first embodiment. Thus, heating of the vehicle interior is achieved.

[0726] In the cooling outside air heat absorption HG heating mode, while cooling the battery 70 as in the cooling outside air heat absorption HG heating mode, the heating capacity of the supply air in the heating unit can be improved compared to the cooling outside air heat absorption heating mode.

[0727] Furthermore, in the cooling outside air heat absorption HG heating mode, the supply air can be heated using the heat absorbed from the outside air by the refrigerant in the outdoor heat exchanger 15. Therefore, in the cooling outside air heat absorption HG heating mode, the operating efficiency of the heat pump cycle 10 can be improved compared to the cooling HG heating mode.

[0728] (11) Cooling mode

[0729] In the heat pump cycle 10a in the cooling mode, the control device 60 determines the control signals to be output respectively so that the heating expansion valve 14a is fully open, the cooling expansion valve 14b is fully closed, the cooling expansion valve 14c is throttling, and the bypass side flow control valve 14d is fully closed.

[0730] In addition, the control device 60 determines the control voltages to be outputted so as to close the low-pressure side on-off valve 22 b , close the first inlet side on-off valve 22 c , and open the second inlet side on-off valve 22 d .

[0731] Furthermore, the control device 60 determines the operating state of the cooling expansion valve 14c so that the degree of superheat SH of the refrigerant sucked into the compressor 11 approaches a preset reference degree of superheat KSH.

[0732] Moreover, the control device 60 appropriately determines the operation state of other control target devices similarly to the first embodiment. Furthermore, the control device 60 outputs a control signal or a control voltage to various control target devices so as to obtain the determined control state.

[0733] Therefore, in the heat pump cycle 10a in the cooling mode, the refrigerant circuit is switched to the following: the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 13, the fully opened heating expansion valve 14a, the outdoor heat exchanger 15, the accumulator 24, the cooling expansion valve 14c, the cold machine 20, and the suction port of the compressor 11.

[0734] Therefore, in the heat pump cycle 10a in the cooling mode, similarly to the first embodiment, the heat of the refrigerant is dissipated to the outside air in the outdoor heat exchanger 15. In addition, the low-temperature side heat medium is cooled by the chiller 20.

[0735] In the low-temperature side heat medium circuit 50 in the cooling mode, similarly to the first embodiment, the low-temperature side heat medium flows through the cooling water passage 70a of the battery 70. Thus, the battery 70 is cooled.

[0736] (12) Air supply mode

[0737] In the air supply mode, the control device 60 stops the compressor 11. In addition, the control device 60 operates the indoor air-sending device 32 based on a setting signal set by the air volume setting switch.

[0738] In the indoor air conditioning unit 30 in the air-sending mode, the air sent from the indoor air-sending fan 32 is blown into the room.

[0739] As described above, in the vehicle air conditioning device 1 a of the present embodiment, by switching between various operation modes, it is possible to realize comfortable air conditioning in the vehicle interior while appropriately adjusting the temperature of the battery 70 .

[0740] Moreover, in the vehicle air conditioning device 1a of this embodiment, the same effect as the vehicle air conditioning device 1 of the first embodiment can be obtained. That is, when dehumidifying and heating the vehicle interior, by switching between the series dehumidification and heating mode and the HG dehumidification and heating mode, the decrease in the operating efficiency can be suppressed, and the temperature of the supply air can be continuously adjusted within a wider range.

[0741] Furthermore, when performing dehumidification and heating in the vehicle interior, by switching between the cooling series dehumidification and heating mode and the cooling HG dehumidification and heating mode, it is possible to suppress the decrease in operating efficiency while cooling the battery 70 and to continuously adjust the temperature of the supply air within a wider range.

[0742] Furthermore, when heating the vehicle interior, by switching between the outdoor air heat absorption heating mode and the HG heating mode, it is possible to suppress a decrease in operating efficiency and to continuously adjust the temperature of the supply air within a wide range.

[0743] Furthermore, when heating the vehicle interior, by switching between the cooled outside air heat absorption heating mode and the cooled HG heating mode, the temperature of the supply air can be continuously adjusted within a wide range while cooling the battery 70 while suppressing a decrease in operating efficiency.

[0744] The present disclosure is not limited to the above-described embodiments, and various modifications as described below are possible without departing from the gist of the present disclosure.

[0745] In the above-mentioned embodiment, an example of applying the refrigeration cycle device of the present disclosure to the vehicle air conditioning device 1, 1a is described, but the application of the refrigeration cycle device involved in the present disclosure is not limited to vehicle use. For example, it can also be applied to a fixed air conditioning device with a temperature control function that adjusts the temperature of a cooling object (such as a computer, a server device, or other peripheral equipment) while performing indoor air conditioning.

[0746] In addition, in the above-mentioned embodiment, the refrigeration cycle device of the present disclosure is applied to an air conditioning device with a vehicle-mounted device temperature adjustment function, and an example is described in which the temperature of the battery 70 as the vehicle-mounted device is adjusted, but the vehicle-mounted device is not limited to the battery 70. For example, the temperature of an inverter, a PCU, a transmission shaft, a control device for ADAS, etc. may also be adjusted. Furthermore, the temperature of multiple vehicle-mounted devices may also be adjusted.

[0747] The inverter supplies power to the motor generator, etc. The PCU is a power control unit that performs power conversion and power distribution. The propeller shaft is a power transmission mechanism that integrates the transmission, differential gear, etc. The control device for ADAS is a control device for advanced driver assistance systems.

[0748] Of course, the refrigeration cycle device according to the present disclosure may be applied to an air conditioning device that does not have a function of adjusting the temperature of a cooling object such as vehicle-mounted equipment and that performs air conditioning exclusively in an air-conditioned space.

[0749] The structure of the refrigeration cycle device according to the present disclosure is not limited to the structure disclosed in the above-mentioned embodiment.

[0750] In the above-described embodiment, an example in which the heating unit is formed by the components of the water-refrigerant heat exchanger 13 and the high-temperature-side heat medium circuit 40 has been described, but the heating unit is not limited to this.

[0751] For example, an indoor condenser may be used as the heating unit. The indoor condenser is a heat exchange unit for heating the supply air by exchanging heat between the exhaust refrigerant branched from the first three-way joint 12a and the supply air that has passed through the indoor evaporator 18. The indoor condenser may be arranged in the air passage of the indoor air conditioning unit 30 in the same manner as the heater core 42.

[0752] In the above-described embodiment, an example in which the cooling unit is formed by the components of the chiller 20 and the low-temperature-side heat medium circuit 50 has been described, but the cooling unit is not limited to this.

[0753] For example, as the cooling unit, a thermosyphon may be used in which the chiller 20 of the low-temperature side heat medium circuit 50 functions as a condensing unit and the cooling water passage 70a functions as an evaporating unit.

[0754] The thermosiphon has an evaporation part for evaporating the refrigerant and a condensation part for condensing the refrigerant, and is formed by connecting the evaporation part and the condensation part in a closed loop (i.e., annular). In addition, the temperature difference between the temperature of the refrigerant in the evaporation part and the temperature of the refrigerant in the condensation part causes a specific gravity difference in the refrigerant in the circuit, and the refrigerant circulates naturally by the action of gravity, thereby transporting heat together with the refrigerant.

[0755] For example, as the cooling unit, a cooling heat exchange unit may be used that directly exchanges heat between the low-pressure refrigerant circulating in the heat pump and the battery 70 without using a low-temperature side heat medium, so that the low-pressure refrigerant directly absorbs waste heat from the battery 70. For example, as the cooling unit, an air-cooling type cooling device that blows the supply air cooled by the cooling evaporator toward the battery 70 may be used.

[0756] In the above-described embodiment, an example is described in which the seventh three-way joint 12g and the eighth three-way joint 12h as the merging portion are arranged on the refrigerant flow downstream side of the sixth embodiment 12f, but the arrangement of the merging portion is not limited to this.

[0757] For example, the seventh three-way joint 12g may be arranged in the refrigerant passage from the outlet side of the cooling expansion valve 14c to the refrigerant inlet side of the cold machine 20. For example, the seventh three-way joint 12g may be arranged in the refrigerant passage from the refrigerant outlet side of the cold machine 20 to the inlet side of the sixth embodiment 12f. For example, in the heat pump cycle 10 of the first embodiment, the seventh three-way joint 12g may be abolished and the bypass passage 21c may be directly connected to the accumulator 23.

[0758] In the above embodiment, an example is described in which the confluence portion is formed by the seventh three-way joint 12g and the eighth three-way joint 12h. However, the confluence portion may be formed by a four-way joint in which the seventh three-way joint 12g and the eighth three-way joint 12h are integrated.

[0759] Similarly, in the heat pump cycle 10 of the first embodiment, the fourth three-way joint 12d and the fifth three-way joint 12e may be integrated into a four-way joint. In the heat pump cycle 10a of the second embodiment, the ninth three-way joint 12i and the fifth three-way joint 12e may be integrated into a four-way joint.

[0760] In addition, with respect to the heat pump cycle 10a of the second embodiment, a subcooling expansion valve may be arranged in the refrigerant passage from the outflow side of the fourth three-way joint 12d to the inlet side of the accumulator 24. The subcooling expansion valve decompresses the refrigerant flowing into the accumulator 24. As the subcooling expansion valve, a fixed throttle valve or a variable throttle mechanism may be used.

[0761] Thus, the degree of subcooling of the refrigerant flowing out of the water-refrigerant heat exchanger 13 can be increased, and the refrigerant pressure (i.e., the discharge refrigerant pressure Pd) in the water-refrigerant heat exchanger 13 can be increased. As a result, the heating capacity of the high-temperature side heat medium in the water-refrigerant heat exchanger 13 can be improved, and the heating capacity of the supply air can be improved.

[0762] In addition, in the above-mentioned embodiment, an example of using R1234yf as the refrigerant of the heat pump cycle 10, 10a is described, but it is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may also be used. Alternatively, a mixed refrigerant obtained by mixing a plurality of these refrigerants may also be used. In addition, carbon dioxide may also be used as the refrigerant to form a supercritical refrigeration cycle in which the refrigerant pressure on the high-pressure side is above the critical pressure of the refrigerant.

[0763] In the above embodiment, an example in which PAG oil (ie, polyalkylene glycol oil) is used as the refrigeration oil is described, but the present invention is not limited thereto. For example, POE (ie, polyol ester) or the like may be used.

[0764] In addition, in the above-mentioned embodiment, an example of using ethylene glycol aqueous solution as a heat medium, a low temperature side heat medium and a high temperature side heat medium is described, but it is not limited to this. For example, dimethyl polysiloxane or a solution containing nanofluids, antifreeze, a water-based liquid refrigerant containing alcohol, etc., a liquid medium containing oil, etc., etc. may also be used.

[0765] In addition, the control sensor group connected to the input side of the control device 60 is not limited to the detection unit disclosed in the above-mentioned embodiment, and various detection units may be added as needed.

[0766] In the above-mentioned embodiment, the vehicle air conditioning device 1, 1a which can switch between a plurality of operation modes is described, but the switching of the operation mode is not limited to this.

[0767] If at least (2) the series dehumidification and heating mode and (3-1) the HG dehumidification and heating mode can be switched, the temperature of the supply air can be adjusted continuously within a wide range while suppressing a decrease in operating efficiency when dehumidifying and heating the air-conditioned space.

[0768] If it is possible to switch at least between (6) the cooling series dehumidification and heating mode and (7-1) the cooling HG dehumidification and heating mode, then when dehumidifying and heating the air-conditioned space, it is possible to suppress the decrease in operating efficiency while cooling the battery 70 and continuously adjust the temperature of the supply air within a wider range.

[0769] If at least (4-1) the outdoor air heat absorption heating mode and (4-2) the HG heating mode can be switched, it is possible to suppress a decrease in operating efficiency when heating the air-conditioned space and to continuously adjust the temperature of the supply air within a wide range.

[0770] If it is possible to switch at least between (9) the cooling outside air heat absorption heating mode and (10-1) the cooling HG heating mode, it is possible to suppress the decrease in operating efficiency while cooling the battery 70 when heating the air-conditioned space, and to continuously adjust the temperature of the supply air within a wider range.

[0771] In the above embodiment, as described in step S140 and the like, an example is described in which the outdoor unit temperature difference ΔTO and the outlet temperature difference ΔTAO are used to determine whether the refrigerant can appropriately absorb the heat of the outdoor air in the outdoor heat exchanger 15, but the present invention is not limited to this.

[0772] For example, in order to determine whether it is possible to absorb heat from the outside air, the amount of heat absorbed by the refrigerant when the refrigerant is allowed to flow into the outdoor heat exchanger 15 may be predicted, and it may be determined whether the amount of heat absorbed is excessive relative to the target outlet temperature TAO. For example, in order to determine whether it is possible to absorb heat from the outside air, the flow rate (mass flow rate) of the refrigerant flowing through the outdoor heat exchanger 15 may be predicted when the refrigerant is allowed to flow into the outdoor heat exchanger 15, and it may be determined whether the refrigeration oil can be returned to the compressor 11.

[0773] The methods disclosed in the above-mentioned embodiments may be combined as appropriate within the scope of implementation. For example, the control method related to the switching of the operation mode described in the second embodiment may be applied to the vehicle air conditioning device 1 a described in the third embodiment.

[0774] The features of the refrigeration cycle device disclosed in this specification are as follows.

[0775] (Item 1)

[0776] A refrigeration cycle device, comprising:

[0777] A compressor (11) which compresses and discharges a refrigerant;

[0778] an upstream branching portion (12a) for branching the flow of the refrigerant discharged from the compressor;

[0779] a heating unit (13, 40) which uses the refrigerant flowing out of one outlet of the upstream branching unit as a heat source to heat the supply air blown to the air-conditioned space;

[0780] a heating portion side decompression portion (14a, 14b, 14c) for decompressing the refrigerant flowing out of the heating portion;

[0781] an outdoor heat exchange section (15) for exchanging heat between the refrigerant flowing out of the heating section side pressure reducing section and the outside air;

[0782] an indoor evaporation section (18) which evaporates the refrigerant after the refrigerant is decompressed by the decompression section on the heating section side and cools the supply air before the refrigerant is heated by the heating section;

[0783] a bypass passage (21c) for guiding the other refrigerant branched from the upstream branch portion to the suction port side of the compressor;

[0784] a bypass-side flow rate regulating unit (14d) for regulating the flow rate of the refrigerant flowing through the bypass passage;

[0785] a merging portion (12g, 12h) that merges the flow of the refrigerant flowing out of the heating portion-side pressure reducing portion with the flow of the refrigerant flowing out of the bypass-side flow regulating portion and flows out toward the suction port side of the compressor; and

[0786] A refrigerant circuit switching unit (22a, 22b, 22c, 22d) for switching the refrigerant circuit.

[0787] The heating section side pressure reducing section comprises an outdoor pressure reducing section (14a), an indoor pressure reducing section (14b) and a detour side pressure reducing section (14c), wherein the outdoor pressure reducing section depressurizes the refrigerant flowing into the outdoor heat exchange section, the indoor pressure reducing section depressurizes the refrigerant flowing into the indoor evaporation section, and the detour side pressure reducing section depressurizes the refrigerant flowing around the outdoor heat exchange section and the indoor evaporation section.

[0788] As the operation mode in which the heating unit reheats the supply air cooled by the indoor evaporation unit, there are a series dehumidification and heating mode and a hot air dehumidification and heating mode.

[0789] In the series dehumidification and heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the indoor pressure reducing unit, the indoor evaporation unit, and the suction port of the compressor.

[0790] In the hot air dehumidification heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the indoor pressure reducing portion, the indoor evaporation portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

[0791] (Item 2)

[0792] The refrigeration cycle device according to item 1, comprising:

[0793] a target outlet temperature determination unit (S20) for determining a target outlet temperature (TAO) of the supply air to be blown into the air-conditioning target space; and

[0794] a supply air temperature detection unit (66) for detecting a supply air temperature (TAV) of the supply air blown to the air-conditioning target space;

[0795] When the supply air temperature (TAV) is lower than the target outlet temperature (TAO), the refrigerant circuit switching unit switches from the series dehumidification and heating mode to the hot gas dehumidification and heating mode.

[0796] (Item 3)

[0797] The refrigeration cycle device according to item 1 or 2, comprising:

[0798] a target evaporator temperature determination unit (S1907) for determining a target evaporator temperature (TEO) of the indoor evaporation unit; and

[0799] an evaporator temperature detection unit (62f) for detecting an evaporator temperature (Tefin) of the indoor evaporation unit,

[0800] When the evaporator temperature (Tefin) is higher than the target evaporator temperature (TEO), the refrigerant circuit switching unit switches from the hot gas dehumidification and heating mode to the series dehumidification and heating mode.

[0801] (Item 4)

[0802] The refrigeration cycle device according to any one of items 1 to 3,

[0803] As an operation mode in which the heating unit reheats the supply air cooled by the indoor evaporation unit, there is also a hot air dehumidification and heating mode in which heat is absorbed by outdoor air.

[0804] In the outdoor air heat absorption hot air dehumidification heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the outdoor pressure reducing section, the outdoor heat exchange section, the confluence section, and the suction port of the compressor; the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the indoor pressure reducing section, the indoor evaporation section, the confluence section, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the detour side pressure reducing section, the confluence section, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the detour side pressure reducing section, the confluence section, and the suction port of the compressor.

[0805] (Item 5)

[0806] The refrigeration cycle device according to item 4, comprising:

[0807] a target evaporator temperature determination unit (S1907) for determining a target evaporator temperature (TEO) of the indoor evaporation unit; and

[0808] an outside air temperature detection unit (61b) for detecting an outside air temperature (Tam), which is the temperature of the outside air,

[0809] When the outdoor unit temperature difference (ΔTO) obtained by subtracting the target evaporator temperature (TEO) from the outdoor air temperature (Tam) is greater than a preset reference temperature difference (KΔTO1), the refrigerant circuit switching unit switches from the hot gas dehumidification and heating mode to the outdoor air heat absorption hot gas dehumidification and heating mode.

[0810] (Item 6)

[0811] The refrigeration cycle device according to item 4 or 5, comprising:

[0812] a target evaporator temperature determination unit (S1807) for determining a target evaporator temperature (TEO) of the indoor evaporation unit; and

[0813] an evaporator temperature detection unit (62f) for detecting an evaporator temperature (Tefin) of the indoor evaporation unit,

[0814] When the evaporator temperature (Tefin) is higher than the target evaporator temperature (TEO), the refrigerant circuit switching unit switches from the outdoor air heat absorbing hot gas dehumidification and heating mode to the hot gas dehumidification and heating mode.

[0815] (Item 7)

[0816] The refrigeration cycle device according to any one of items 1 to 6,

[0817] A cooling unit (20, 50) is provided, which cools a cooling object.

[0818] As operation modes in which the cooling unit cools the cooling object and the heating unit reheats the supply air cooled by the indoor evaporation unit, there are a cooling series dehumidification and heating mode and a cooling hot air dehumidification and heating mode.

[0819] In the cooling series dehumidification and heating mode, the refrigerant circuit switching unit is switched to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the indoor pressure reducing unit, the indoor evaporation unit, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the detour side pressure reducing unit, the cooling unit, and the suction port of the compressor,

[0820] In the cooling hot air dehumidification and heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the indoor pressure reducing portion, the indoor evaporation portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the cooling portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

[0821] (Item 8)

[0822] A refrigeration cycle device, comprising:

[0823] A compressor (11) which compresses and discharges a refrigerant;

[0824] an upstream branching portion (12a) for branching the flow of the refrigerant discharged from the compressor;

[0825] a heating unit (13, 40) which uses the refrigerant flowing out of one outlet of the upstream branching unit as a heat source to heat the supply air blown to the air-conditioned space;

[0826] a heating portion side decompression portion (14a, 14b, 14c) for decompressing the refrigerant flowing out of the heating portion;

[0827] an outdoor heat exchange section (15) for exchanging heat between the refrigerant flowing out of the heating section side pressure reducing section and the outside air;

[0828] a bypass passage (21c) for guiding the other refrigerant branched from the upstream branch portion to the suction port side of the compressor;

[0829] a bypass-side flow rate regulating unit (14d) for regulating the flow rate of the refrigerant flowing through the bypass passage;

[0830] a merging portion (12g, 12h) that merges the flow of the refrigerant flowing out of the heating portion-side pressure reducing portion with the flow of the refrigerant flowing out of the bypass-side flow regulating portion and flows out toward the suction port side of the compressor; and

[0831] A refrigerant circuit switching unit (22a, 22b, 22c, 22d) for switching the refrigerant circuit.

[0832] The heating section side pressure reducing section comprises an outdoor side pressure reducing section (14a) and a detour side pressure reducing section (14c), wherein the outdoor side pressure reducing section depressurizes the refrigerant flowing into the outdoor heat exchange section, and the detour side pressure reducing section depressurizes the refrigerant flowing around the outdoor heat exchange section.

[0833] As the operation mode in which the heating unit heats the supply air, there are an outdoor air heat absorption heating mode and a hot air heating mode.

[0834] In the outdoor air heat absorption heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, and the suction port of the compressor.

[0835] In the hot air heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit:

[0836] The refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

[0837] (Item 9)

[0838] The refrigeration cycle device according to item 8, comprising:

[0839] a target outlet temperature determination unit (S20) for determining a target outlet temperature (TAO) of the supply air to be blown into the air-conditioning target space; and

[0840] a supply air temperature detection unit (66) for detecting a supply air temperature (TAV) of the supply air blown to the air-conditioning target space;

[0841] When the supply air temperature (TAV) is lower than the target outlet temperature (TAO), the refrigerant circuit switching unit switches from the outdoor air heat absorption heating mode to the hot air heating mode.

[0842] (Item 10)

[0843] A refrigeration cycle apparatus according to item 8 or 9,

[0844] A target outlet temperature determination unit (S20) is provided, the target outlet temperature determination unit determining a target outlet temperature (TAO) of the supply air blown to the air conditioning target space,

[0845] When the target air outlet temperature (TAO) is lower than the hot air reference temperature (δ), the refrigerant circuit switching unit switches from the hot air heating mode to the outdoor air heat absorption heating mode.

[0846] (Item 11)

[0847] The refrigeration cycle device according to any one of items 8 to 10,

[0848] A cooling unit (20, 50) is provided, which cools a cooling object.

[0849] As an operation mode in which the cooling unit cools the cooling object and the heating unit heats the supply air, there are a cooling series dehumidification and heating mode and a cooling hot air dehumidification and heating mode, and the decompression unit on the bypass side decompresses the refrigerant flowing into the cooling unit.

[0850] As operation modes in which the cooling unit cools the cooling object and the heating unit heats the supply air, there are a cooling outside air heat absorption heating mode and a cooling hot air heating mode.

[0851] In the cooling outdoor air heat absorption heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor side pressure reducing unit, the outdoor heat exchange unit, the detour side pressure reducing unit, the cooling unit, and the suction port of the compressor.

[0852] In the cooling hot air heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the cooling portion, the confluence portion, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

[0853] The present disclosure is described according to the embodiments, but it should be understood that the present disclosure is not limited to the embodiments and structures. The present disclosure also includes various modifications and modifications within the equivalent range. In addition, various combinations and methods, even other combinations and methods including only one element among these, or including more than one element or less than multiple elements, are all within the scope and thought of the present disclosure.

Claims

1. A refrigeration cycle device, characterized in that: have: A compressor (11) which compresses and discharges a refrigerant; an upstream branching portion (12a) for branching the flow of the refrigerant discharged from the compressor; a heating unit (13, 40) which uses the refrigerant flowing out of one outlet of the upstream branching unit as a heat source to heat the supply air blown to the air-conditioned space; a heating portion side decompression portion (14a, 14b, 14c) for decompressing the refrigerant flowing out of the heating portion; an outdoor heat exchange section (15) for exchanging heat between the refrigerant flowing out of the heating section side pressure reducing section and the outside air; an indoor evaporation section (18) which evaporates the refrigerant after the refrigerant is decompressed by the decompression section on the heating section side and cools the supply air before the refrigerant is heated by the heating section; a bypass passage (21c) for guiding the other refrigerant branched from the upstream branch portion to the suction port side of the compressor; a bypass-side flow rate regulating unit (14d) for regulating the flow rate of the refrigerant flowing through the bypass passage; a merging portion (12g, 12h) that merges the flow of the refrigerant flowing out of the heating portion-side pressure reducing portion with the flow of the refrigerant flowing out of the bypass-side flow regulating portion and flows out toward the suction port side of the compressor; and A refrigerant circuit switching unit (22a, 22b, 22c, 22d) for switching the refrigerant circuit. The heating section side pressure reducing section comprises an outdoor pressure reducing section (14a), an indoor pressure reducing section (14b) and a detour side pressure reducing section (14c), wherein the outdoor pressure reducing section depressurizes the refrigerant flowing into the outdoor heat exchange section, the indoor pressure reducing section depressurizes the refrigerant flowing into the indoor evaporation section, and the detour side pressure reducing section depressurizes the refrigerant flowing around the outdoor heat exchange section and the indoor evaporation section. As the operation mode in which the heating unit reheats the supply air cooled by the indoor evaporation unit, there are a series dehumidification and heating mode and a hot air dehumidification and heating mode. In the series dehumidification and heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the indoor pressure reducing unit, the indoor evaporation unit, and the suction port of the compressor. In the hot air dehumidification heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the indoor pressure reducing portion, the indoor evaporation portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

2. The refrigeration cycle device according to claim 1, characterized in that: have: a target outlet temperature determination unit (S20) for determining a target outlet temperature (TAO) of the supply air to be blown into the air-conditioning target space; as well as a supply air temperature detection unit (66) for detecting a supply air temperature (TAV) of the supply air blown to the air-conditioning target space; When the supply air temperature (TAV) is lower than the target outlet temperature (TAO), the refrigerant circuit switching unit switches from the series dehumidification and heating mode to the hot gas dehumidification and heating mode.

3. The refrigeration cycle device according to claim 1, characterized in that: have: a target evaporator temperature determination unit (S1907) for determining a target evaporator temperature (TEO) of the indoor evaporation unit; and an evaporator temperature detection unit (62f) for detecting an evaporator temperature (Tefin) of the indoor evaporation unit, When the evaporator temperature (Tefin) is higher than the target evaporator temperature (TEO), the refrigerant circuit switching unit switches from the hot gas dehumidification and heating mode to the series dehumidification and heating mode.

4. The refrigeration cycle device according to claim 1, characterized in that: As an operation mode in which the heating unit reheats the supply air cooled by the indoor evaporation unit, there is also a hot air dehumidification and heating mode in which heat is absorbed by outdoor air. In the outdoor air heat absorption hot air dehumidification heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the outdoor pressure reducing section, the outdoor heat exchange section, the confluence section, and the suction port of the compressor; the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the indoor pressure reducing section, the indoor evaporation section, the confluence section, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the detour side pressure reducing section, the confluence section, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream branch section, the heating section, the detour side pressure reducing section, the confluence section, and the suction port of the compressor.

5. The refrigeration cycle device according to claim 4, characterized in that: have: a target evaporator temperature determination unit (S1907) for determining a target evaporator temperature (TEO) of the indoor evaporation unit; and an outside air temperature detection unit (61b) for detecting an outside air temperature (Tam), which is the temperature of the outside air, When the outdoor unit temperature difference (ΔTO) obtained by subtracting the target evaporator temperature (TEO) from the outdoor air temperature (Tam) is greater than a preset reference temperature difference (KΔTO1), the refrigerant circuit switching unit switches from the hot gas dehumidification and heating mode to the outdoor air heat absorption hot gas dehumidification and heating mode.

6. The refrigeration cycle device according to claim 4, characterized in that: have: a target evaporator temperature determination unit (S1807) for determining a target evaporator temperature (TEO) of the indoor evaporation unit; and an evaporator temperature detection unit (62f) for detecting an evaporator temperature (Tefin) of the indoor evaporation unit, When the evaporator temperature (Tefin) is higher than the target evaporator temperature (TEO), the refrigerant circuit switching unit switches from the outdoor air heat absorbing hot gas dehumidification and heating mode to the hot gas dehumidification and heating mode.

7. The refrigeration cycle device according to any one of claims 1 to 6, characterized in that: A cooling unit (20, 50) is provided, which cools a cooling object. As operation modes in which the cooling unit cools the cooling object and the heating unit reheats the supply air cooled by the indoor evaporation unit, there are a cooling series dehumidification and heating mode and a cooling hot air dehumidification and heating mode. In the cooling series dehumidification and heating mode, the refrigerant circuit switching unit is switched to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the indoor pressure reducing unit, the indoor evaporation unit, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the detour side pressure reducing unit, the cooling unit, and the suction port of the compressor, In the cooling hot air dehumidification and heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the indoor pressure reducing portion, the indoor evaporation portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the cooling portion, the confluence portion, and the suction port of the compressor, and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

8. A refrigeration cycle device, characterized in that: have: A compressor (11) which compresses and discharges a refrigerant; an upstream branching portion (12a) for branching the flow of the refrigerant discharged from the compressor; a heating unit (13, 40) which uses the refrigerant flowing out of one outlet of the upstream branching unit as a heat source to heat the supply air blown to the air-conditioned space; a heating portion side decompression portion (14a, 14b, 14c) for decompressing the refrigerant flowing out of the heating portion; an outdoor heat exchange section (15) for exchanging heat between the refrigerant flowing out of the heating section side pressure reducing section and the outside air; a bypass passage (21c) for guiding the other refrigerant branched from the upstream branch portion to the suction port side of the compressor; a bypass-side flow rate regulating unit (14d) for regulating the flow rate of the refrigerant flowing through the bypass passage; a merging portion (12g, 12h) that merges the flow of the refrigerant flowing out of the heating portion-side pressure reducing portion with the flow of the refrigerant flowing out of the bypass-side flow regulating portion and flows out toward the suction port side of the compressor; and A refrigerant circuit switching unit (22a, 22b, 22c, 22d) for switching the refrigerant circuit. The heating section side pressure reducing section comprises an outdoor side pressure reducing section (14a) and a detour side pressure reducing section (14c), wherein the outdoor side pressure reducing section depressurizes the refrigerant flowing into the outdoor heat exchange section, and the detour side pressure reducing section depressurizes the refrigerant flowing around the outdoor heat exchange section. As the operation mode in which the heating unit heats the supply air, there are an outdoor air heat absorption heating mode and a hot air heating mode. In the outdoor air heat absorption heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, and the suction port of the compressor. In the hot air heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the confluence portion, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

9. The refrigeration cycle device according to claim 8, characterized in that: have: a target outlet temperature determination unit (S20) for determining a target outlet temperature (TAO) of the supply air to be blown into the air-conditioning target space; as well as a supply air temperature detection unit (66) for detecting a supply air temperature (TAV) of the supply air blown to the air-conditioning target space; When the supply air temperature (TAV) is lower than the target outlet temperature (TAO), the refrigerant circuit switching unit switches from the outdoor air heat absorption heating mode to the hot air heating mode.

10. The refrigeration cycle device according to claim 8, characterized in that: A target outlet temperature determination unit (S20) is provided for determining a target outlet temperature (TAO) of the supply air to be blown into the air-conditioning target space. The refrigerant circuit switching unit switches from the hot air heating mode to the outdoor air heat absorption heating mode when the target air outlet temperature (TAO) is lower than the hot air reference temperature (δ).

11. The refrigeration cycle device according to any one of claims 8 to 10, characterized in that: A cooling unit (20, 50) is provided, which cools a cooling object. As an operation mode in which the cooling unit cools the cooling object and the heating unit heats the supply air, there are a cooling series dehumidification and heating mode and a cooling hot air dehumidification and heating mode, and the decompression unit on the bypass side decompresses the refrigerant flowing into the cooling unit. As operation modes in which the cooling unit cools the cooling object and the heating unit heats the supply air, there are a cooling outside air heat absorption heating mode and a cooling hot air heating mode. In the cooling outside air heat absorption heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: The refrigerant discharged from the compressor circulates in the order of the heating unit, the outdoor pressure reducing unit, the outdoor heat exchange unit, the detour pressure reducing unit, the cooling unit, and the suction port of the compressor. In the cooling hot air heating mode, the refrigerant circuit switching unit switches to the following refrigerant circuit: the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the heating portion, the detour side pressure reducing portion, the cooling portion, the confluence portion, and the suction port of the compressor; and the refrigerant discharged from the compressor circulates in the order of the upstream branch portion, the bypass passage, the confluence portion, and the suction port of the compressor.

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