Heat pump cycle device

Abstract

A heat pump cycle device is provided with a compressor (11), a branch section (12a), heating sections (13, 30, 30c), a heating section-side pressure reduction section (14c), a bypass passage (21c), a bypass-side flow rate adjustment section (14d), a converging section (12f), heat generation sections (44, 70, 84), and heat absorption sections (40, 40c). The heating unit (13, 30, 30c) heats the object to be heated using the refrigerant flowing out from one of the outlets of the branch unit as a heat source. And a bypass passage (21c) through which the other refrigerant branched from the branch portion flows. The heat-absorbing section (40, 40c) absorbs heat generated by the heat-generating section (44, 70, 84) at least by the refrigerant flowing out from the heating-section-side pressure-reducing section (14c).

Description

[0001] Cross-reference to related applications

[0002] This application is based on Japanese Patent Application No. 2022-179483 filed on November 9, 2022, the contents of which are incorporated herein by reference. Technical field

[0003] The present disclosure relates to a heat pump cycle device that heats an object to be heated using heat generated by the compression operation of a compressor. Background art

[0004] Conventionally, Patent Document 1 discloses a heat pump cycle device applied to a vehicle air conditioner and used for heating the interior of a vehicle. In the heat pump cycle device of Patent Document 1, when operating under conditions where it is difficult to absorb heat from the outside air for heating the supply air blown into the vehicle interior, such as at low outside air temperatures, the refrigerant circuit is switched to perform a hot gas heating mode operation.

[0005] In the refrigerant circuit for the hot gas heating mode, the flow of the refrigerant discharged from the compressor is branched, and one of the branched refrigerants flows into the heating section. In the heating section, the refrigerant discharged from the compressor is used as a heat source to heat the supply air. Further, in the refrigerant circuit of the hot gas heating mode, the refrigerant flowing out of the heating section and the other refrigerant branched at the branch section are mixed after being decompressed respectively and then sucked into the compressor.

[0006] Accordingly, in the heat pump cycle device of Patent Document 1, in the hot gas heating mode, the supply air as the object to be heated is heated using the heat generated by the compression operation of the compressor instead of the heat absorbed from the outside air.

[0007] Prior art documents

[0008] Patent documents

[0009] Patent Document 1: Japanese Unexamined Patent Application Publication No. 2021-156567

[0010] However, in the hot gas heating mode of Patent Document 1, only the heat generated by the compression operation of the compressor is used to heat the supply air. Therefore, if the rotational speed of the compressor reaches the upper limit rotational speed determined according to the durability of the compressor, the noise tolerated by the compressor, etc., the heating capacity of the supply air in the heating section cannot be increased. As a result, the heating capacity in the heating section may be insufficient. Summary of the invention

[0011] In view of the above points, an object of the present disclosure is to provide a heat pump cycle device capable of increasing the heating capacity of an object to be heated without increasing the rotational speed of the compressor.

[0012] One aspect of the present disclosure, a heat pump cycle device includes a compressor, a branch portion, a heating portion, a decompression portion on the heating portion side, a bypass passage, a flow rate adjustment portion on the bypass side, a confluence portion, a heat generating portion, and a heat absorbing portion.

[0013] The compressor compresses and discharges a refrigerant. The branch portion branches the flow of the refrigerant discharged from the compressor. The heating portion heats a heating object using the refrigerant flowing out from one outlet of the branch portion as a heat source. The decompression portion on the heating portion side decompresses the refrigerant flowing out from the heating portion. The bypass passage allows the other refrigerant branched in the branch portion to flow therethrough. The flow rate adjustment portion on the bypass side adjusts the flow rate of the refrigerant flowing through the bypass passage. The confluence portion causes the flow of the refrigerant flowing out from the flow rate adjustment portion on the bypass side to merge with the flow of the refrigerant flowing out from the decompression portion on the heating portion side and flow out toward the suction port side of the compressor. Moreover, the heat generating portion generates heat. The heat absorbing portion causes at least the refrigerant flowing out from the decompression portion on the heating portion side to absorb the heat generated by the heat generating portion.

[0014] Accordingly, it is possible to heat the heating object in the heating portion. At this time, in the confluence portion, the refrigerant having a relatively high enthalpy flowing out from the flow rate adjustment portion on the bypass side merges with the refrigerant having a relatively low enthalpy flowing out from the decompression portion on the heating portion side and flows out toward the suction port side of the compressor. Therefore, it is possible to maintain the suction refrigerant sucked into the compressor in an appropriate state and stably heat the heating object in the heating portion.

[0015] Moreover, the heat absorbing portion causes at least the refrigerant flowing out from the decompression portion on the heating portion side to absorb the heat generated by the heat generating portion. Therefore, by increasing the heat absorption amount of the refrigerant flowing out from the decompression portion on the heating portion side, it is possible to increase the heat dissipation amount from the refrigerant to the heating object in the heating portion without increasing the rotational speed of the compressor.

[0016] That is, according to one aspect of the present disclosure, a heat pump cycle device can improve the heating ability of the heating object in the heating portion without increasing the rotational speed of the compressor.

[0017] Here, "at least the refrigerant flowing out from the decompression portion on the heating portion side" is not limited to the refrigerant flowing out only from the decompression portion on the heating portion side. As long as it includes the refrigerant flowing out from the decompression portion on the heating portion side, it may be the refrigerant after merging with the refrigerant flowing out from the flow rate adjustment portion on the bypass side. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The above object and other objects, features, and advantages of the present disclosure will become more apparent by referring to the accompanying drawings and the following detailed description.

[0019] Figure 1 is a schematic overall structure diagram of an air conditioner for a vehicle according to the first embodiment.

[0020] Figure 2It is a schematic structural diagram of the indoor air conditioner unit of the first embodiment.

[0021] Figure 3 It is a block diagram showing the electric control unit of the vehicle air conditioner device of the first embodiment.

[0022] Figure 4 It is a control characteristic diagram for determining the upper limit rotational speed of the compressor corresponding to the vehicle speed of the first embodiment.

[0023] Figure 5 It is a control characteristic diagram for determining the target heat medium temperature corresponding to the upper limit rotational speed of the compressor of the first embodiment.

[0024] Figure 6 It is a schematic overall structural diagram showing the flow of refrigerant and the like in the first heat absorption hot gas heating mode of the vehicle air conditioner device of the first embodiment.

[0025] Figure 7 It is a Mollier diagram showing the state of the refrigerant in the first heat absorption hot gas heating mode of the heat pump cycle of the first embodiment.

[0026] Figure 8 It is a schematic overall structural diagram showing the flow of refrigerant and the like in the second heat absorption hot gas heating mode of the vehicle air conditioner device of the first embodiment.

[0027] Figure 9 It is a schematic overall structural diagram showing the flow of refrigerant and the like in the first heat absorption hot gas heating preparation mode of the vehicle air conditioner device of the first embodiment.

[0028] Figure 10 It is a schematic overall structural diagram showing the flow of refrigerant and the like in the second heat absorption hot gas heating preparation mode of the vehicle air conditioner device of the first embodiment.

[0029] Figure 11 It is a schematic overall structural diagram of the vehicle air conditioner device of the second embodiment.

[0030] Figure 12 It is a schematic overall structural diagram of the vehicle air conditioner device of the third embodiment.

[0031] Figure 13 It is a schematic overall structural diagram of the vehicle air conditioner device of the fourth embodiment. Specific embodiments

[0032] Hereinafter, a plurality of embodiments for implementing the present disclosure will be described with reference to the accompanying drawings. In each embodiment, there are cases where the same reference signs are assigned to parts corresponding to those described in the previous embodiments, and repeated descriptions are omitted. When only a part of the structure is described in each embodiment, other previously described embodiments can be applied to the other parts of the structure. Not only can the parts that can be specifically combined in each embodiment be combined with each other, but also the embodiments can be partially combined with each other as long as there is no particular obstacle to the combination, even if not explicitly stated.

[0033] (First Embodiment)

[0034] Use Figures 1 to 10 The first embodiment of the heat pump cycle device according to the present disclosure will be described. In the present embodiment, the heat pump cycle device according to the present disclosure is applied to the vehicle air conditioner 1 mounted on an electric vehicle. An electric vehicle is a vehicle that obtains driving force for traveling from an electric motor. The vehicle air conditioner 1 performs air conditioning in the vehicle interior, which is the air conditioning target space, and also adjusts the temperature of in-vehicle equipment. Therefore, the vehicle air conditioner 1 can be called an air conditioner with an in-vehicle equipment temperature adjustment function or an in-vehicle equipment temperature adjustment device with an air conditioning function.

[0035] In the vehicle air conditioner 1, as in-vehicle equipment, specifically, the temperature of the battery 70 is adjusted. The battery 70 is a secondary battery that stores electric power supplied to a plurality of in-vehicle equipment that operate using electricity. The battery 70 is a battery pack formed by electrically connecting a plurality of battery cells stacked in series or in parallel. The battery cell in the present embodiment is a lithium-ion battery.

[0036] The battery 70 generates heat during operation (i.e., during charging and discharging). The output of the battery 70 is likely to decrease at low temperatures, and deterioration is likely to occur at high temperatures. Therefore, the temperature of the battery 70 needs to be maintained within an appropriate temperature range (15°C or higher and 55°C or lower in the present embodiment). Therefore, in the electric vehicle of the present embodiment, the vehicle air conditioner 1 is used to adjust the temperature of the battery 70.

[0037] The vehicle air conditioner 1 includes a heat pump cycle 10, a high-temperature side heat medium circuit 30, a low-temperature side heat medium circuit 40, an in-vehicle air conditioning unit 50, a control device 60, and the like.

[0038] First, use Figure 1The heat pump cycle 10 will be described. The heat pump cycle 10 is a vapor compression refrigeration cycle that adjusts the temperature of the supply air blown into the vehicle interior, the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 30, and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 40. Moreover, in order to perform air conditioning in the vehicle interior and temperature adjustment of in-vehicle equipment, the heat pump cycle 10 is configured to be able to switch the refrigerant circuit according to various operating modes described later.

[0039] In the heat pump cycle 10, an HFO-based refrigerant (specifically, R1234yf) is used as the refrigerant. The heat pump cycle 10 constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure side refrigerant does not exceed the critical pressure of the refrigerant. In the refrigerant, a refrigeration oil for lubricating the compressor 11 is mixed. The refrigeration oil is a PAG oil (i.e., polyalkylene glycol oil) that is compatible with the liquid-phase refrigerant. A part of the refrigeration oil circulates in the heat pump cycle 10 together with the refrigerant.

[0040] In the heat pump cycle 10, the compressor 11 sucks in the refrigerant, compresses and discharges it. The compressor 11 is an electric compressor in which a fixed displacement type compression mechanism whose discharge capacity is fixed is rotated by an electric motor. The compressor 11 controls the rotational speed (i.e., the refrigerant discharge capacity) according to a control signal output from a control device 60 described later.

[0041] The compressor 11 is disposed in a drive device chamber formed on the front side of the vehicle interior. The drive device chamber forms a space in which at least a part of equipment (such as a driving motor for the vehicle) used for generating and adjusting the driving force for vehicle travel is disposed.

[0042] The discharge port of the compressor 11 is connected to the inflow port side of the first three-way joint 12a. The first three-way joint 12a has three inflow / outflow ports that communicate with each other. As the first three-way joint 12a, a joint formed by joining a plurality of pipes or a joint formed by providing a plurality of refrigerant passages in a metal block or a resin block can be used.

[0043] Moreover, as described below, the heat pump cycle 10 includes a second three-way joint 12b to a sixth three-way joint 12f. The basic structure of the second three-way joint 12b to the sixth three-way joint 12f is the same as that of the first three-way joint 12a. In addition, the basic structure of each three-way joint described in the embodiments below is also the same as that of the first three-way joint 12a.

[0044] When one of the three inflow / outflow ports of these three-way joints is used as the inflow port and the remaining two are used as the outflow ports, the flow of the refrigerant branches. In addition, when two of the three inflow / outflow ports are used as the inflow ports and the remaining one is used as the outflow port, the flow of the refrigerant merges. The first three-way joint 12a is a branch portion that branches the flow of the discharged refrigerant from the compressor 11.

[0045] One outlet 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 outlet of the first three-way joint 12a is connected to one inlet side of the sixth three-way joint 12f.

[0046] The refrigerant passage from the other outlet of the first three-way joint 12a to one inlet of the sixth three-way joint 12f is the bypass passage 21c. A bypass-side flow control valve 14d is arranged in the bypass passage 21c.

[0047] The bypass-side flow control valve 14d is a bypass-passage-side decompression section that decompresses the discharged refrigerant flowing out from the other outlet of the first three-way joint 12a (i.e., the discharged refrigerant branched at the first three-way joint 12a) during the hot-gas heating mode and the like described later. Moreover, the bypass-side flow control valve 14d is a bypass-side flow control section that adjusts the flow rate (mass flow rate in this embodiment) of the refrigerant flowing through the bypass passage 21c.

[0048] The bypass-side flow control valve 14d is an electric variable throttle mechanism having a valve element that changes the throttle opening degree and an electric actuator (specifically, a stepping motor) as a driving section that displaces the valve element. The bypass-side flow control valve 14d controls its operation using control pulses output from the control device 60.

[0049] The bypass-side flow control valve 14d has a fully open function that hardly exerts a refrigerant decompression effect and a flow control effect by setting the throttle opening degree to the fully open state and functions as a simple refrigerant passage. In addition, the bypass-side flow control valve 14d has a fully closed function that closes the refrigerant passage by setting the throttle opening degree to the fully closed state.

[0050] Moreover, as described later, the heat pump cycle 10 includes a heating expansion valve 14a, a refrigeration expansion valve 14b, and a cooling expansion valve 14c. The basic structures of the heating expansion valve 14a, the refrigeration expansion valve 14b, and the cooling expansion valve 14c are the same as those of the bypass-side flow control valve 14d.

[0051] The heating expansion valve 14a, the refrigeration expansion valve 14b, the cooling expansion valve 14c, and the bypass-side flow control valve 14d can switch the refrigerant circuit by exerting the above-mentioned fully closed function. Therefore, the heating expansion valve 14a, the refrigeration expansion valve 14b, the cooling expansion valve 14c, and the bypass-side flow control valve 14d also function as refrigerant circuit switching sections.

[0052] Of course, a variable throttle mechanism that does not have a fully closed function and an on-off valve for opening and closing the throttle passage can also be combined to form a heating expansion valve 14a, a refrigeration expansion valve 14b, a cooling expansion valve 14c, and a bypass side flow rate adjustment valve 14d. In this case, each on-off valve becomes a refrigerant circuit switching section.

[0053] The water-refrigerant heat exchanger 13 is a heat dissipation heat exchange section that exchanges heat between the discharged refrigerant flowing out from one of the outlets of the first three-way joint 12a (i.e., one of the discharged refrigerants branched at the first three-way joint 12a) and the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 30. In the water-refrigerant heat exchanger 13, the heat possessed by the discharged refrigerant is dissipated to the high-temperature side heat medium to heat the high-temperature side heat medium.

[0054] 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 of the outlets of the second three-way joint 12b is connected to the inlet side of the heating expansion valve 14a. The other outlet of the second three-way joint 12b is connected to one of the inlets of the four-way joint 12x.

[0055] The refrigerant passage from the other outlet of the second three-way joint 12b to one of the inlets of the four-way joint 12x is the high-pressure side passage 21a. A high-pressure side on-off valve 22a is arranged in the high-pressure side passage 21a.

[0056] The high-pressure side on-off valve 22a is an on-off valve for opening and closing the high-pressure side passage 21a. The high-pressure side on-off valve 22a is an electromagnetic valve that controls its opening and closing operation by using the 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 section.

[0057] The four-way joint 12x is a joint section having four inlets and outlets communicating with each other. As the four-way joint 12x, a joint section formed in the same manner as the above-mentioned three-way joint can be adopted. The four-way joint 12x can also be formed by combining two three-way joints.

[0058] The heating expansion valve 14a is a decompression section on the outdoor heat exchanger side that decompresses the refrigerant flowing into the outdoor heat exchanger 15 during the outdoor air heat absorption heating mode described later and the like. Moreover, the heating expansion valve 14a is a flow rate adjustment section on the outdoor heat exchanger side that adjusts the flow rate of the refrigerant flowing into the outdoor heat exchanger 15.

[0059] The outlet of the expansion valve 14a for heating is connected to the refrigerant inlet side of the outdoor heat exchanger 15. The outdoor heat exchanger 15 is an outdoor air heat exchange section that exchanges heat between the refrigerant flowing out from the expansion valve 14a for heating and the outdoor air blown by an outdoor air fan (not shown). The outdoor heat exchanger 15 is disposed on the front side of the drive unit chamber. Therefore, when the vehicle is running, the running air flowing into the drive unit chamber via the grille can be brought into contact with the outdoor heat exchanger 15.

[0060] 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 four-way joint 12x via the first check valve 16a. The other outlet of the third three-way joint 12c is connected to the inlet side of one of the fourth three-way joints 12d.

[0061] The refrigerant passage from the other outlet of the third three-way joint 12c to the inlet side of one of the fourth three-way joints 12d is the low-pressure side passage 21b. The low-pressure side on-off valve 22b is disposed in the low-pressure side passage 21b.

[0062] The low-pressure side on-off valve 22b is an on-off valve that opens and closes 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 section. In addition, the basic structure of each on-off valve described in the embodiments to be described later is also the same as that of the high-pressure side on-off valve 22a.

[0063] The first check valve 16a allows the refrigerant to flow from the third three-way joint 12c side to the four-way joint 12x side and prohibits the refrigerant from flowing from the four-way joint 12x side to the third three-way joint 12c side.

[0064] One outlet of the four-way joint 12x is connected to the refrigerant inlet side of the indoor evaporator 18 via the expansion valve 14b for refrigeration.

[0065] The expansion valve 14b for refrigeration is a decompression section on the indoor evaporator side that decompresses the refrigerant flowing into the indoor evaporator 18 in the refrigeration mode to be described later and so on. Moreover, the expansion valve 14b for refrigeration is a flow rate adjustment section on the indoor evaporator side that adjusts the flow rate of the refrigerant flowing into the indoor evaporator 18.

[0066] The indoor evaporator 18 is disposed in the air-conditioning housing 51 of the indoor air-conditioning unit 50 to be described later. The indoor evaporator 18 is a refrigeration heat exchange section that exchanges heat between the low-pressure refrigerant decompressed by the expansion valve 14b for refrigeration and the supply air blown from the indoor blower 52 toward the vehicle interior. In the indoor evaporator 18, the low-pressure refrigerant evaporates to exert an endothermic effect to cool the supply air.

[0067] The refrigerant outlet of the indoor evaporator 18 is connected to the inlet side of one of the ports of the fifth three-way joint 12e via the second check valve 16b. The second check valve 16b allows the refrigerant to flow from the refrigerant outlet side of the indoor evaporator 18 to the fifth three-way joint 12e side, and prohibits the refrigerant from flowing from the fifth three-way joint 12e to the refrigerant outlet side of the indoor evaporator 18.

[0068] The other outlet of the four-way joint 12x is connected to the inlet side of the other port of the sixth three-way joint 12f via the cooling expansion valve 14c. The outlet of the sixth three-way joint 12f is connected to the inlet side of the refrigerant passage of the cooler 20.

[0069] The cooling expansion valve 14c is a decompression part on the cooler side that decompresses the refrigerant flowing into the cooler 20 in the hot gas heating mode described later, the operation mode for cooling the battery 70, etc. Moreover, the cooling expansion valve 14c is a flow rate adjustment part on the cooler side that adjusts the flow rate of the refrigerant flowing into the cooler 20.

[0070] The cooler 20 is a heat absorption heat exchange part 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 40. In the cooler 20, the low-pressure refrigerant is evaporated to exert a heat absorption effect to cool the low-temperature side heat medium.

[0071] The outlet of the refrigerant passage of the cooler 20 is connected to the inlet side of the other port of the fourth three-way joint 12d. The outlet of the fourth three-way joint 12d is connected to the inlet side of the other port of the fifth three-way joint 12e.

[0072] The outlet of the fifth three-way joint 12e is connected to the inlet side of the accumulator 23. The accumulator 23 is a low-pressure side gas-liquid separator that separates the refrigerant flowing into it into gas and liquid phases and stores the separated liquid-phase refrigerant as the remaining refrigerant for circulation. The gas-phase refrigerant outlet of the accumulator 23 is connected to the suction inlet side of the compressor 11.

[0073] Next, the high-temperature side heat medium circuit 30 will be described. The high-temperature side heat medium circuit 30 is a circuit for circulating the high-temperature side heat medium. In the present embodiment, an ethylene glycol aqueous solution is used as the high-temperature side heat medium. In the high-temperature side heat medium circuit 30, a high-temperature side pump 31, a heater core 32, a heat medium passage of the water-refrigerant heat exchanger 13, etc. are arranged.

[0074] The high-temperature side pump 31 is a high-temperature side heat medium pumping part that sucks the high-temperature side heat medium flowing out from the heater core 32 and pumps it to the inlet side of the heat medium passage of the water-refrigerant heat exchanger 13. The high-temperature side pump 31 is an electric pump that controls the rotation speed (i.e., the pumping capacity) using the control voltage output from the control device 60.

[0075] The heater core 32 is a heat exchanger for heating supply air by exchanging heat between the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 and the supply air that has passed through the indoor evaporator 18. The heater core 32 is disposed within the air-conditioning housing 51 of the indoor air-conditioning unit 50. The heat medium outlet of the heater core 32 is connected to the suction port side of the high-temperature side pump 31.

[0076] Therefore, in the high-temperature side heat medium circuit 30, by operating the high-temperature side pump 31, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 can be made to flow into the heater core 32. Then, the high-temperature side heat medium can exchange heat with the supply air in the heater core 32 to heat the supply air.

[0077] Therefore, each component device of the water refrigerant heat exchanger 13 and the high-temperature side heat medium circuit 30 in the present embodiment is a heating unit that uses the refrigerant flowing out from one of the outlets of the first three-way joint 12a as a heat source to heat the supply air as the object to be heated.

[0078] In addition, the cooling expansion valve 14c is a decompression unit on the heating unit side that decompresses the refrigerant flowing out from the water refrigerant heat exchanger 13 forming the heating unit during the hot gas heating mode or the like. Moreover, the sixth three-way joint 12f is a merging unit that merges the flow of the refrigerant flowing out from the cooling expansion valve 14c and the flow of the bypass side refrigerant flowing out from the bypass side flow rate adjustment valve 14d and discharges the mixture to the suction port side of the compressor 11.

[0079] Next, the low-temperature side heat medium circuit 40 will be described. The low-temperature side heat medium circuit 40 is a circuit for circulating the low-temperature side heat medium. In the present embodiment, the same type of fluid as the high-temperature side heat medium is used as the low-temperature side heat medium. In the low-temperature side heat medium circuit 40, there are arranged a first low-temperature side pump 41a, a second low-temperature side pump 41b, a heat medium three-way valve 42, a heat medium four-way valve 43, a heating passage 44a of the heat medium electric heater 44, a cooling water passage 70a of the battery 70, a heat medium passage of the cooler 20, and the like.

[0080] The first low-temperature side pump 41a is a low-temperature side heat medium pumping unit that sucks the low-temperature side heat medium flowing out from one of the outlets of the heat medium four-way valve 43 and pumps it to the heating passage 44a of the heat medium electric heater 44. The second low-temperature side pump 41b is a low-temperature side heat medium pumping unit that sucks the low-temperature side heat medium flowing out from the other outlet of the heat medium four-way valve 43 and pumps it to the cooling water passage 70a of the battery 70.

[0081] The basic structures of the first low-temperature side pump 41a and the second low-temperature side pump 41b are the same as those of the high-temperature side pump 31. The first low-temperature side pump 41a and the second low-temperature side pump 41b can adjust the flow rate of the heat medium circulating in the heat medium circuit. Therefore, the first low-temperature side pump 41a and the second low-temperature side pump 41b in the present embodiment are heat medium flow rate adjustment parts that adjust the inflow rate of the heat medium flowing into the heat medium passage of the cooler 20.

[0082] The heat medium electric heater 44 is a heat generating part that generates heat by supplying electric power. In the present embodiment, a PTC heater having a PTC element (i.e., a positive temperature coefficient thermistor) can be used as the heat medium electric heater 44. The heat medium electric heater 44 controls the calorific value by the electric power supplied from the control device 60.

[0083] The heating passage 44a is a heat medium passage through which the low-temperature side heat medium pumped by the first low-temperature side pump 41a flows. The heating passage 44a is integrally formed in the housing that houses the heat medium electric heater 44. Therefore, when the heat medium electric heater 44 generates heat, if the low-temperature side heat medium is made to flow through the heating passage 44a, the heat generated by the heat medium electric heater 44 can be used to heat the low-temperature side heat medium.

[0084] The heat medium outlet of the heating passage 44a is connected to the inlet side of the heat medium three-way valve 42. One outlet of the heat medium three-way valve 42 is connected to the inlet side of the heat medium passage of the cooler 20. In addition, the other outlet of the heat medium three-way valve 42 is connected to the inlet side of the heat medium bypass passage 45. The heat medium bypass passage 45 is a heat medium passage that allows the low-temperature side heat medium flowing out of the heating passage 44a to flow around the heat medium passage of the cooler 20.

[0085] The heat medium three-way valve 42 is a heat medium circuit switching part that switches the circuit structure of the low-temperature side heat medium circuit 40. The heat medium three-way valve 42 controls its operation using the control voltage output from the control device 60.

[0086] Specifically, the heat medium three-way valve 42 can be switched to the circuit connecting the outlet side of the heating passage 44a and the inlet side of the heat medium passage of the cooler 20. In addition, the heat medium three-way valve 42 can be switched to the circuit connecting the outlet side of the heating passage 44a and the inlet side of the heat medium bypass passage 45.

[0087] The outlet of the heat medium passage of the cooler 20 is connected to one inlet side of the heat medium three-way joint 46. The outlet of the heat medium bypass passage 45 is connected to the other inlet side of the heat medium three-way joint 46. The outlet of the heat medium three-way joint 46 is connected to one inlet side of the heat medium four-way valve 43. The basic structure of the heat medium three-way joint 46 is the same as that of the first three-way joint 12a of the heat pump cycle 10, etc.

[0088] The hot medium four-way valve 43 is a hot medium circuit switching unit that switches the circuit structure of the low-temperature side hot medium circuit 40. The hot medium four-way valve 43 controls its operation using the control voltage output from the control device 60.

[0089] Specifically, the hot medium four-way valve 43 can be switched to a circuit that connects the outlet side of the hot medium three-way joint 46 and the inlet side of the second low-temperature side pump 41b while connecting the outlet side of the cooling water passage 70a of the battery 70 and the inlet side of the first low-temperature side pump 41a. In addition, the hot medium four-way valve 43 can be switched to a circuit that connects the outlet side of the hot medium three-way joint 46 and the inlet side of the first low-temperature side pump 41a while connecting the outlet side of the cooling water passage 70a of the battery 70 and the inlet side of the second low-temperature side pump 41b.

[0090] The cooling water passage 70a of the battery 70 is a hot medium passage through which the low-temperature side hot medium pumped by the second low-temperature side pump 41b flows. The cooling water passage 70a is formed inside the battery dedicated housing that houses a plurality of battery cells stacked.

[0091] Therefore, when the battery 70 generates heat, if the low-temperature low-temperature side hot medium is made to flow through the cooling water passage 70a, the battery 70 can be cooled. In other words, when the battery 70 generates heat, if the low-temperature low-temperature side hot medium is made to flow through the cooling water passage 70a, the heat generated by the battery 70 can be used to heat the low-temperature side hot medium.

[0092] In addition, the passage structure of the cooling water passage 70a is a passage structure in which a plurality of passages are connected in parallel inside the battery dedicated housing. Thus, in the cooling water passage 70a, all the battery cells can be cooled evenly. The outlet of the cooling water passage 70a is connected to the other inlet side of the hot medium four-way valve 43.

[0093] Therefore, the hot medium electric heater 44 and the battery 70 in the present embodiment are heat generating parts that generate heat for heating the low-temperature side hot medium.

[0094] Moreover, the calorific value of the hot medium electric heater 44 can be controlled using the electric power supplied from the control device 60. Therefore, the hot medium electric heater 44 in the present embodiment is a highly controllable heat generating part that can easily control the calorific value to the amount desired by the user. Moreover, the hot medium electric heater 44 is a priority heat generating part that preferentially controls the calorific value in order to adjust the temperature of the low-temperature side hot medium.

[0095] In contrast, the battery 70 discharges according to the needs of various in-vehicle devices during driving and parking, and charges according to the specifications of the charger, etc. during charging. Therefore, the heat generation amount of the battery 70 is more difficult to control than that of the highly controllable heating part. Therefore, the battery 70 of the present embodiment is a low controllable heating part with a lower controllability than the highly controllable heating part. The low controllable heating part also includes a heating part whose heat generation amount cannot be controlled by the control device 60. Moreover, the battery 70 is a low priority heating part that controls the heat generation amount with a lower priority than the priority heating part.

[0096] In addition, the low-temperature side heat medium circuit 40 is a heat medium circuit that circulates the low-temperature side heat medium heated by the heat medium electric heater 44 or the battery 70. In addition, the cooler 20 serves as a heat absorption part that causes the refrigerant flowing out from the sixth three-way joint 12f to absorb the heat generated by the heat medium electric heater 44 and the battery 70 via the low-temperature side heat medium.

[0097] Next, Figure 2 The in-vehicle air conditioner unit 50 will be described. The in-vehicle air conditioner unit 50 is a unit in which a plurality of constituent devices are integrated in order to blow the supply air adjusted to an appropriate temperature for air conditioning in the vehicle interior to an appropriate part in the vehicle interior. The in-vehicle air conditioner unit 50 is disposed inside the instrument panel (instrument panel) at the foremost part in the vehicle interior.

[0098] The in-vehicle air conditioner unit 50 is formed by accommodating an in-vehicle blower 52, an in-vehicle evaporator 18, a heater core 32, etc. in an air conditioner housing 51 that forms an air passage for the supply air. The air conditioner housing 51 is formed of a resin (such as polypropylene) having a certain degree of elasticity and excellent strength.

[0099] An inside / outside air switching device 53 is disposed on the most upstream side of the supply air flow of the air conditioner housing 51. The inside / outside air switching device 53 switches between introducing inside air (i.e., vehicle interior air) and outside air (i.e., vehicle exterior air) into the air conditioner housing 51. The inside / outside air switching device 53 controls its operation using a control signal output from the control device 60.

[0100] An in-vehicle blower 52 is disposed on the downstream side of the supply air flow of the inside / outside air switching device 53. The in-vehicle blower 52 is a blowing part that blows the air sucked through the inside / outside air switching device 53 toward the vehicle interior. The in-vehicle blower 52 controls the rotation speed (i.e., blowing ability) using a control voltage output from the control device 60.

[0101] An in-vehicle evaporator 18 and a heater core 32 are disposed on the downstream side of the supply air flow of the in-vehicle blower 52. The in-vehicle evaporator 18 is disposed on the upstream side of the supply air flow compared to the heater core 32. A cold air bypass passage 55 is formed in the air conditioner housing 51 to allow the supply air that has passed through the in-vehicle evaporator 18 to bypass the heater core 32 and flow.

[0102] An air mixing door 54 is disposed on the downstream side of the air flow of the indoor evaporator 18 in the air conditioner housing 51 and on the upstream side of the air flows of the heater core 32 and the cold air bypass passage 55.

[0103] The air mixing door 54 adjusts the air volume ratio between the air volume of the air flow passing through the heater core 32 side and the air volume of the air flow passing through the cold air bypass passage 55 in the air flow passing through the indoor evaporator 18. The actuator for driving the air mixing door 54 controls its operation using a control signal output from the control device 60.

[0104] A mixing space 56 is disposed on the downstream side of the air flows of the heater core 32 and the cold air bypass passage 55. The mixing space 56 is a space where the air flow heated by the heater core 32 and the air flow not heated passing through the cold air bypass passage 55 are mixed.

[0105] Therefore, in the indoor air conditioner unit 50, the temperature of the air flow (i.e., the air conditioner air) mixed in the mixing space 56 and blown into the vehicle interior can be adjusted by adjusting the opening degree of the air mixing door 54. The air mixing door 54 of the present embodiment is an air volume adjustment unit that adjusts the air volume of the air flow that exchanges heat in the heater core 32.

[0106] A plurality of unillustrated opening holes for blowing the air conditioner air toward various parts of the vehicle interior are formed at the most downstream portion of the air flow in the air conditioner housing 51. A blowing mode door (not shown) for opening and closing each opening hole is disposed at the plurality of opening holes. The actuator for driving the blowing mode door controls its operation using a control signal output from the control device 60.

[0107] Therefore, in the indoor air conditioner unit 50, the air conditioner air adjusted to an appropriate temperature can be blown to an appropriate part of the vehicle interior by switching the opening holes opened and closed by the blowing mode door.

[0108] Next, the electric control unit of the present embodiment will be described. The control device 60 includes a well-known microcomputer such as a CPU, a ROM, and a RAM and its peripheral circuits. The control device 60 performs various operations and processes based on a control program stored in the ROM. Then, the control device 60 controls the operation of various controlled devices connected to the output side based on the operation and processing results.

[0109] As Figure 3As shown in the block diagram, the input side of the control device 60 is connected to a group of control sensors such as an internal air temperature sensor 61a, an outside air temperature sensor 61b, a solar radiation sensor 61c, a discharged refrigerant temperature sensor 62a, a high-pressure side refrigerant temperature and pressure sensor 62b, an outdoor unit side refrigerant temperature and pressure sensor 62c, an evaporator temperature sensor 62d, a cooler side refrigerant temperature and pressure sensor 62e, a high-temperature side heat medium temperature sensor 63a, a low-temperature side heat medium temperature sensor 63b, a battery temperature sensor 64, and an air-conditioning air temperature sensor 65.

[0110] The internal air temperature sensor 61a is an internal air temperature detection unit that detects the temperature of the air inside the vehicle (internal air temperature) Tr. The outside air temperature sensor 61b is an outside air temperature detection unit that detects the temperature of the air outside the vehicle (outside air temperature) Tam. The solar radiation sensor 61c is a solar radiation detection unit that detects the amount of solar radiation As irradiated into the vehicle interior.

[0111] The discharged refrigerant temperature sensor 62a is a discharged refrigerant temperature detection unit that detects the discharged refrigerant temperature Td of the discharged refrigerant from the compressor 11.

[0112] The high-pressure side refrigerant temperature and pressure sensor 62b is a high-pressure side refrigerant temperature and pressure detection unit that detects the high-pressure side refrigerant temperature T1 and the discharged refrigerant pressure Pd. The high-pressure side refrigerant temperature T1 is the temperature of the refrigerant flowing out of the water-refrigerant heat exchanger 13, and the discharged refrigerant pressure Pd is the pressure of the refrigerant flowing out of the water-refrigerant heat exchanger 13. The discharged refrigerant pressure Pd can be used as the pressure of the discharged refrigerant from the compressor 11.

[0113] The outdoor unit side refrigerant temperature and pressure sensor 62c 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. The outdoor unit side refrigerant temperature T2 is the temperature of the refrigerant flowing out of the outdoor heat exchanger 15, and the outdoor unit side refrigerant pressure P2 is the pressure of the refrigerant flowing out of the outdoor heat exchanger 15. Specifically, it detects the temperature and pressure of the refrigerant flowing through the refrigerant passage from the refrigerant outlet of the outdoor heat exchanger 15 to the inlet of the third three-way joint 12c.

[0114] The evaporator temperature sensor 62d is an evaporator temperature detection unit for detecting the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18. Specifically, the evaporator temperature sensor 62d detects the heat exchange fin temperature of the indoor evaporator 18.

[0115] The cooler-side refrigerant temperature and pressure sensor 62e is a cooler-side refrigerant temperature and pressure detection unit that detects the cooler-side refrigerant temperature Tc and the cooler-side refrigerant pressure Pc. The cooler-side refrigerant temperature Tc is the temperature of the refrigerant flowing out of the refrigerant passage of the cooler 20, and the cooler-side refrigerant pressure Pc is the pressure of the refrigerant flowing out of the refrigerant passage of the cooler 20. In the present embodiment, the cooler-side refrigerant pressure Pc can be used as the suction refrigerant pressure Ps, which is the pressure of the suction refrigerant sucked into the compressor 11.

[0116] In the present embodiment, as the refrigerant temperature and pressure sensor, a detection unit in which the pressure detection unit and the temperature detection unit are integrated is adopted. However, of course, a pressure detection unit and a temperature detection unit each composed of a separate body can also be adopted.

[0117] The high-temperature-side heat medium temperature sensor 63a is a high-temperature-side heat medium temperature detection unit that detects the high-temperature-side heat medium temperature TWH. The high-temperature-side heat medium temperature TWH is the temperature of the high-temperature-side heat medium flowing into the heater core 32.

[0118] The low-temperature-side heat medium temperature sensor 63b is a low-temperature-side heat medium temperature detection unit that detects the low-temperature-side heat medium temperature TWL. The low-temperature-side heat medium temperature TWL is the temperature of the low-temperature-side heat medium flowing out of the heating passage 44a of the heat medium electric heater 44 and flowing into the heat medium three-way valve 42. In the present embodiment, the low-temperature-side heat medium temperature TWL can be used as the inflow temperature TWLC, which is the temperature of the heat medium flowing into the heat medium passage of the cooler 20 from the heat medium three-way valve 42.

[0119] The battery temperature sensor 64 is a battery temperature detection unit that detects the battery temperature TB, which is the temperature of the battery 70. The battery temperature sensor 64 has a plurality of temperature sensors and detects the temperatures of a plurality of parts of the battery 70. Therefore, in the control device 60, the temperature difference and temperature distribution of each battery cell forming the battery 70 can be detected. Moreover, the average value of the detection values of the plurality of temperature sensors is adopted as the battery temperature TB.

[0120] The air-conditioning air temperature sensor 65 is an air-conditioning air temperature detection unit that detects the air supply air temperature TAV blown from the mixing space 56 into the vehicle interior. The air supply air temperature TAV is the object temperature of the air supply air as the heating object.

[0121] In addition, as Figure 3 shown, the operation panel 69 disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device 60 by wire or wirelessly. The operation signals from various operation switches provided on the operation panel 69 are input to the control device 60.

[0122] As various operation switches provided on the operation panel 69, there are specifically an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, etc.

[0123] The auto switch is an automatic control setting unit for setting or canceling the automatic control operation of the vehicle air conditioner device 1. The air conditioner switch is a cooling requirement unit for requiring the cooling of the supply air in 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 52. The temperature setting switch is a temperature setting unit for setting the set temperature Tset in the vehicle interior.

[0124] In addition, the control device 60 of the present embodiment is integrally constituted by a control unit, and this control unit controls various controlled devices connected to its output side. Therefore, the structure (hardware and software) for controlling the operations of the respective controlled devices constitutes the control unit for controlling the operations of the respective controlled devices.

[0125] For example, the structure for controlling the refrigerant discharge capacity of the compressor 11 in the control device 60 constitutes the discharge capacity control unit 60a. The structure for controlling the calorific value of the highly controllable heating part, i.e., the heat medium electric heater 44, constitutes the calorific value control unit 60b. The structure for controlling the operations of the heat medium circuit switching parts, i.e., the heat medium three-way valve 42 and the heat medium four-way valve 43, constitutes the heat medium circuit control unit 60c. The structure for controlling the operations of the heat medium flow rate adjustment parts, i.e., the first low-temperature side pump 41a and the second low-temperature side pump 41b, constitutes the inflow flow rate adjustment unit 60d.

[0126] In addition, the structure for determining the upper limit speed Nclmt of the compressor 11 constitutes the upper limit speed determination unit 60e. In the upper limit speed determination unit 60e of the present embodiment, as Figure 4 shown in the control characteristic diagram, within the range below the maximum speed Ncmax determined by the durability of the compressor 11, the upper limit speed Nclmt is decreased as the vehicle speed Vv decreases. The reason is that as the vehicle speed Vv decreases, the allowable noise level of the compressor 11 decreases.

[0127] In addition, the structure for determining the target heat medium temperature TWLCO of the inflow temperature TWLC constitutes the target heat medium temperature determination unit 60f. The target heat medium temperature TWLCO is determined to be a value higher than the cooler side refrigerant temperature Tc detected by the cooler side refrigerant temperature pressure sensor 62e. In other words, it is determined to be capable of allowing the low-pressure refrigerant to absorb heat from the low-temperature side heat medium in the cooler 20.

[0128] In the target heat medium temperature determination unit 60f of the present embodiment, as Figure 5As shown in the control characteristic diagram, the target hot medium temperature TWLCO rises as the upper limit rotational speed Nclmt decreases. That is, the total calorific value of the battery 70 and the electric heater 44 for the hot medium increases as the upper limit rotational speed Nclmt increases. The reason is that as the upper limit rotational speed Nclmt decreases, the compression work of the compressor 11 tends to decrease.

[0129] Next, the operation of the vehicle air conditioner 1 of the present embodiment in the above structure will be described. In the vehicle air conditioner 1 of the present embodiment, various operation modes are switched in order to perform air conditioning in the vehicle interior and adjust the temperature of the battery 70. The switching of the operation mode is performed by executing a control program pre-stored in the control device 60.

[0130] In the control program, the detection signals of the above-described sensor group for control and the operation signals of the operation panel 69 are read. Then, based on the read detection signals and operation signals, the target blow-out temperature TAO, which is the target temperature of the supply air blown into the vehicle interior, is calculated. Further, based on the detection signals, operation signals, target blow-out temperature TAO, etc., the operation mode is selected, and the operations of various controlled devices are controlled according to the selected operation mode.

[0131] After that, until the termination condition of the control program is satisfied, the above-described control routine of reading the detection signals and operation signals, calculating the target blow-out temperature TAO, selecting the operation mode, and controlling various controlled devices is repeated at each prescribed control cycle.

[0132] The target blow-out temperature TAO is calculated using the following mathematical formula F1.

[0133] TAO = Kset × Tset - Kr × Tr - Kam × Tam - Ks × As + C...(F1)

[0134] Tset is the set temperature in the vehicle interior set by the temperature setting switch. Tr is the internal air temperature detected by the internal air temperature sensor 61a. Tam is the outside air temperature detected by the outside air temperature sensor 61b. As is the amount of sunlight detected by the sunlight amount sensor 61c. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant. Each operation mode will be described below.

[0135] (a) Cooling mode

[0136] The cooling mode is an operation mode in which the vehicle interior is cooled by blowing the cooled supply air into the vehicle interior. In a state where the automatic switch and the air conditioner switch are turned on, when the outside air temperature Tam becomes a relatively high temperature (25°C or higher in the present embodiment) or the target blow-out temperature TAO becomes a relatively low value, the cooling mode is easily selected.

[0137] In the refrigeration mode, there are a single refrigeration mode and a cooling refrigeration mode. The single refrigeration mode is an operating mode in which the interior of the vehicle is refrigerated without cooling the battery 70. The cooling refrigeration mode is an operating mode in which the battery 70 is cooled and the interior of the vehicle is refrigerated.

[0138] In the control program of the present embodiment, when the battery temperature TB detected by the battery temperature sensor 64 becomes equal to or higher than a predetermined reference cooling temperature KTB1, an operating mode for cooling the battery 70 is executed. This is the same for other operating modes described below.

[0139] (a-1) Single refrigeration mode

[0140] In the heat pump cycle 10 of the single refrigeration mode, the control device 60 sets the heating expansion valve 14a to the fully open state, sets the refrigeration expansion valve 14b to a throttling state that exerts a refrigerant pressure-reducing effect, sets the cooling expansion valve 14c to the fully closed state, and sets the bypass side flow control valve 14d to the fully closed state. In addition, the control device 60 closes the high-pressure side on-off valve 22a and closes the low-pressure side on-off valve 22b.

[0141] In addition, in the heat pump cycle 10, the control device 60 controls the operation of the expansion valve in the throttling state so that the suction refrigerant sucked into the accumulator 23 approaches the saturated vapor refrigerant.

[0142] Therefore, in the heat pump cycle 10 of the single refrigeration mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of the water refrigerant heat exchanger 13, the heating expansion valve 14a in the fully open state, the outdoor heat exchanger 15, the refrigeration expansion valve 14b in the throttling state, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11.

[0143] In addition, in the high-temperature side heat medium circuit 30 of the single refrigeration mode, the control device 60 operates the high-temperature side pump 31 to exert a predetermined reference pumping capacity. Therefore, in the high-temperature side heat medium circuit 30 of the single refrigeration mode, the high-temperature side heat medium pumped from the high-temperature side pump 31 circulates in the order of the heat medium passage of the water refrigerant heat exchanger 13, the heater core 32, and the suction port of the high-temperature side pump 31.

[0144] In addition, in the low-temperature side heat medium circuit 40 of the single refrigeration mode, the control device 60 stops the first low-temperature side pump 41a and the second low-temperature side pump 41b.

[0145] In addition, in the indoor air-conditioning unit 50 of the single refrigeration mode, the control device 60 controls the rotation speed of the indoor blower 52 based on the target blowing temperature TAO with reference to a control map stored in advance in the control device 60.

[0146] In addition, the control device 60 adjusts the opening degree of the air mixing door 54 so that the supply air temperature TAV detected by the air-conditioning air temperature sensor 65 approaches the target blow-out temperature TAO. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0147] Therefore, in the heat pump cycle 10 in the single cooling mode, it constitutes a vapor compression refrigeration cycle in which the water refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers for dissipating heat and condensing the refrigerant, and the indoor evaporator 18 functions as an evaporator for evaporating the refrigerant. Here, in the operation mode where the refrigerant evaporates in the indoor evaporator 18, the evaporation temperature of the refrigerant in the indoor evaporator 18 is adjusted within a range that can suppress frosting of the indoor evaporator 18.

[0148] In the high-temperature side heat medium circuit 30 in the single cooling mode, the high-temperature side heat medium flowing into the heat medium passage of the water refrigerant heat exchanger 13 exchanges heat with the refrigerant discharged from the compressor 11 and is heated. The high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32 and exchanges heat with the supply air. Thereby, the supply air is heated.

[0149] In the indoor air-conditioning unit 50 in the single cooling mode, the supply air blown from the indoor blower 52 is cooled by absorbing heat from the refrigerant when passing through the indoor evaporator 18. According to the opening degree of the air mixing door 54, the supply air cooled by the indoor evaporator 18 exchanges heat with the high-temperature side heat medium in the heater core 32 and is heated again. Then, by blowing the supply air whose temperature is adjusted to be close to the target blow-out temperature TAO into the vehicle interior, refrigeration in the vehicle interior is achieved.

[0150] (a-2) Cooling refrigeration mode

[0151] In the heat pump cycle 10 in the cooling refrigeration mode, the control device 60 sets the cooling expansion valve 14c to a throttling state as compared with the single cooling mode.

[0152] Therefore, in the heat pump cycle 10 in the cooling refrigeration mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single cooling mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of the water refrigerant heat exchanger 13, the heating expansion valve 14a that is fully open, the outdoor heat exchanger 15, the cooling expansion valve 14c that is in a throttling state, the cooler 20, the accumulator 23, and the suction port of the compressor 11. That is, it is switched to a refrigerant circuit in which the indoor evaporator 18 and the cooler 20 are connected in parallel with respect to the flow of the refrigerant.

[0153] In addition, in the high-temperature side heat medium circuit 30 in the cooling and refrigeration mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the independent refrigeration mode.

[0154] In addition, in the low-temperature side heat medium circuit 40 in the cooling and refrigeration mode, the control device 60 controls the operation of the heat medium three-way valve 42 to connect the outlet side of the heating passage 44a of the heat medium electric heater 44 to the inlet side of the heat medium passage of the cooler 20.

[0155] In addition, the control device 60 controls the operation of the heat medium four-way valve 43 to connect the outlet side of the heat medium three-way joint 46 to the suction port side of the second low-temperature side pump 41b while connecting the outlet side of the cooling water passage 70a of the battery 70 to the suction port side of the first low-temperature side pump 41a.

[0156] In addition, the control device 60 operates the first low-temperature side pump 41a and the second low-temperature side pump 41b to exert a predetermined reference pumping capacity for the cooling and refrigeration mode. In addition, the control device 60 stops the supply of power to the heat medium electric heater 44.

[0157] Therefore, in the low-temperature side heat medium circuit 40 in the cooling and refrigeration mode, the low-temperature side heat medium pumped from the first low-temperature side pump 41a flows in the order of the heating passage 44a of the heat medium electric heater 44, the heat medium three-way valve 42, the heat medium passage of the cooler 20, the heat medium four-way valve 43, and the suction port of the second low-temperature side pump 41b. Then, the low-temperature side heat medium pumped from the second low-temperature side pump 41b flows in the order of the cooling water passage 70a of the battery 70, the heat medium four-way valve 43, and the suction port of the first low-temperature side pump 41a.

[0158] In addition, in the indoor air-conditioning unit 50 in the cooling and refrigeration mode, the control device 60 controls the rotational speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the independent refrigeration mode. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0159] Therefore, in the heat pump cycle 10 in the cooling and refrigeration mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 and the outdoor heat exchanger 15 function as condensers, and the indoor evaporator 18 and the cooler 20 function as evaporators.

[0160] In the high-temperature side heat medium circuit 30 in the cooling and refrigeration mode, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32, similarly to the independent refrigeration mode.

[0161] In the low-temperature side heat medium circuit 40 in the cooling and refrigerating mode, the low-temperature side heat medium flowing into the heat medium passage of the cooler 20 exchanges heat with the low-pressure refrigerant decompressed by the cooling expansion valve 14c and is cooled. The low-temperature side heat medium cooled by the cooler 20 flows into the cooling water passage 70a of the battery 70 and absorbs the heat generated by the battery 70. Thereby, the battery 70 is cooled.

[0162] In the indoor air conditioner unit 50 in the cooling and refrigerating mode, similar to the single refrigerating mode, by blowing the temperature-adjusted supply air into the vehicle interior, refrigeration in the vehicle interior is thereby achieved.

[0163] (b) Dehumidifying and heating mode

[0164] The dehumidifying and heating mode is an operating mode in which the supply air cooled and dehumidified is reheated and blown into the vehicle interior, thereby performing dehumidifying and heating in the vehicle interior. In a state where the ignition switch and the air conditioner switch are turned on, when the outside air temperature Tam is in the intermediate temperature range (in this embodiment, 0 °C or higher and less than 25 °C) or the target blow-out temperature TAO is in the intermediate temperature range, the dehumidifying and heating mode is easily selected.

[0165] There are a single dehumidifying and heating mode and a cooling dehumidifying and heating mode in the dehumidifying and heating mode. The single dehumidifying and heating mode is an operating mode in which dehumidifying and heating in the vehicle interior are performed without cooling the battery 70. The cooling dehumidifying and heating mode is an operating mode in which the battery 70 is cooled and dehumidifying and heating in the vehicle interior are performed.

[0166] (b-1) Single dehumidifying and heating mode

[0167] In the heat pump cycle 10 in the single dehumidifying and heating mode, the control device 60 sets the heating expansion valve 14a to a throttling state, sets the refrigerating expansion valve 14b to a throttling state, sets the cooling expansion valve 14c to a fully closed state, and sets the bypass side flow rate adjustment valve 14d to a fully closed state. In addition, the control device 60 closes the high-pressure side on-off valve 22a and closes the low-pressure side on-off valve 22b.

[0168] Therefore, in the heat pump cycle 10 in the single dehumidifying and heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of the water-refrigerant heat exchanger 13, the heating expansion valve 14a in a throttling state, the outdoor heat exchanger 15, the refrigerating expansion valve 14b in a throttling state, the indoor evaporator 18, the accumulator 23, and the suction port of the compressor 11.

[0169] In addition, in the high-temperature side heat medium circuit 30 in the single dehumidifying and heating mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the single refrigerating mode.

[0170] In addition, in the low-temperature side heat medium circuit 40 in the separate dehumidifying and heating mode, the control device 60 stops the first low-temperature side pump 41a and the second low-temperature side pump 41b in the same manner as in the separate refrigeration mode.

[0171] In addition, in the indoor air-conditioning unit 50 in the separate dehumidifying and heating mode, the control device 60 controls the rotational speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the separate refrigeration mode. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0172] Therefore, in the heat pump cycle 10 in the separate dehumidifying and heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser and the indoor evaporator 18 functions as an evaporator.

[0173] Moreover, in the heat pump cycle 10 in the separate dehumidifying and 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 functions 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 functions as an evaporator.

[0174] In the high-temperature side heat medium circuit 30 in the separate dehumidifying and heating mode, in the same manner as in the separate refrigeration mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0175] In the indoor air-conditioning unit 50 in the separate dehumidifying and heating mode, the supply air blown from the indoor blower 52 is cooled and dehumidified in the indoor evaporator 18. The supply air cooled and dehumidified in the indoor evaporator 18 is reheated in the heater core 32 according to the opening degree of the air mixing door 54. Then, by blowing the supply air whose temperature is adjusted to be close to the target blow-out temperature TAO into the vehicle interior, dehumidifying and heating in the vehicle interior is achieved.

[0176] (b-2) Cooling dehumidifying and heating mode

[0177] In the heat pump cycle 10 in the cooling dehumidifying and heating mode, the control device 60 sets the cooling expansion valve 14c to a throttling state relative to the separate dehumidifying and heating mode.

[0178] Therefore, in the heat pump cycle 10 of the cooling dehumidifying and heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the separate dehumidifying and heating mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of the water refrigerant heat exchanger 13, the heating expansion valve 14a in a throttled state, the outdoor heat exchanger 15, the cooling expansion valve 14c in a throttled state, the cooler 20, the accumulator 23, and the suction port of the compressor 11. That is, it is switched to a refrigerant circuit in which the indoor evaporator 18 and the cooler 20 are connected in parallel with respect to the flow of the refrigerant.

[0179] In addition, in the high-temperature side heat medium circuit 30 of the cooling dehumidifying and heating mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the separate refrigeration mode.

[0180] In addition, in the low-temperature side heat medium circuit 40 of the cooling dehumidifying and heating mode, the control device 60 controls the operation of the heat medium three-way valve 42, the heat medium four-way valve 43, the first low-temperature side pump 41a, and the second low-temperature side pump 41b in the same manner as in the cooling refrigeration mode.

[0181] In addition, in the indoor air-conditioning unit 50 of the cooling dehumidifying and heating mode, the control device 60 controls the rotational speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the separate refrigeration mode. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0182] Therefore, in the heat pump cycle 10 of the cooling dehumidifying and heating mode, similar to the separate dehumidifying and heating mode, a vapor compression refrigeration cycle is constituted in which the water refrigerant heat exchanger 13 functions as a condenser and the indoor evaporator 18 and the cooler 20 function as evaporators.

[0183] Moreover, in the heat pump cycle 10 of the cooling dehumidifying and heating mode, similar to the separate dehumidifying and 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 functions 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 functions as an evaporator.

[0184] In the high-temperature side heat medium circuit 30 of the cooling dehumidifying and heating mode, similar to the separate refrigeration mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0185] In the low-temperature side heat medium circuit 40 of the cooling dehumidifying and heating mode, similar to the cooling refrigeration mode, the low-temperature side heat medium cooled by the cooler 20 flows into the cooling water passage 70a of the battery 70, whereby the battery 70 is cooled.

[0186] In the indoor air-conditioning unit 50 in the cooling and dehumidifying heating mode, similar to the separate dehumidifying heating mode, the temperature-adjusted supply air is blown into the vehicle interior, thereby achieving dehumidifying heating in the vehicle interior.

[0187] (c) Outside air heat absorption heating mode

[0188] The outside air heat absorption heating mode is an operation mode for heating the vehicle interior by blowing the heated supply air into the vehicle interior. In the state where the ignition switch and the air-conditioning switch are turned on, when the outside air temperature Tam is relatively low (in this embodiment, -10°C or higher and less than 0°C) or the target blowing temperature TAO is relatively high, the outside air heat absorption heating mode is likely to be selected.

[0189] There are a separate outside air heat absorption heating mode and a cooling outside air heat absorption heating mode in the outside air heat absorption heating mode. The separate outside air heat absorption heating mode is an operation mode for heating the vehicle interior without cooling the battery 70. The cooling outside air heat absorption heating mode is an operation mode for cooling the battery 70 and heating the vehicle interior.

[0190] (c-1) Separate outside air heat absorption heating mode

[0191] In the heat pump cycle 10 of the separate outside air heat absorption heating mode, the control device 60 sets the heating expansion valve 14a to a throttling state, sets the refrigeration expansion valve 14b to a fully closed state, sets the cooling expansion valve 14c to a fully closed state, and sets the bypass side flow rate adjustment valve 14d to a fully closed state. In addition, the control device 60 closes the high-pressure side on-off valve 22a and opens the low-pressure side on-off valve 22b.

[0192] Therefore, in the heat pump cycle 10 of the separate outside air heat absorption heating mode, the refrigerant circuit is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates in the order of the water refrigerant heat exchanger 13, the heating expansion valve 14a in a throttling state, the outdoor heat exchanger 15, the low-pressure side passage 21b, the accumulator 23, and the suction port of the compressor 11.

[0193] In addition, the control device 60 controls the rotational speed of the compressor 11 within a range not exceeding the upper limit rotational speed Nclmt so that the discharge refrigerant pressure Pd detected by the high-pressure side refrigerant temperature and pressure sensor 62b approaches the target high pressure PDO. Based on the target blowing temperature TAO, the target high pressure PDO is determined by referring to the control map pre-stored in the control device 60. In the control map, it is determined that the target high pressure PDO increases as the target blowing temperature TAO rises.

[0194] In addition, in the high-temperature side heat medium circuit 30 of the separate outside air heat absorption heating mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the separate refrigeration mode.

[0195] In addition, in the low-temperature side heat medium circuit 40 in the separate outside air heat absorption and heating mode, the control device 60 stops the first low-temperature side pump 41a and the second low-temperature side pump 41b in the same manner as in the separate refrigeration mode.

[0196] In addition, in the indoor air conditioner unit 50 in the separate outside air heat absorption and heating mode, the control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the separate refrigeration mode. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0197] Therefore, in the heat pump cycle 10 in the separate outside air heat absorption and heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser and the outdoor heat exchanger 15 functions as an evaporator.

[0198] In the high-temperature side heat medium circuit 30 in the separate outside air heat absorption and heating mode, in the same manner as in the separate refrigeration mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0199] In the indoor air conditioner unit 50 in the separate outside air heat absorption and heating mode, the supply air blown from the indoor blower 52 passes through the indoor evaporator 18. The supply air after passing through the indoor evaporator 18 is heated by the heater core 32 according to the opening degree of the air mixing door 54 to approach the target blow-out temperature TAO. Moreover, by blowing the temperature-adjusted supply air into the vehicle interior, heating of the vehicle interior is thereby achieved.

[0200] (c-2) Cooling outside air heat absorption and heating mode

[0201] In the heat pump cycle 10 in the cooling outside air heat absorption and heating mode, the control device 60 sets the cooling expansion valve 14c to a throttling state with respect to the separate outside air heat absorption and heating mode. In addition, the control device 60 opens the high-pressure side on-off valve 22a.

[0202] Therefore, in the heat pump cycle 10 in the cooling outside air heat absorption and heating mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the separate outside air heat absorption and heating mode. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of the water refrigerant heat exchanger 13, the high-pressure side passage 21a, the cooling expansion valve 14c in a throttling state, the cooler 20, the accumulator 23, and the suction port of the compressor 11. That is, it is switched to a refrigerant circuit in which the outdoor heat exchanger 15 and the cooler 20 are connected in parallel with respect to the refrigerant flow.

[0203] In addition, in the high-temperature side heat medium circuit 30 in the cooling outside air heat absorption and heating mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the separate refrigeration mode.

[0204] In addition, in the low-temperature side heat medium circuit 40 of the cooling outside air heat absorption and heating mode, the control device 60 controls the operation of the heat medium three-way valve 42, the heat medium four-way valve 43, the first low-temperature side pump 41a, and the second low-temperature side pump 41b in the same manner as in the cooling refrigeration mode.

[0205] Therefore, in the heat pump cycle 10 of the cooling outside air heat absorption and heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser, and the outdoor heat exchanger 15 and the cooler 20 function as evaporators.

[0206] In the high-temperature side heat medium circuit 30 of the cooling outside air heat absorption and heating mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32 in the same manner as in the single refrigeration mode.

[0207] In the low-temperature side heat medium circuit 40 of the cooling outside air heat absorption and heating mode, the low-temperature side heat medium cooled by the cooler 20 flows into the cooling water passage 70a of the battery 70 in the same manner as in the cooling refrigeration mode, whereby the battery 70 is cooled.

[0208] In the indoor air conditioner unit 50 of the cooling outside air heat absorption and heating mode, in the same manner as in the single outside air heat absorption and heating mode, the heated air after temperature adjustment is blown into the vehicle interior, thereby achieving heating in the vehicle interior.

[0209] (d) Hot gas heating mode

[0210] The hot gas heating mode is an operation mode for heating the vehicle interior with a heating capacity higher than that of the outside air heat absorption and heating mode. In a state where the ignition switch and the air conditioner switch are turned on, when the outside air temperature Tam is extremely low (less than -10°C in the present embodiment) or during the execution of the outside air heat absorption and heating mode, the hot gas heating mode is selected when it is determined that the heating capacity of the supply air in the heater core 32 is insufficient.

[0211] In the control program of the present embodiment, during the execution of the outside air heat absorption and heating mode, when the rotational speed of the compressor 11 reaches the upper limit rotational speed Nclmt and the supply air temperature TAV is lower than the target blow-out temperature TAO, the heating capacity of the supply air is determined to be insufficient.

[0212] In the heat pump cycle 10 of the hot gas heating mode, the control device 60 sets the heating expansion valve 14a to the fully closed state, sets the refrigeration expansion valve 14b to the fully closed state, sets the cooling expansion valve 14c to the throttling state, and sets the bypass side flow rate adjustment valve 14d to the throttling state. In addition, the control device 60 opens the high-pressure side on-off valve 22a and closes the low-pressure side on-off valve 22b.

[0213] Therefore, in the heat pump cycle 10 of the hot gas heating mode, 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 in a throttled state, the cooler 20, the accumulator 23, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched so that 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 in a throttled state disposed in the bypass passage 21c, the accumulator 23, and the suction port of the compressor 11.

[0214] In addition, the control device 60 controls the rotational speed of the compressor 11 within a range not exceeding the upper limit rotational speed Nclmt so that the suction refrigerant pressure Ps detected by the cooler side refrigerant temperature and pressure sensor 62e approaches a preset target low pressure PSO.

[0215] Here, controlling the cooler side refrigerant pressure Pc corresponding to the suction refrigerant pressure Ps to be close to a constant pressure is effective for stabilizing the discharge flow rate Gr (mass flow rate) of the compressor 11. More specifically, by making the suction refrigerant a saturated vapor refrigerant at a constant pressure, the density of the suction refrigerant is made constant. Therefore, when the suction refrigerant pressure Ps is controlled to be close to a constant pressure, it is easy to stabilize the discharge flow rate Gr of the compressor 11 at the same rotational speed.

[0216] In addition, the control device 60 controls the throttling opening of the bypass side flow control valve 14d so that the discharge refrigerant pressure Pd approaches the target high pressure PDO.

[0217] In addition, the control device 60 controls the throttling opening of the cooling expansion valve 14c so that the refrigerant on the outlet side of the cooler 20 approaches a saturated vapor refrigerant.

[0218] In addition, in the high-temperature side heat medium circuit 30 of the hot gas heating mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the independent refrigeration mode.

[0219] In addition, in the low-temperature side heat medium circuit 40 of the hot gas heating mode, the control device 60 stops the first low-temperature side pump 41a and the second low-temperature side pump 41b in the same manner as in the independent refrigeration mode.

[0220] In addition, in the indoor air conditioner unit 50 in the hot gas heating mode, the control device 60 controls the rotational speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the independent refrigeration mode. In the hot gas heating mode, the opening degree of the air mixing door 54 is mostly controlled so that substantially all of the air volume of the supply air blown from the indoor blower 52 passes through the heater core 32.

[0221] In addition, the control device 60 controls the operation of the inside / outside air switching device 53 to introduce inside air into the air-conditioning housing 51. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0222] Therefore, in the heat pump cycle 10 in the hot gas heating mode, the flow of the refrigerant discharged from the compressor 11 branches at the first three-way joint 12a. One of the refrigerants branched at the first three-way joint 12a flows into the water-refrigerant heat exchanger 13. The refrigerant that has flowed into the water-refrigerant heat exchanger 13 dissipates heat to the high-temperature side heat medium. As a result, the high-temperature side heat medium is heated.

[0223] The refrigerant flowing out of the water-refrigerant heat exchanger 13 flows into the high-pressure side passage 21a. The refrigerant that has flowed into the high-pressure side passage 21a flows into the cooling expansion valve 14c as the decompression part on the heating part side and is decompressed. The refrigerant with a lower enthalpy after being decompressed by the cooling expansion valve 14c flows into the other inflow port of the sixth three-way joint 12f.

[0224] In addition, the other refrigerant branched at the first three-way joint 12a flows into the bypass passage 21c. The refrigerant that has flowed into the bypass passage 21c is flow-adjusted by the bypass side flow adjustment valve 14d and is decompressed. The refrigerant with a higher enthalpy after being decompressed by the bypass side flow adjustment valve 14d flows into one inflow port of the sixth three-way joint 12f.

[0225] In the sixth three-way joint 12f, the flow of the refrigerant flowing out of the cooling expansion valve 14c merges with the flow of the refrigerant flowing out of the bypass side flow adjustment valve 14d and mixes. The refrigerant flowing out of the sixth three-way joint 12f flows into the cooler 20 and is further uniformly mixed. In the hot gas heating mode, the first low-temperature side pump 41a and the second low-temperature side pump 41b are stopped, so there is no heat exchange between the refrigerant and the low-temperature side heat medium in the cooler 20.

[0226] The refrigerant flowing out of the refrigerant passage of the cooler 20 flows into the accumulator 23. The gaseous refrigerant separated in the accumulator 23 flows into the compressor 11 and is compressed again.

[0227] In the high-temperature side heat medium circuit 30 in the hot gas heating mode, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 flows into the heater core 32, similarly to the single refrigeration mode.

[0228] In the in-vehicle air-conditioning unit 50 in the hot gas heating mode, similar to the single outside air heat absorption heating mode, the temperature-adjusted supply air is blown into the vehicle interior, thereby achieving heating of the vehicle interior.

[0229] Here, the hot-gas heating mode is executed when the outside air temperature Tam is extremely low. Therefore, if the refrigerant flowing out of the water-refrigerant heat exchanger 13 flows into the outdoor heat exchanger 15, the refrigerant may dissipate heat to the outside air in the outdoor heat exchanger 15. If the refrigerant dissipates heat to the outside air in the outdoor heat exchanger 15, the amount of heat dissipated from the refrigerant to the supply air in the water-refrigerant heat exchanger 13 decreases, and the heating capacity of the supply air decreases.

[0230] In contrast, in the hot-gas heating mode, the refrigerant circuit is switched so that the refrigerant flowing out of the water-refrigerant heat exchanger 13 does not flow into the outdoor heat exchanger 15. Therefore, it is possible to suppress the refrigerant from dissipating heat to the outside air in the outdoor heat exchanger 15.

[0231] Moreover, in the hot-gas heating mode, the throttle opening of the cooling expansion valve 14c is controlled so that the refrigerant on the outlet side of the cooler 20 approaches the saturated vapor refrigerant. Thus, even if the refrigerant discharge capacity of the compressor 11 is increased so that the amount of heat dissipated from the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 13 increases, the suction refrigerant sucked into the compressor 11 can be maintained in an appropriate state. Therefore, the cycle can operate stably.

[0232] As a result, in the hot-gas heating mode, even when the outside air temperature Tam becomes extremely low, the heat generated by the compression work of the compressor 11 can be effectively used to heat the supply air, and heating in the vehicle interior can be achieved.

[0233] (e) Heat-absorbing hot-gas heating mode

[0234] The heat-absorbing hot-gas heating mode is an operation mode for heating the vehicle interior with a higher heating capacity than the hot-gas heating mode. When it is determined during the execution of the hot-gas heating mode that the heating capacity of the supply air in the heater core 32 is insufficient and the heat generated by the heating unit can be used to heat the vehicle interior, the heat-absorbing hot-gas heating mode is selected.

[0235] In the control program of the present embodiment, during the execution of the hot-gas heating mode, when the rotational speed of the compressor 11 reaches the upper limit speed Nclmt and the supply air temperature TAV is lower than the target blow-out temperature TAO, the heating capacity of the supply air is determined to be insufficient.

[0236] In addition, during the execution of the hot-gas heating mode, when the inflow temperature TWLC detected by the low-temperature side heat medium temperature sensor 63b is equal to or higher than the target heat medium temperature TWLCO, it is determined that the heat generated by the heating unit can be used to heat the vehicle interior.

[0237] The heat-absorbing hot-gas heating mode includes a first heat-absorbing hot-gas heating mode and a second heat-absorbing hot-gas heating mode.

[0238] The first heat-absorbing hot-gas heating mode is an operating mode in which heating inside the vehicle compartment is performed using both the heat generated by the heat medium electric heater 44 as a highly controllable heating unit and the heat generated by the battery 70 as a lowly controllable heating unit. The first heat-absorbing hot-gas heating mode is selected when it is determined that the heat generated by the battery 70 can be used for heating inside the vehicle compartment.

[0239] The second heat-absorbing hot-gas heating mode is an operating mode in which heating inside the vehicle compartment is performed using only the heat generated by the heat medium electric heater 44. The second heat-absorbing hot-gas heating mode is selected when it is determined that the heat generated by the battery 70 can be used for heating inside the vehicle compartment.

[0240] In the control program of the present embodiment, when the battery temperature TB detected by the battery temperature sensor 64 becomes equal to or higher than a preset reference heat-absorbing temperature KTB2, it is determined that the heat generated by the battery 70 can be used for heating inside the vehicle compartment. The reference heat-absorbing temperature KTB2 is set to a value lower than the reference cooling temperature KTB1 and the target heat medium temperature TWLCO.

[0241] (e-1) The first heat-absorbing hot-gas heating mode

[0242] In the heat pump cycle 10 of the first heat-absorbing hot-gas heating mode, similar to the hot-gas heating mode, the control device 60 controls the operations of the heating expansion valve 14a, the refrigeration expansion valve 14b, the cooling expansion valve 14c, the bypass-side flow rate adjustment valve 14d, the high-pressure side on-off valve 22a, and the low-pressure side on-off valve 22b.

[0243] Therefore, in the heat pump cycle 10 of the first hot-gas heating mode, as Figure 6 shown by the solid-line arrow, the refrigerant discharged from the compressor 11 circulates in the same manner as in the hot-gas heating mode.

[0244] In addition, in the high-temperature side heat medium circuit 30 of the first heat-absorbing hot-gas heating mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the independent refrigeration mode. Therefore, in the high-temperature side heat medium circuit 30 of the first heat-absorbing hot-gas heating mode, as Figure 6 shown by the dashed-line arrow, the high-temperature side heat medium pumped by the high-temperature side pump 31 circulates in the same manner as in the independent refrigeration mode.

[0245] In addition, in the low-temperature side heat medium circuit 40 of the first heat-absorbing hot-gas heating mode, the control device 60 controls the operation of the heat medium three-way valve 42 in the same manner as in the cooling refrigeration mode to connect the outlet side of the heating passage 44a of the heat medium electric heater 44 and the inlet side of the heat medium passage of the cooler 20.

[0246] In addition, the control device 60 controls the operation of the heat medium four-way valve 43 to connect the outlet side of the heat medium three-way joint 46 and the suction port side of the second low-temperature side pump 41b, and at the same time, connect the outlet side of the cooling water passage 70a of the battery 70 and the suction port side of the first low-temperature side pump 41a.

[0247] In addition, the control device 60 operates the first low-temperature side pump 41a and the second low-temperature side pump 41b. In the first endothermic hot gas heating mode, the rotational speeds of the first low-temperature side pump 41a and the second low-temperature side pump 41b are increased as the inflow temperature TWLC rises. That is, the inflow rate of the heat medium flowing into the heat medium passage of the cooler 20 is increased as the inflow temperature TWLC rises.

[0248] In addition, the control device 60 supplies power to the heat medium electric heater 44 so that the inflow temperature TWLC becomes equal to or higher than the target heat medium temperature TWLCO.

[0249] Therefore, in the low-temperature side heat medium circuit 40 in the first endothermic hot gas heating mode, as Figure 6 shown by the dotted arrow, the low-temperature side heat medium pumped from the first low-temperature side pump 41a flows in the order of the heating passage 44a of the heat medium electric heater 44, the heat medium three-way valve 42, the heat medium passage of the cooler 20, the heat medium four-way valve 43, and the suction port of the second low-temperature side pump 41b. Moreover, the low-temperature side heat medium pumped from the second low-temperature side pump 41b flows in the order of the cooling water passage 70a of the battery 70, the heat medium four-way valve 43, and the suction port of the first low-temperature side pump 41a.

[0250] In addition, in the indoor air-conditioning unit 50 in the first endothermic hot gas heating mode, the control device 60 controls the rotational speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the single refrigeration mode. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0251] Therefore, in the heat pump cycle 10 in the first endothermic hot gas heating mode, the state of the refrigerant changes as Figure 7 shown in the Mollier diagram.

[0252] First, the flow of the discharged refrigerant discharged from the compressor 11 ( Figure 7 point a7) branches at the first three-way joint 12a. One of the refrigerants branched at the first three-way joint 12a flows into the water-refrigerant heat exchanger 13, dissipates heat to the high-temperature side heat medium, and reduces the enthalpy (from Figure 7 point a7 to point b7). As a result, the high-temperature side heat medium is heated.

[0253] 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 as a decompression part on the heating part side and is decompressed (from Figure 7 point b7 to point c7). The refrigerant with a lower enthalpy after being decompressed by the cooling expansion valve 14c flows into the other inflow port of the sixth three-way joint 12f.

[0254] In addition, the other refrigerant branched out at the first three-way joint 12a flows into the bypass passage 21c. The refrigerant flowing into the bypass passage 21c has its flow rate adjusted by the bypass side flow rate adjustment valve 14d and is decompressed (from Figure 7 point a7 to point d7). The refrigerant with a higher enthalpy after being decompressed by the bypass side flow rate adjustment valve 14d flows into one inflow port of the sixth three-way joint 12f.

[0255] In the sixth three-way joint 12f, the flow of the refrigerant flowing out of the cooling expansion valve 14c merges with the flow of the refrigerant flowing out of the bypass side flow rate adjustment valve 14d and mixes (from Figure 7 point c7 to point e7, from point d7 to point e7). The refrigerant flowing out of the sixth three-way joint 12f flows into the cooler 20 and is further uniformly mixed.

[0256] The refrigerant flowing into the cooler 20 absorbs heat from the low-temperature side heat medium and increases its enthalpy. The refrigerant flowing out of the refrigerant passage of the cooler 20 flows into the accumulator 23. The gaseous refrigerant separated in the accumulator 23 ( Figure 7 point f7) is sucked into the compressor 11 and is compressed again.

[0257] In the high-temperature side heat medium circuit 30 of the first heat absorption hot gas heating mode, similar to the single refrigeration mode, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32.

[0258] In the low-temperature side heat medium circuit 40 of the first heat absorption hot gas heating mode, the low-temperature side heat medium pumped by the first low-temperature side pump 41a is heated and its temperature rises when flowing through the heating passage 44a of the heat medium electric heater 44. The low-temperature side heat medium flowing out of the heating passage 44a flows into the heat medium passage of the cooler 20 via the heat medium three-way valve 42.

[0259] The low-temperature side heat medium flowing into the heat medium passage of the cooler 20 is cooled by the low-pressure refrigerant flowing through the refrigerant passage. The low-temperature side heat medium flowing out of the heat medium passage of the cooler 20 is sucked into the second low-temperature side pump 41b via the heat medium four-way valve 43.

[0260] The low-temperature-side heat medium pumped from the second low-temperature-side pump 41b absorbs the heat generated by the battery 70 when flowing through the cooling water passage 70a of the battery 70 and the temperature rises. The low-temperature-side heat medium flowing out from the cooling water passage 70a of the battery 70 is sucked into the first low-temperature-side pump 41a via the heat medium four-way valve 43.

[0261] That is, in the low-temperature-side heat medium circuit 40 of the first heat-absorbing hot gas heating mode, the low-temperature-side heat medium heated when flowing through the cooling water passage 70a is heated by the heat medium electric heater 44. Then, the low-temperature-side heat medium heated by the heat medium electric heater 44 flows into the cooler 20.

[0262] In the indoor air-conditioning unit 50 of the first heat-absorbing hot gas heating mode, similar to the hot gas heating mode, the temperature-adjusted supply air is blown into the vehicle interior, thereby achieving heating in the vehicle interior.

[0263] In the first heat-absorbing hot gas heating mode, the heat generated by the heat medium electric heater 44 and the battery 70 as the heating part can be used to heat the supply air. Therefore, it is possible to heat the vehicle interior with a heating capacity higher than that of the hot gas heating mode without increasing the rotational speed of the compressor 11.

[0264] (e-2) Second heat-absorbing hot gas heating mode

[0265] In the heat pump cycle 10 of the second hot gas heating mode, similar to the first hot gas heating mode, the control device 60 controls the operations of the heating expansion valve 14a, the refrigeration expansion valve 14b, the cooling expansion valve 14c, the bypass-side flow rate adjustment valve 14d, the high-pressure-side on-off valve 22a, and the low-pressure-side on-off valve 22b.

[0266] Therefore, in the heat pump cycle 10 of the second hot gas heating mode, as Figure 8 shown by the solid arrow, the refrigerant discharged from the compressor 11 circulates in the same manner as in the hot gas heating mode.

[0267] In addition, in the high-temperature-side heat medium circuit 30 of the second heat-absorbing hot gas heating mode, the control device 60 operates the high-temperature-side pump 31 in the same manner as in the single refrigeration mode. Therefore, in the high-temperature-side heat medium circuit 30 of the second heat-absorbing hot gas heating mode, as Figure 8 shown by the dashed arrow, the high-temperature-side heat medium pumped from the high-temperature-side pump 31 circulates in the same manner as in the single refrigeration mode.

[0268] In addition, in the low-temperature-side heat medium circuit 40 of the second heat-absorbing hot gas heating mode, the control device 60 controls the operation of the heat medium three-way valve 42 to connect the outlet side of the heating passage 44a of the heat medium electric heater 44 and the inlet side of the heat medium passage of the cooler 20.

[0269] In addition, the control device 60 controls the operation of the heat medium four-way valve 43 to connect the outlet side of the heat medium three-way joint 46 and the inlet side of the first low-temperature side pump 41a, and at the same time, connect the outlet side of the cooling water passage 70a of the battery 70 and the inlet side of the second low-temperature side pump 41b.

[0270] In addition, the control device 60 operates at least the first low-temperature side pump 41a. In the second endothermic hot gas heating mode, at least the rotational speed of the first low-temperature side pump 41a is increased as the inflow temperature TWLC rises. That is, the inflow flow rate is increased as the inflow temperature TWLC rises.

[0271] In addition, the control device 60 supplies power to the heat medium electric heater 44 in the same manner as in the first endothermic hot gas heating mode.

[0272] Therefore, in the low-temperature side heat medium circuit 40 of the second endothermic hot gas heating mode, as Figure 8 shown by the dotted arrow, the low-temperature side heat medium pumped from the first low-temperature side pump 41a circulates in the order of the heating passage 44a of the heat medium electric heater 44, the heat medium passage of the cooler 20, and the inlet of the first low-temperature side pump 41a.

[0273] In addition, in the indoor air conditioner unit 50 in the second endothermic hot gas heating mode, the control device 60 controls the rotational speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the single refrigeration mode. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0274] Therefore, in the heat pump cycle 10 in the second endothermic hot gas heating mode, the high-temperature side heat medium is heated in the same manner as in the first endothermic hot gas heating mode.

[0275] In the high-temperature side heat medium circuit 30 in the second endothermic hot gas heating mode, in the same manner as in the single refrigeration mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0276] In the low-temperature side heat medium circuit 40 in the second endothermic hot gas heating mode, the low-temperature side heat medium pumped from the first low-temperature side pump 41a flows into the heating passage 44a of the heat medium electric heater 44. The low-temperature side heat medium flowing into the heating passage 44a is heated and its temperature rises while flowing through the heating passage 44a. The low-temperature side heat medium flowing out of the heating passage 44a flows into the heat medium passage of the cooler 20 via the heat medium three-way valve 42.

[0277] The low-temperature side heat medium flowing into the low-temperature side of the heat medium passage of the cooler 20 is cooled by the low-pressure refrigerant flowing through the refrigerant passage. The low-temperature side heat medium flowing out of the heat medium passage of the cooler 20 is sucked into the first low-temperature side pump 41a via the heat medium four-way valve 43. That is, in the low-temperature side heat medium circuit 40 of the second heat absorption hot gas heating mode, the low-temperature side heat medium heated by the heat medium electric heater 44 is made to flow into the cooler 20.

[0278] In the indoor air-conditioning unit 50 in the second heat absorption hot gas heating mode, similar to the hot gas heating mode, the temperature-adjusted supply air is blown into the vehicle interior, thereby achieving heating in the vehicle interior.

[0279] In the second heat absorption hot gas heating mode, the heat generated by the heat medium electric heater 44 as the heating part can be used to heat the supply air. Therefore, it is possible to heat the vehicle interior with a heating capacity higher than that of the hot gas heating mode without increasing the rotational speed of the compressor 11.

[0280] Moreover, in the second heat absorption hot gas heating mode, the low-temperature side heat medium heated by the heat medium electric heater 44 is not made to flow into the cooling water passage 70a of the battery 70. Therefore, it is possible to suppress the heat generated by the heat medium electric heater 44 from being absorbed by the battery 70 with a large heat capacity.

[0281] (f) Heat absorption hot gas heating preparation mode

[0282] The heat absorption hot gas heating preparation mode is an operation mode that raises the inflow temperature TWLC. During the execution of the hot gas heating mode, even if the heating capacity of the supply air in the heater core 32 is determined to be insufficient, but when the inflow temperature TWLC is lower than the target heat medium temperature TWLCO and the heat absorption hot gas heating mode cannot be executed, the heat absorption hot gas heating preparation mode is selected.

[0283] There are a first heat absorption hot gas heating preparation mode and a second heat absorption hot gas heating preparation mode in the heat absorption hot gas heating preparation mode.

[0284] The first heat absorption hot gas heating preparation mode is an operation mode that raises the inflow temperature TWLC by using both the heat generated by the heat medium electric heater 44 and the heat generated by the battery 70. When it is determined that the heat generated by the battery 70 can be used to raise the inflow temperature TWLC, the first heat absorption hot gas heating preparation mode is selected.

[0285] The second heat absorption hot gas heating preparation mode is an operation mode that raises the inflow temperature TWLC only by using the heat generated by the heat medium electric heater 44. When it is not determined that the heat generated by the battery 70 can be used to raise the inflow temperature TWLC, the second heat absorption hot gas heating preparation mode is selected.

[0286] In the control program of the present embodiment, when the battery temperature TB detected by the battery temperature sensor 64 becomes equal to or higher than a predetermined reference heat absorption temperature KTB2, it is determined that the heat generated by the battery 70 can be used to increase the inflow temperature TWLC.

[0287] (f-1) First heat absorption hot gas heating preparation mode

[0288] In the heat pump cycle 10 of the first hot gas heating preparation mode, the control device 60 controls the operations of the heating expansion valve 14a, the refrigeration expansion valve 14b, the cooling expansion valve 14c, the bypass side flow rate adjustment valve 14d, the high-pressure side on-off valve 22a, and the low-pressure side on-off valve 22b in the same manner as in the hot gas heating mode.

[0289] Therefore, in the heat pump cycle 10 of the first hot gas heating preparation mode, as Figure 9 shown by the solid arrow, the refrigerant discharged from the compressor 11 circulates in the same manner as in the hot gas heating mode.

[0290] In addition, in the high-temperature side heat medium circuit 30 of the first hot gas heating preparation mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the independent refrigeration mode. Therefore, in the high-temperature side heat medium circuit 30 of the first heat absorption hot gas heating preparation mode, as Figure 9 shown by the dashed arrow, the high-temperature side heat medium pumped from the high-temperature side pump 31 circulates in the same manner as in the independent refrigeration mode.

[0291] In addition, in the low-temperature side heat medium circuit 40 of the first hot gas heating preparation mode, the control device 60 controls the operation of the heat medium three-way valve 42 to connect the outlet side of the heating passage 44a of the heat medium electric heater 44 and the inlet side of the heat medium bypass passage 45.

[0292] In addition, the control device 60 controls the operation of the heat medium four-way valve 43 to connect the outlet side of the heat medium three-way joint 46 and the suction inlet side of the second low-temperature side pump 41b, and at the same time, connect the outlet side of the cooling water passage 70a of the battery 70 and the suction inlet side of the first low-temperature side pump 41a.

[0293] In addition, the control device 60 operates the first low-temperature side pump 41a and the second low-temperature side pump 41b to exert a predetermined pumping capacity.

[0294] In addition, the control device 60 supplies power to the heat medium electric heater 44 so that the inflow temperature TWLC becomes equal to or higher than the target heat medium temperature TWLCO.

[0295] Therefore, in the low-temperature side heat medium circuit 40 of the first heat absorption hot gas heating preparation mode, as Figure 9As shown by the dashed arrows, the low-temperature side heat medium pumped from the first low-temperature side pump 41a and the second low-temperature side pump 41b flows in the order of the heating passage 44a of the heat medium electric heater 44, the heat medium three-way valve 42, the heat medium bypass passage 45, the heat medium four-way valve 43, and the suction port of the second low-temperature side pump 41b. Moreover, the low-temperature side heat medium pumped from the second low-temperature side pump 41b flows in the order of the cooling water passage 70a of the battery 70, the heat medium four-way valve 43, and the suction port of the first low-temperature side pump 41a.

[0296] In addition, in the indoor air-conditioning unit 50 in the first heat absorption hot gas heating preparation mode, the control device 60 controls the rotation speed of the indoor blower 52, the opening degree of the air mixing door 54, etc. in the same manner as in the single refrigeration mode. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0297] Therefore, in the heat pump cycle 10 in the first heat absorption hot gas heating preparation mode, the state of the refrigerant changes in the same manner as in the hot gas heating mode.

[0298] In the high-temperature side heat medium circuit 30 in the first heat absorption hot gas heating preparation mode, in the same manner as in the single refrigeration mode, the high-temperature side heat medium heated by the water-refrigerant heat exchanger 13 flows into the heater core 32.

[0299] In the low-temperature side heat medium circuit 40 in the first heat absorption hot gas heating preparation mode, the low-temperature side heat medium pumped from the first low-temperature side pump 41a is heated and its temperature rises when flowing through the heating passage 44a of the heat medium electric heater 44. The low-temperature side heat medium flowing out of the heating passage 44a is sucked by the second low-temperature side pump 41b via the heat medium three-way valve 42, the heat medium bypass passage 45, and the heat medium four-way valve 43.

[0300] The low-temperature side heat medium pumped from the second low-temperature side pump 41b absorbs the heat generated by the battery 70 and its temperature rises when flowing through the cooling water passage 70a of the battery 70. The low-temperature side heat medium flowing out of the cooling water passage 70a of the battery 70 is sucked into the first low-temperature side pump 41a via the heat medium four-way valve 43. As a result, the inflow temperature TWLC of the low-temperature side heat medium rises and becomes above the target heat medium temperature TWLCO.

[0301] In the indoor air-conditioning unit 50 in the first heat absorption hot gas heating preparation mode, in the same manner as in the hot gas heating mode, the temperature-adjusted supply air is blown into the vehicle interior.

[0302] Therefore, in the first heat absorption hot gas heating preparation mode, it is possible to raise the inflow temperature TWLC and quickly shift to the first heat absorption hot gas heating mode. Moreover, even if the heating capacity of the supply air is insufficient, it is possible to continue heating equivalent to the hot gas heating mode.

[0303] (f-2) Second endothermic hot gas heating preparation mode

[0304] In the heat pump cycle 10 of the second hot gas heating preparation mode, the control device 60 controls the operations of the heating expansion valve 14a, the refrigeration expansion valve 14b, the cooling expansion valve 14c, the bypass side flow adjustment valve 14d, the high-pressure side on-off valve 22a, and the low-pressure side on-off valve 22b in the same manner as in the hot gas heating mode.

[0305] Therefore, in the heat pump cycle 10 of the second hot gas heating preparation mode, as Figure 10 shown by the solid-line arrow, the refrigerant discharged from the compressor 11 circulates in the same manner as in the hot gas heating mode.

[0306] In addition, in the high-temperature side heat medium circuit 30 of the second hot gas heating preparation mode, the control device 60 operates the high-temperature side pump 31 in the same manner as in the independent refrigeration mode. Therefore, as Figure 10 shown by the dashed-line arrow, in the high-temperature side heat medium circuit 30 of the second endothermic hot gas heating preparation mode, the high-temperature side heat medium pumped from the high-temperature side pump 31 circulates in the same manner as in the independent refrigeration mode.

[0307] In addition, in the low-temperature side heat medium circuit 40 of the second hot gas heating preparation mode, the control device 60 controls the operation of the heat medium three-way valve 42 to connect the outlet side of the heating passage 44a of the heat medium electric heater 44 and the inlet side of the heat medium bypass passage 45.

[0308] In addition, the control device 60 controls the operation of the heat medium four-way valve 43 to connect the outlet side of the heat medium three-way joint 46 and the suction inlet side of the first low-temperature side pump 41a, and at the same time, connect the outlet side of the cooling water passage 70a of the battery 70 and the suction inlet side of the second low-temperature side pump 41b.

[0309] In addition, the control device 60 operates at least the first low-temperature side pump 41a to exhibit a predetermined pumping capacity.

[0310] In addition, the control device 60 supplies power to the heat medium electric heater 44 in the same manner as in the second endothermic hot gas heating preparation mode.

[0311] Therefore, in the low-temperature side heat medium circuit 40 of the second endothermic hot gas heating preparation mode, the low-temperature side heat medium pumped from the first low-temperature side pump 41a circulates as Figure 10 shown by the dashed-line arrow.

[0312] Therefore, in the heat pump cycle 10 of the second endothermic hot gas heating preparation mode, the state of the refrigerant changes in the same manner as in the hot gas heating mode.

[0313] In the high-temperature side heat medium circuit 30 in the second endothermic hot gas heating preparation mode, similar to the single refrigeration mode, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0314] In the low-temperature side heat medium circuit 40 in the second endothermic hot gas heating preparation mode, the low-temperature side heat medium pumped by the first low-temperature side pump 41a is heated and its temperature rises when flowing through the heating passage 44a of the heat medium electric heater 44. The low-temperature side heat medium flowing out of the heating passage 44a is sucked into the first low-temperature side pump 41a via the heat medium three-way valve 42 and the heat medium four-way valve 43. As a result, the inflow temperature TWLC rises to be above the target heat medium temperature TWLCO.

[0315] In the vehicle interior air conditioning unit 50 in the second endothermic hot gas heating preparation mode, similar to the hot gas heating mode, the temperature-adjusted supply air is blown into the vehicle interior.

[0316] Therefore, in the second endothermic hot gas heating preparation mode, the inflow temperature TWLC can be raised to quickly shift to the second endothermic hot gas heating mode. Moreover, even if the heating capacity of the supply air is insufficient, heating equivalent to the hot gas heating mode can be continued.

[0317] As described above, in the vehicle air conditioning device 1 of the present embodiment, by switching the operation mode, comfortable air conditioning in the vehicle interior and appropriate temperature adjustment of the battery 70 as an in-vehicle device can be performed.

[0318] Here, in the compressor 11 of the heat pump cycle 10, an upper limit speed Nclmt determined by the durability of the compressor 11 and the noise allowed by the compressor 11 is set. Therefore, in an operation mode such as the hot gas heating mode where heat generated by the compression work of the compressor 11 is used for heating in the vehicle interior, if the rotational speed of the compressor 11 reaches the upper limit speed Nclmt, the heating capacity of the supply air cannot be increased.

[0319] In contrast, in the vehicle air conditioning device 1 of the present embodiment, an endothermic hot gas heating mode can be executed. In the endothermic hot gas heating mode, heat generated by the heat medium electric heater 44 as a heat generating part and the battery 70 is absorbed by the low-pressure refrigerant decompressed by the cooling expansion valve 14c via the low-temperature side heat medium in the cooler 20.

[0320] Therefore, by increasing the heat absorption amount of the low-pressure refrigerant, the heat dissipation amount from the refrigerant to the high-temperature side heat medium can be increased without increasing the rotational speed of the compressor 11. As a result, in the endothermic hot gas heating mode, the heating capacity of the supply air can be increased more than in the hot gas heating mode without increasing the rotational speed of the compressor 11.

[0321] Further, in the endothermic hot-gas heating mode, the low-pressure refrigerant absorbs the heat generated by the heating unit. Thus, compared with the case of directly heating the high-temperature side heat medium and the supply air using the heat generated by the heating unit, the temperature of the heating unit can be made lower. Therefore, even the heat generated by the low-controllability heating unit, which is more difficult to adjust the heat generation amount compared with the high-controllability heating unit, can be easily used to heat the supply air.

[0322] In addition, in the vehicle air conditioner 1 of the present embodiment, when the inflow temperature TWLC of the low-temperature side heat medium becomes equal to or higher than the target heat medium temperature TWLCO, the circuit structure of the low-temperature side heat medium circuit 40 is switched so that the low-temperature side heat medium flows into the cooler 20. That is, when the inflow temperature TWLC of the low-temperature side heat medium becomes equal to or higher than the target heat medium temperature TWLCO, the endothermic hot-gas heating mode is executed.

[0323] Thus, the heat generated by the heat medium electric heater 44 and the battery 70, which are the heating units, can be reliably absorbed by the low-pressure refrigerant via the low-temperature side heat medium. That is, the heating ability of the supply air can be reliably improved.

[0324] In addition, in the vehicle air conditioner 1 of the present embodiment, in the first endothermic hot-gas heating mode, the low-temperature side heat medium heated by the battery 70, which is a low-controllability heating unit, is heated by the heat medium electric heater 44, which is a high-controllability heating unit. Moreover, the circuit structure of the low-temperature side heat medium circuit 40 is switched so that the low-temperature side heat medium heated by the heat medium electric heater 44 flows into the heat medium circuit of the cooler 20.

[0325] That is, in the first endothermic hot-gas heating mode, the circuit structure of the low-temperature side heat medium circuit 40 is switched so that the low-temperature side heat medium flows in the order of the cooling water passage 70a of the battery 70, the heating passage 44a of the heat medium electric heater 44, and the heat medium passage of the cooler 20. Thus, the heat generation amount of the high-controllability heating unit can be appropriately controlled according to the heat generation amount of the low-controllability heating unit.

[0326] For example, when the temperature of the low-temperature side heat medium heated by the cooling water passage 70a of the battery 70 is lower than the target heat medium temperature TWLCO, it is sufficient to supply power to the heat medium electric heater 44 so that the inflow temperature TWLC becomes equal to or higher than the target heat medium temperature TWLCO.

[0327] In addition, when the temperature of the low-temperature side heat medium heated by the cooling water passage 70a of the battery 70 is equal to or higher than the target heat medium temperature TWLCO, it is sufficient to stop the supply of power to the heat medium electric heater 44. Thus, unnecessary power consumption can be suppressed.

[0328] In addition, in the vehicle air conditioner 1 of the present embodiment, the first heat absorption hot gas heating mode and the second heat absorption hot gas heating mode are switched according to the battery temperature TB of the battery 70 which is a low controllability heat generating part. Thereby, it is possible to appropriately determine whether the heat generated by the low controllability heat generating part can be used for heating the supply air, and thus effectively utilize the heat generated by the low controllability heat generating part and the heat generated by the controllability heat generating part.

[0329] In addition, in the vehicle air conditioner 1 of the present embodiment, the target heat medium temperature TWLCO is increased as the upper limit speed Nclmt decreases. Thereby, in the heat absorption hot gas heating mode, it is possible to more appropriately control the calorific value of the high controllability heat generating part in accordance with the compression work amount that the compressor 11 can exert.

[0330] In addition, in the vehicle air conditioner 1 of the present embodiment, the low-temperature side heat medium circuit 40 has a heat medium bypass passage 45. Moreover, when the inflow temperature TWLC is lower than the target heat medium temperature TWLCO, the heat absorption hot gas heating preparation mode is executed. Thereby, during the execution of the hot gas heating mode, even if the heating ability of the supply air is insufficient, it is possible to rapidly increase the inflow temperature TWLC and shift to the heat absorption hot gas heating mode.

[0331] In addition, in the vehicle air conditioner 1 of the present embodiment, the first heat absorption hot gas heating preparation mode and the second heat absorption hot gas heating preparation mode are switched according to the battery temperature TB of the battery 70 which is a low controllability heat generating part. Thereby, it is possible to appropriately determine whether the heat generated by the low controllability heat generating part can be used to increase the inflow temperature TWLC, and thus effectively utilize the heat generated by the low controllability heat generating part and the heat generated by the high controllability heat generating part.

[0332] (Second Embodiment)

[0333] In the present embodiment, the heat pump cycle device according to the present disclosure is applied to Figure 11 the vehicle air conditioner 1a shown in the overall structure diagram. The vehicle air conditioner 1a is an air conditioner with an in-vehicle equipment temperature adjustment function similar to that of the first embodiment.

[0334] In the heat pump cycle 10 of the vehicle air conditioner 1a, the heating passage 84a of the refrigerant electric heater 84 is arranged in the refrigerant passage from the outflow port of the fifth three-way joint 12e to the inlet of the accumulator 23. The basic structure of the refrigerant electric heater 84 is the same as that of the heat medium electric heater 44 described in the first embodiment.

[0335] Therefore, the refrigerant electric heater 84 is a highly controllable heating part. Additionally, the heating passage 84a of the refrigerant electric heater 84 is a heat absorption part. More specifically, the cooler 20 of the first embodiment is a heat absorption part that indirectly absorbs the heat generated by the heat medium electric heater 44 through the low-temperature side heat medium by the low-pressure refrigerant. In contrast, the heating passage 84a of the present embodiment is a heat absorption part that directly absorbs the heat generated by the refrigerant electric heater 84 by the low-pressure refrigerant.

[0336] In addition, in the vehicle air conditioner 1a, the low-temperature side heat medium circuit 40a is adopted instead of the low-temperature side heat medium circuit 40 described in the first embodiment.

[0337] In the low-temperature side heat medium circuit 40a, the first low-temperature side pump 41a, the heat medium three-way valve 42, and the heat medium electric heater 44 are abolished. In the low-temperature side heat medium circuit 40a, a low-temperature side pump 41, a heat medium three-way valve 42, a heat medium bypass passage 45, the cooling water passage 70a of the battery 70, the heat medium passage of the cooler 20, etc. are arranged. The low-temperature side pump 41 is a low-temperature side heat medium pumping part corresponding to the second low-temperature side pump 41b of the first embodiment.

[0338] In the low-temperature side heat medium circuit 40a, 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 42. Additionally, the outlet of the heat medium three-way joint 46 is connected to the suction side of the low-temperature side pump 41.

[0339] The input side of the control device 60 of the vehicle air conditioner 1a is connected to the suction refrigerant temperature sensor 62f. The suction refrigerant temperature sensor 62f is a suction refrigerant temperature detection part that detects the suction refrigerant temperature Ts, which is the temperature of the suction refrigerant sucked by the compressor 11. Specifically, the evaporator temperature sensor 62d detects the temperature of the refrigerant in the inlet part of the accumulator 23. Other structures are the same as those of the vehicle air conditioner 1 described in the first embodiment.

[0340] Next, the operation of the vehicle air conditioner 1a of the present embodiment in the above structure will be described. In the vehicle air conditioner 1a, similar to the vehicle air conditioner 1 described in the first embodiment, it is possible to execute (a) a refrigeration mode, (b) a dehumidifying heating mode, (c) an outside air heat absorption heating mode, and (d) a hot gas heating mode.

[0341] In the above operation modes, when cooling the battery 70, the control device 60 controls the operation of the heat medium three-way valve 42 to connect the outlet side of the cooling water passage 70a of the battery 70 and the inlet side of the heat medium passage of the cooler 20. Moreover, the low-temperature side pump 41 is operated to exhibit a predetermined pumping capacity.

[0342] (e) Heat-absorbing hot-air heating mode

[0343] When it is determined that the heating capacity of the supply air in the heater core 32 is insufficient during the execution of the hot-air heating mode, the heat-absorbing hot-air heating mode of the present embodiment is selected.

[0344] (e-1) First heat-absorbing hot-air heating mode

[0345] In the heat pump cycle 10 of the first heat-absorbing hot-air heating mode, the control device 60 supplies power to the refrigerant electric heater 84.

[0346] In the low-temperature side heat medium circuit 40a of the first heat-absorbing hot-air heating mode, the control device 60 controls the operation of the heat medium three-way valve 42 to connect the outlet side of the cooling water passage 70a of the battery 70 and the inlet side of the heat medium passage of the cooler 20.

[0347] Therefore, in the low-temperature side heat medium circuit 40a, the low-temperature side heat medium pumped by the low-temperature side pump 41 circulates in the order of the cooling water passage 70a of the battery 70, the heat medium passage of the cooler 20, and the suction port of the low-temperature side pump 41. Other operations are the same as those of the first embodiment.

[0348] Therefore, in the heat pump cycle 10 of the first heat-absorbing hot-air heating mode, the refrigerant mixed at the sixth three-way joint 12f absorbs heat from the low-temperature side heat medium in the cooler 20 and the enthalpy increases. In addition, the refrigerant flowing out from the fifth three-way joint 12e is heated by the refrigerant electric heater 84 when passing through the heating passage 84a, and the enthalpy increases.

[0349] In the high-temperature side heat medium circuit 30 of the first heat-absorbing hot-air heating mode, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 flows into the heater core 32 in the same manner as in the single refrigeration mode.

[0350] In the low-temperature side heat medium circuit 40 of the first heat-absorbing hot-air heating preparation mode, the low-temperature side heat medium heated when flowing through the cooling water passage 70a of the battery 70 flows into the heat medium passage of the cooler 20.

[0351] In the indoor air conditioner unit 50 of the first heat-absorbing hot-air heating mode, the heated supply air is blown into the vehicle interior in the same manner as in the first embodiment, thereby achieving heating in the vehicle interior.

[0352] In the first heat-absorbing hot-air heating mode, the heat generated by the heat medium electric heater 44 and the battery 70 as the heating part can be used to heat the supply air. Therefore, similar to the first embodiment, heating in the vehicle interior can be performed with a heating capacity higher than that of the hot-air heating mode without increasing the rotation speed of the compressor 11.

[0353] (e-2) Second endothermic hot gas heating mode

[0354] In the heat pump cycle 10 of the second endothermic hot gas heating mode, the control device 60 supplies power to the refrigerant electric heater 84.

[0355] In the low-temperature side heat medium circuit 40a of the second endothermic hot gas heating mode, the control device 60 controls the operation of the heat medium three-way valve 42 to connect the outlet side of the cooling water passage 70a of the battery 70 and the inlet side of the heat medium bypass passage 45. Therefore, in the low-temperature side heat medium circuit 40a, the low-temperature side heat medium pumped by the low-temperature side pump 41 circulates in the order of the cooling water passage 70a of the battery 70 and the suction port of the low-temperature side pump 41. Other operations are the same as those in the first embodiment.

[0356] Therefore, in the heat pump cycle 10 of the second endothermic hot gas heating mode, the refrigerant flowing out from the fifth three-way joint 12e is heated by the refrigerant electric heater 84 when passing through the heating passage 84a, and its enthalpy increases.

[0357] In addition, in the vehicle air conditioner unit 50 of the second endothermic hot gas heating mode, similar to the first embodiment, heating in the vehicle interior is achieved by blowing the temperature-adjusted supply air into the vehicle interior.

[0358] In the second endothermic hot gas heating mode, the heat generated by the heat medium electric heater 44 as the heating part can be used to heat the supply air. Therefore, similar to the first embodiment, heating in the vehicle interior can be performed with a heating capacity higher than that in the hot gas heating mode without increasing the rotational speed of the compressor 11. In addition, in the second endothermic hot gas heating mode, the low-temperature side pump 41 can also be stopped.

[0359] As described above, in the vehicle air conditioner device 1a of the present embodiment, by switching the operation mode, comfortable air conditioning in the vehicle interior and appropriate temperature adjustment of the battery 70 as an in-vehicle device can be performed.

[0360] Moreover, in the vehicle air conditioner device 1a, the endothermic hot gas heating mode can be executed, so the same effect as that in the first embodiment can be obtained. That is, in the endothermic hot gas heating mode, the heating capacity of the supply air can be increased more than that in the hot gas heating mode without increasing the rotational speed of the compressor 11.

[0361] (Third Embodiment)

[0362] In the present embodiment, the heat pump cycle device related to the present disclosure is applied to Figure 12 the vehicle air conditioner device 1b shown in the overall structure diagram. The vehicle air conditioner device 1b is an air conditioner device with an in-vehicle device temperature adjustment function similar to that in the first embodiment. The vehicle air conditioner device 1b includes a heat pump cycle 10b.

[0363] In the heat pump cycle 10b, a receiver 24 etc. are adopted instead of a liquid reservoir 23 etc. as compared with the heat pump cycle 10 described in the first embodiment.

[0364] In the heat pump cycle 10b, the other outlet of the second three-way joint 12b is connected to the inlet side of the receiver 24. The refrigerant passage from the other outlet of the second three-way joint 12b to the inlet of the receiver 24 is the inlet side passage 21d. A first inlet side on-off valve 22c and a seventh three-way joint 12g are arranged in the inlet side passage 21d.

[0365] The receiver 24 is a high-pressure side gas-liquid separation part that separates the refrigerant flowing into the interior into gas and liquid and stores the separated liquid-phase refrigerant as the remaining refrigerant for circulation. The receiver 24 causes a part of the separated liquid-phase refrigerant to flow out to the downstream side from the liquid-phase refrigerant outlet.

[0366] 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 one inlet of the seventh three-way joint 12g. The first inlet side on-off valve 22c is a refrigerant circuit switching part.

[0367] In addition, one outlet of the second three-way joint 12b is connected to one inlet side of an eighth three-way joint 12h. A second inlet side on-off valve 22d is arranged in the refrigerant passage from one outlet of the second three-way joint 12b to one inlet of the eighth three-way joint 12h. The second inlet side on-off valve 22d opens and closes the refrigerant passage from one outlet of the second three-way joint 12b to one inlet of the eighth three-way joint 12h. The second inlet side on-off valve 22d is a refrigerant circuit switching part.

[0368] The liquid-phase refrigerant outlet of the receiver 24 is connected to one inlet side of the eighth three-way joint 12h. The refrigerant passage from the outlet of the receiver 24 to one inlet of the eighth three-way joint 12h is the outlet side passage 21e. A ninth three-way joint 12i and a third check valve 16c are arranged in the outlet side passage 21e.

[0369] The third check valve 16c allows the refrigerant to flow from the ninth three-way joint 12i 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 ninth three-way joint 12i side. The outlet of the eighth three-way joint 12h is connected to the inlet side of the heating expansion valve 14a.

[0370] The outlet on the other side of the ninth three-way joint 12i is connected to the inlet side of the thirteenth three-way joint 12j. The outlet on one side of the thirteenth three-way joint 12j is connected to the refrigerant inlet side of the indoor evaporator 18 via the refrigeration expansion valve 14b. The outlet on the other side of the thirteenth three-way joint 12j is connected to the inlet side of the other side of the sixth three-way joint 12f via the cooling expansion valve 14c.

[0371] The structure of the other vehicle air conditioner 1b is the same as that of the vehicle air conditioner 1 described in the first embodiment.

[0372] Next, the operation of the vehicle air conditioner 1b of the present embodiment in the above structure will be described. In the vehicle air conditioner 1a, various operation modes are switched in the same manner as the vehicle air conditioner 1 described in the first embodiment. Each operation mode will be described below.

[0373] (a-1) Single refrigeration mode

[0374] In the heat pump cycle 10b of the single refrigeration mode, the control device 60 sets the heating expansion valve 14a to the fully open state, sets the refrigeration expansion valve 14b to the throttling state, sets the cooling expansion valve 14c to the fully closed state, and sets the bypass side flow control valve 14d to the fully closed state. In addition, the control device 60 closes the low-pressure side on-off valve 22b, closes the first inlet side on-off valve 22c, and opens the second inlet side on-off valve 22d.

[0375] In addition, in the heat pump cycle 10b, the control device 60 controls the operation of the expansion valve in the throttling state so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a predetermined reference superheat KSH (5°C in the present embodiment).

[0376] Therefore, in the heat pump cycle 10b of the single refrigeration mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of the water refrigerant heat exchanger 13, the fully open heating expansion valve 14a, the outdoor heat exchanger 15, the receiver 24, the refrigeration expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11. Other operations are the same as those in the first embodiment.

[0377] Therefore, in the heat pump cycle 10b of the single refrigeration mode, a vapor compression refrigeration cycle is formed 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.

[0378] In addition, in the high-temperature side heat medium circuit 30 of the single refrigeration mode, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32 in the same manner as in the first embodiment.

[0379] In addition, in the indoor air-conditioning unit 50 in the single cooling mode, similar to the first embodiment, the conditioned air is blown into the vehicle interior. Thereby, cooling in the vehicle interior is achieved.

[0380] (a-2) Cooling refrigeration mode

[0381] In the heat pump cycle 10b in the cooling refrigeration mode, the control device 60 sets the cooling expansion valve 14c to a throttling state relative to the single cooling mode. Other operations are the same as those in the first embodiment.

[0382] Therefore, in the heat pump cycle 10b in the cooling refrigeration mode, a vapor compression refrigeration cycle is formed 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.

[0383] In addition, in the high-temperature side heat medium circuit 30 in the cooling refrigeration mode, similar to the first embodiment, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0384] In addition, in the low-temperature side heat medium circuit 40 in the cooling refrigeration mode, similar to the first embodiment, the low-temperature side heat medium cooled by the cooler 20 flows through the cooling water passage 70a of the battery 70. Thereby, the battery 70 is cooled.

[0385] In addition, in the indoor air-conditioning unit 50 in the cooling refrigeration mode, similar to the first embodiment, the conditioned air is blown into the vehicle interior. Thereby, cooling in the vehicle interior is achieved.

[0386] (b-1) Single dehumidification heating mode

[0387] In the heat pump cycle 10b in the single dehumidification heating mode, the control device 60 sets the heating expansion valve 14a to a throttling state, sets the cooling expansion valve 14b to a throttling state, sets the cooling expansion valve 14c to a fully closed state, and sets the bypass side flow control valve 14d to a fully closed state. In addition, the control device 60 closes the low-pressure side on-off valve 22b, closes the first inlet side on-off valve 22c, and opens the second inlet side on-off valve 22d.

[0388] Therefore, in the heat pump cycle 10b in the single dehumidification heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of the water refrigerant heat exchanger 13, the throttling heating expansion valve 14a, the outdoor heat exchanger 15, the receiver 24, the cooling expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11. Other operations are the same as those in the first embodiment.

[0389] Therefore, in the heat pump cycle 10b of the separate dehumidification and heating mode, a vapor compression refrigeration cycle is formed 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.

[0390] In addition, in the high-temperature side heat medium circuit 30 of the separate dehumidification and heating mode, similar to the first embodiment, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0391] In addition, in the indoor air conditioning unit 50 of the separate dehumidification and heating mode, similar to the first embodiment, the air conditioner that has been dehumidified and temperature-adjusted is blown into the vehicle interior. Thereby, dehumidification and heating in the vehicle interior are achieved.

[0392] Here, the heat pump cycle 10b has a receiver 24. Therefore, the dehumidification and 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 outside air temperature Tam.

[0393] (b-2) Cooling dehumidification and heating mode

[0394] In the heat pump cycle 10b of the cooling dehumidification and heating mode, the control device 60 sets the cooling expansion valve 14c to a throttling state with respect to the separate dehumidification and heating mode. Other operations are the same as those of the first embodiment.

[0395] Therefore, in the heat pump cycle 10b of the cooling dehumidification and heating mode, a vapor compression refrigeration cycle is formed 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.

[0396] In addition, in the high-temperature side heat medium circuit 30 of the cooling dehumidification and heating mode, similar to the first embodiment, the high-temperature side heat medium heated by the water refrigerant heat exchanger 13 flows into the heater core 32.

[0397] In addition, in the low-temperature side heat medium circuit 40 of the cooling dehumidification and heating mode, similar to the first embodiment, the low-temperature side heat medium cooled by the cooler 20 flows through the cooling water passage 70a of the battery 70. Thereby, the battery 70 is cooled.

[0398] In addition, in the indoor air conditioning unit 50 of the cooling dehumidification and heating mode, similar to the first embodiment, the air conditioner that has been dehumidified and temperature-adjusted is blown into the vehicle interior. Thereby, dehumidification and heating in the vehicle interior are achieved.

[0399] (c-1) Separate outside air heat absorption and heating mode

[0400] In the heat pump cycle 10b in the separate outside air heat absorption and heating mode, the control device 60 sets the heating expansion valve 14a to the throttling state, sets the refrigerating expansion valve 14b to the fully closed state, sets the cooling expansion valve 14c to the fully closed state, and sets the bypass side flow rate adjustment valve 14d to the fully closed state. In addition, the control device 60 opens the low-pressure side opening and closing valve 22b, opens the first inlet side opening and closing valve 22c, and closes the second inlet side opening and closing valve 22d.

[0401] Therefore, in the heat pump cycle 10b in the separate outside air heat absorption and heating mode, the refrigerant discharged from the compressor 11 is switched to circulate in the refrigerant circuit in the order of the water refrigerant heat exchanger 13, the inlet side passage 21d, the receiver 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. Other operations are the same as those in the first embodiment.

[0402] Therefore, in the heat pump cycle 10b in the separate outside air heat absorption and heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser and the outdoor heat exchanger 15 functions as an evaporator.

[0403] In addition, in the high-temperature side heat medium circuit 30 in the separate outside air heat absorption and heating mode, similar to the first embodiment, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32.

[0404] In addition, in the indoor air conditioner unit 50 in the separate outside air heat absorption and heating mode, similar to the first embodiment, the air with adjusted temperature is blown into the vehicle interior by the air-conditioning air guide vane. Thereby, heating in the vehicle interior is achieved.

[0405] (c-2) Cooling outside air heat absorption and heating mode

[0406] In the heat pump cycle 10b in the cooling outside air heat absorption and heating mode, the control device 60 sets the cooling expansion valve 14c to the throttling state as compared with the separate outside air heat absorption and heating mode. Other operations are the same as those in the first embodiment.

[0407] Therefore, in the heat pump cycle 10b in the cooling outside air heat absorption and heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser and the outdoor heat exchanger 15 and the cooler 20 function as evaporators.

[0408] In addition, in the high-temperature side heat medium circuit 30 in the cooling outside air heat absorption and heating mode, similar to the first embodiment, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32.

[0409] In addition, in the low-temperature side heat medium circuit 40 of the cooling outside air heat absorption and heating mode, similar to the first embodiment, the low-temperature side heat medium cooled by the cooler 20 flows through the cooling water passage 70a of the battery 70. As a result, the battery 70 is cooled.

[0410] In addition, in the indoor air-conditioning unit 50 of the cooling outside air heat absorption and heating mode, similar to the first embodiment, the air-conditioning wind direction adjusted in temperature is blown into the vehicle interior. As a result, heating of the vehicle interior is achieved.

[0411] (d) Hot gas heating mode

[0412] In the heat pump cycle 10b of the hot gas heating mode, the control device 60 sets the heating expansion valve 14a to the fully closed state, sets the refrigeration expansion valve 14b to the fully closed state, sets the cooling expansion valve 14c to the throttling state, and sets the bypass side flow rate adjustment valve 14d to the throttling state. In addition, the control device 60 closes the low-pressure side opening and closing valve 22b, opens the first inlet side opening and closing valve 22c, and closes the second inlet side opening and closing valve 22d.

[0413] Therefore, in the heat pump cycle 10b of the hot gas heating mode, 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 receiver 24, the cooling expansion valve 14c, the sixth three-way joint 12f, the cooler 20, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched to the refrigerant that circulates in the order of the first three-way joint 12a, the bypass side flow rate adjustment valve 14d disposed in the bypass passage 21c, the sixth three-way joint 12f, and the suction port of the compressor 11. Other operations are the same as those of the first embodiment.

[0414] Therefore, in the heat pump cycle 10b of the hot gas heating mode, similar to the first embodiment, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 13.

[0415] In the high-temperature side heat medium circuit 30 of the hot gas heating mode, similar to the first embodiment, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 13 flows into the heater core 32.

[0416] In the indoor air-conditioning unit 50 of the hot gas heating mode, similar to the first embodiment, the air-conditioning wind direction adjusted in temperature is blown into the vehicle interior. As a result, heating of the vehicle interior is achieved.

[0417] (e) Heat absorption hot gas heating mode

[0418] In the heat pump cycle 10b of the first heat-absorbing hot-gas heating mode and the second heat-absorbing hot-gas heating mode, the control device 60 controls the operations of the heating expansion valve 14a, the refrigerating expansion valve 14b, the cooling expansion valve 14c, the bypass-side flow adjustment valve 14d, the low-pressure side on-off valve 22b, the first inlet side on-off valve 22c, and the second inlet side on-off valve 22d in the same manner as in the hot-gas heating mode. Other operations are the same as those in the first embodiment.

[0419] Therefore, in the first heat-absorbing hot-gas heating mode and the second heat-absorbing hot-gas heating mode, as in the first embodiment, the heating inside the vehicle compartment can be performed with a heating capacity higher than that in the hot-gas heating mode.

[0420] (f) Heat-absorbing hot-gas heating preparation mode

[0421] In the heat pump cycle 10b of the first heat-absorbing hot-gas heating preparation mode and the second heat-absorbing hot-gas heating preparation mode, the control device 60 controls the operations of the heating expansion valve 14a, the refrigerating expansion valve 14b, the cooling expansion valve 14c, the bypass-side flow adjustment valve 14d, the low-pressure side on-off valve 22b, the first inlet side on-off valve 22c, and the second inlet side on-off valve 22d in the same manner as in the hot-gas heating mode. Other operations are the same as those in the first embodiment.

[0422] Therefore, in the first heat-absorbing hot-gas heating preparation mode and the second heat-absorbing hot-gas heating preparation mode, as in the first embodiment, the inflow temperature TWLC of the low-temperature side heat medium can be increased, and the heating equivalent to that in the hot-gas heating mode can be continued.

[0423] As described above, in the vehicle air conditioner 1b of the present embodiment, by switching the operation mode, comfortable air conditioning inside the vehicle compartment and appropriate temperature adjustment of the battery 70 as an in-vehicle device can be performed.

[0424] Moreover, in the vehicle air conditioner 1b, the heat-absorbing hot-gas heating mode can be executed, so the same effects as those in the first embodiment can be obtained. That is, in the heat-absorbing hot-gas heating mode, the heating capacity of the supply air can be increased more than that in the hot-gas heating mode without increasing the rotational speed of the compressor 11.

[0425] (Fourth embodiment)

[0426] In the present embodiment, the heat pump cycle device related to the present disclosure is applied to Figure 13 the vehicle air conditioner 1c shown in the overall structure diagram. The vehicle air conditioner 1c is an air conditioner with an in-vehicle device temperature adjustment function similar to that in the first embodiment. The vehicle air conditioner 1c includes a heat pump cycle 10c, a high-temperature side heat medium circuit 30c, and a low-temperature side heat medium circuit 40c.

[0427] In the heat pump cycle 10c of the present embodiment, compared with the heat pump cycle 10b described in the third embodiment, the heating expansion valve 14a, the outdoor heat exchanger 15, the low-pressure side passage 21b, the inlet side passage 21d, the outlet side passage 21e, etc. are eliminated.

[0428] In addition, in the heat pump cycle 10c, the outlet side of the refrigerant passage of the water refrigerant heat exchanger 13 is connected to the inlet side of the receiver 24. The outlet of the receiver 24 is connected to the inlet side of the thirteenth joint 12j. The structure of the other heat pump cycle 10c is the same as that of the heat pump cycle 10b described in the third embodiment.

[0429] In the high-temperature side heat medium circuit 30c, compared with the high-temperature side heat medium circuit 30 described in the first embodiment, a high-temperature side three-way flow control valve 33 and a high-temperature side radiator 34 are added.

[0430] The high-temperature side three-way flow control valve 33 is a three-way type flow control unit that can continuously adjust the flow ratio of the high-temperature side heat medium flowing out of the heat medium passage of the water refrigerant heat exchanger 13 between the heat medium flowing into the heater core 32 and the heat medium flowing into the high-temperature side radiator 34. The high-temperature side three-way flow control valve 33 is controlled by a control signal output from the control device 60.

[0431] The high-temperature side three-way flow control valve 33 can make all the flow of the high-temperature side heat medium flowing out of the heat medium passage of the water refrigerant heat exchanger 13 flow into the heater core 32. In addition, the high-temperature side three-way flow control valve 33 can make all the flow of the high-temperature side heat medium flowing out of the heat medium passage of the water refrigerant heat exchanger 13 flow into the high-temperature side radiator 34.

[0432] The high-temperature side radiator 34 is a high-temperature side water-air heat exchange unit that exchanges heat between the high-temperature side heat medium flowing out of the high-temperature side three-way flow control valve 33 and the outside air. The high-temperature side radiator 34 is arranged on the front side of the drive device chamber.

[0433] The heat medium outlet of the high-temperature side radiator 34 is connected to one of the inlet sides of the high-temperature side heat medium three-way joint 35. In addition, in the present embodiment, the heat medium outlet of the heater core 32 is connected to the other inlet side of the high-temperature side heat medium three-way joint 35. The outlet of the high-temperature side heat medium three-way joint 35 is connected to the suction side of the high-temperature side pump 31.

[0434] In the low-temperature side heat medium circuit 40c, compared with the low-temperature side heat medium circuit 40 described in the first embodiment, a low-temperature side three-way flow control valve 47, a low-temperature side radiator 48, and a third low-temperature side pump 41c are added.

[0435] The low-temperature-side three-way flow control valve 47 is a three-way flow control section that can continuously adjust the flow rate ratio of the hot medium flowing into the first low-temperature-side hot medium three-way joint 46a to the hot medium flowing into the third low-temperature-side pump 41c in the low-temperature-side hot medium flowing out of the hot medium passage of the cooler 20. The basic structure of the low-temperature-side three-way flow control valve 47 is the same as that of the high-temperature-side three-way flow control valve 33. Therefore, the low-temperature-side three-way flow control valve 47 also functions as a hot medium circuit switching section.

[0436] The first low-temperature-side hot medium three-way joint 46a is a three-way joint corresponding to the hot medium three-way joint 46 described in the first embodiment. The third low-temperature-side pump 41c is a low-temperature-side hot medium pumping section that sucks the low-temperature-side hot medium flowing out of the low-temperature-side three-way flow control valve 47 and pumps it to the hot medium inlet side of the low-temperature-side radiator 48. The basic structure of the third low-temperature-side pump 41c is the same as that of the first low-temperature-side pump 41a.

[0437] The low-temperature-side radiator 48 is a low-temperature-side water-air heat exchange section that exchanges heat between the low-temperature-side hot medium pumped by the third low-temperature-side pump 41c and the outside air. The low-temperature-side radiator 48 and the high-temperature-side radiator 34 are arranged on the front side of the drive device room.

[0438] The hot medium outlet of the low-temperature-side radiator 48 is connected to one of the inflow port sides of the second low-temperature-side hot medium three-way joint 46b. In addition, in this embodiment, one of the outflow ports of the hot medium three-way valve 42 is connected to the other inflow port side of the second low-temperature-side hot medium three-way joint 46b. The outflow port of the second low-temperature-side hot medium three-way joint 46b is connected to the inlet side of the hot medium passage of the cooler 20.

[0439] The structure of the other vehicle air conditioner 1c is the same as that of the vehicle air conditioner 1 described in the first embodiment.

[0440] Next, the operation of the vehicle air conditioner 1b in the above structure will be described. In the vehicle air conditioner 1a, various operation modes are switched in the same manner as the vehicle air conditioner 1 described in the first embodiment. Hereinafter, each operation mode will be described.

[0441] (a-1) Single refrigeration mode

[0442] In the heat pump cycle 10c of the single refrigeration mode, the control device 60 sets the refrigeration expansion valve 14b to the throttling state, sets the cooling expansion valve 14c to the fully closed state, and sets the bypass-side flow control valve 14d to the fully closed state.

[0443] In addition, in the heat pump cycle 10c, the control device 60 controls the operation of the expansion valve in a throttling state so that the superheat SH of the refrigerant sucked into the compressor 11 approaches a predetermined reference superheat KSH (5°C in this embodiment).

[0444] Therefore, in the heat pump cycle 10c in the single cooling mode, the refrigerant circuit is switched to circulate in the order of the water refrigerant heat exchanger 13, the receiver 24, the refrigeration expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11 for the refrigerant discharged from the compressor 11.

[0445] In addition, in the high-temperature side heat medium circuit 30c in the single cooling mode, the control device 60 operates the high-temperature side pump 31 to exhibit a predetermined reference pumping capacity. In addition, the control device 60 controls the operation of the high-temperature side three-way flow control valve 33 so that the high-temperature side heat medium temperature TWH detected by the high-temperature side heat medium temperature sensor 63a approaches the predetermined reference high-temperature side heat medium temperature KTWH heater core.

[0446] In addition, in the low-temperature side heat medium circuit 40c in the single cooling mode, the control device 60 stops the first low-temperature side pump 41a, the second low-temperature side pump 41b, and the third low-temperature side pump 41c.

[0447] In addition, in the indoor air conditioner unit 50 in the single cooling mode, the control device 60 controls the rotational speed of the indoor blower 52 and the opening degree of the air mixing door 54 in the same manner as in the first embodiment. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0448] Therefore, in the heat pump cycle 10c in the single cooling mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser and the indoor evaporator 18 functions as an evaporator.

[0449] In the high-temperature side heat medium circuit 30 in the single cooling mode, the high-temperature side heat medium flowing into the heat medium passage of the water refrigerant heat exchanger 13 exchanges heat with the refrigerant discharged from the compressor 11 and is heated. The high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32 according to the opening degree of the high-temperature side three-way flow control valve 33.

[0450] In the indoor air conditioner unit 50 in the single cooling mode, in the same manner as in the first embodiment, the conditioned air is blown into the vehicle interior. Thereby, cooling of the vehicle interior is achieved. In addition, in the single cooling mode of this embodiment, as the target blow-out temperature TAO rises, the high-temperature side three-way flow control valve 33 of the high-temperature side heat medium circuit 30c increases the flow rate of the high-temperature side heat medium flowing into the heater core 32, and thus dehumidification and heating of the vehicle interior can also be performed.

[0451] (a-2) Cooling and refrigeration mode

[0452] In the heat pump cycle 10c of the cooling and refrigeration mode, the control device 60 sets the cooling expansion valve 14c to a throttling state relative to the single refrigeration mode. The operation of the other heat pump cycle 10c is the same as that of the single refrigeration mode.

[0453] Therefore, in the heat pump cycle 10c of the cooling and refrigeration mode, the refrigerant discharged from the compressor 11 circulates in the same manner as in the single refrigeration mode. At the same time, the refrigerant circuit is switched to the one in which the refrigerant discharged from the compressor 11 circulates in the order of the water refrigerant heat exchanger 13, the receiver 24, the cooling expansion valve 14c, the cooler 20, and the suction port of the compressor 11. That is, the refrigerant circuit is switched to the one in which the indoor evaporator 18 and the cooler 20 are connected in parallel with respect to the flow of the refrigerant.

[0454] In addition, in the high-temperature side heat medium circuit 30c of the cooling and refrigeration mode, the control device 60 controls the operations of the high-temperature side pump 31 and the high-temperature side three-way flow control valve 33 in the same manner as in the single refrigeration mode.

[0455] In addition, in the low-temperature side heat medium circuit 40c of the cooling and refrigeration mode, the control device 60 controls the operation of the low-temperature side three-way flow control valve 47 so that all the flow of the low-temperature side heat medium flowing out of the cooler 20 flows into the first low-temperature side heat medium three-way joint 46a. In addition, the control device 60 stops the third low-temperature side pump 41c.

[0456] In addition, the control device 60 controls the operations of the first low-temperature side pump 41a, the second low-temperature side pump 41b, the heat medium three-way valve 42, and the heat medium four-way valve 43 in the same manner as in the first embodiment.

[0457] In addition, in the indoor air-conditioning unit 50 of the cooling and refrigeration mode, the control device 60 controls the rotational speed of the indoor blower 52 and the opening degree of the air mixing door 54 in the same manner as in the first embodiment. Moreover, the control device 60 appropriately controls the operations of other controlled devices.

[0458] Therefore, in the heat pump cycle 10c of the cooling and refrigeration mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser, and the indoor evaporator 18 and the cooler 20 function as evaporators.

[0459] In the high-temperature side heat medium circuit 30c of the cooling and refrigeration mode, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32 according to the opening degree of the high-temperature side three-way flow control valve 33, the same as in the single refrigeration mode.

[0460] In the low-temperature side heat medium circuit 40c in the cooling and refrigeration mode, similar to the first embodiment, the low-temperature side heat medium cooled by the cooler 20 flows through the cooling water passage 70a of the battery 70. Thus, the battery 70 is cooled.

[0461] In addition, in the in-vehicle air-conditioning unit 50 in the independent refrigeration mode, similar to the first embodiment, the air-conditioning air whose temperature has been adjusted is blown into the vehicle interior. Thus, refrigeration in the vehicle interior is achieved. In addition, in the cooling and refrigeration mode of the present embodiment, similar to the independent refrigeration mode, dehumidification and heating in the vehicle interior can be performed.

[0462] (c-1) Independent outside air heat absorption and heating mode

[0463] In the heat pump cycle 10c in the independent outside air heat absorption and heating mode, the control device 60 sets the refrigerant expansion valve 14b for refrigeration to the fully closed state, sets the refrigerant expansion valve 14c for cooling to the throttling state, and sets the bypass side flow rate adjustment valve 14d to the fully closed state.

[0464] Therefore, in the heat pump cycle 10c in the independent outside air heat absorption and heating mode, the refrigerant circuit is switched to the one in which the refrigerant discharged from the compressor 11 circulates in the order of the water refrigerant heat exchanger 13, the receiver 24, the refrigerant expansion valve 14c for cooling, the cooler 20, and the suction port of the compressor 11.

[0465] In addition, in the high-temperature side heat medium circuit 30c in the independent outside air heat absorption and heating mode, the control device 60 controls the operations of the high-temperature side pump 31 and the high-temperature side three-way flow rate adjustment valve 33 in the same manner as in the independent refrigeration mode.

[0466] In addition, in the low-temperature side heat medium circuit 40c in the independent outside air heat absorption and heating mode, the control device 60 controls the operation of the low-temperature side three-way flow rate adjustment valve 47 so that all the flow rate of the low-temperature side heat medium flowing out from the cooler 20 flows into the third low-temperature side pump 41c.

[0467] In addition, the control device 60 stops the first low-temperature side pump 41a and the second low-temperature side pump 41b. In addition, the control device 60 operates the third low-temperature side pump 41c to exhibit a predetermined reference pumping capacity.

[0468] In addition, in the in-vehicle air-conditioning unit 50 in the independent outside air heat absorption and heating mode, the control device 60 controls the rotational speed of the in-vehicle blower 52 and the opening degree of the air mixing door 54 in the same manner as in the first embodiment. Moreover, the control device 60 appropriately controls the operations of other controlled devices.

[0469] Therefore, in the heat pump cycle 10c in the independent outside air heat absorption and heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser and the cooler 20 functions as an evaporator.

[0470] In the high-temperature side heat medium circuit 30c in the separate outside air heat absorption and heating mode, similar to the separate refrigeration mode, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32 according to the opening degree of the high-temperature side three-way flow control valve 33.

[0471] In the low-temperature side heat medium circuit 40c in the cooling and refrigeration mode, the low-temperature side heat medium cooled in the cooler 20 is sucked into the third low-temperature side pump 41c via the low-temperature side three-way flow control valve 47. The low-temperature low-temperature side heat medium pumped from the third low-temperature side pump 41c flows into the low-temperature side radiator 48. The low-temperature side heat medium flowing into the low-temperature side radiator 48 absorbs heat from the outside air.

[0472] The low-temperature side heat medium whose enthalpy has risen in the low-temperature side radiator 48 flows into the heat medium passage of the cooler 20. In the cooler 20, the low-pressure refrigerant exchanges heat with the low-temperature side heat medium. Thereby, the low-pressure refrigerant absorbs the heat possessed by the low-temperature side heat medium (i.e., the heat absorbed by the low-temperature side heat medium from the outside air).

[0473] In addition, in the indoor air conditioner unit 50 in the separate refrigeration mode, similar to the first embodiment, the air-conditioning wind direction adjusted in temperature is blown into the vehicle interior. Thereby, heating in the vehicle interior is achieved.

[0474] (c-2) Cooling outside air heat absorption and heating mode

[0475] In the heat pump cycle 10c in the cooling outside air heat absorption and heating mode, similar to the separate outside air heat absorption and heating mode, the control device 60 sets the refrigeration expansion valve 14b to the fully closed state, sets the cooling expansion valve 14c to the throttling state, and sets the bypass side flow control valve 14d to the fully closed state.

[0476] In addition, in the high-temperature side heat medium circuit 30c in the cooling outside air heat absorption and heating mode, the control device 60 controls the operations of the high-temperature side pump 31 and the high-temperature side three-way flow control valve 33 in the same manner as in the separate refrigeration mode.

[0477] In addition, in the low-temperature side heat medium circuit 40c in the cooling outside air heat absorption and heating mode, the control device 60 controls the operation of the low-temperature side three-way flow control valve 47 so that the low-temperature side heat medium flowing out of the cooler 20 flows into both the first low-temperature side heat medium three-way joint 46a and the third low-temperature side pump 41c. In addition, the control device 60 operates the third low-temperature side pump 41c to exhibit a predetermined reference pumping capacity.

[0478] In addition, the control device 60 controls the operations of the first low-temperature side pump 41a, the second low-temperature side pump 41b, the heat medium three-way valve 42, and the heat medium four-way valve 43 in the same manner as in the first embodiment.

[0479] In addition, in the indoor air-conditioning unit 50 in the cooling outside air heat absorption heating mode, the control device 60 controls the rotational speed of the indoor blower 52 and the opening degree of the air mixing door 54 in the same manner as in the first embodiment. Moreover, the control device 60 appropriately controls the operation of other controlled devices.

[0480] Therefore, in the heat pump cycle 10c in the cooling outside air heat absorption heating mode, similar to the separate outside air heat absorption heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 13 functions as a condenser and the cooler 20 functions as an evaporator.

[0481] In the high-temperature side heat medium circuit 30c in the cooling outside air heat absorption heating mode, similar to the separate refrigeration mode, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32 according to the opening degree of the high-temperature side three-way flow control valve 33.

[0482] In the low-temperature side heat medium circuit 40c in the cooling outside air heat absorption heating mode, the low-temperature side heat medium that has flowed into the first low-temperature side heat medium three-way joint 46a from the low-temperature side three-way flow control valve 47 circulates through the cooling water passage 70a of the battery 70. As a result, the battery 70 is cooled. In addition, the low-temperature side heat medium that has flowed into the third low-temperature side pump 41c from the low-temperature side three-way flow control valve 47 absorbs the heat possessed by the outside air in the low-temperature side radiator 48.

[0483] In addition, in the indoor air-conditioning unit 50 in the cooling outside air heat absorption heating mode, similar to the first embodiment, the air-conditioning air whose temperature has been adjusted is blown into the vehicle interior. As a result, heating in the vehicle interior is achieved.

[0484] (d) Hot gas heating mode

[0485] In the heat pump cycle 10c in the hot gas heating mode, the control device 60 sets the refrigeration expansion valve 14b to the fully closed state, sets the cooling expansion valve 14c to the throttling state, and sets the bypass side flow control valve 14d to the throttling state.

[0486] Therefore, in the heat pump cycle 10c in the hot gas heating mode, 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 receiver 24, the cooling expansion valve 14c, the sixth three-way joint 12f, the cooler 20, and the suction port of the compressor 11. At the same time, the refrigerant circuit is switched so that 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 disposed in the bypass passage 21c, the sixth three-way joint 12f, and the suction port of the compressor 11.

[0487] In addition, in the high-temperature side heat medium circuit 30c in the hot gas heating mode, the control device 60 controls the operations of the high-temperature side pump 31 and the high-temperature side three-way flow control valve 33 in the same manner as in the independent refrigeration mode.

[0488] In addition, in the low-temperature side heat medium circuit 40c in the hot gas heating mode, the control device 60 stops the first low-temperature side pump 41a, the second low-temperature side pump 41b, and the third low-temperature side pump 41c in the same manner as in the independent refrigeration mode.

[0489] In addition, in the indoor air conditioner unit 50 in the hot gas heating mode, the control device 60 controls the rotational speed of the indoor blower 52 and the opening degree of the air mixing door 54 in the same manner as in the first embodiment. Moreover, the control device 60 appropriately controls the operations of other controlled devices.

[0490] Therefore, in the heat pump cycle 10b in the hot gas heating mode, similar to the first embodiment, the high-temperature side heat medium is heated in the water refrigerant heat exchanger 13.

[0491] In addition, in the high-temperature side heat medium circuit 30c in the hot gas heating mode, similar to the independent refrigeration mode, the high-temperature side heat medium heated in the water refrigerant heat exchanger 13 flows into the heater core 32 according to the opening degree of the high-temperature side three-way flow control valve 33.

[0492] In the indoor air conditioner unit 50 in the hot gas heating mode, similar to the first embodiment, the conditioned air is blown into the vehicle interior. Thereby, heating of the vehicle interior is achieved.

[0493] (e) Heat-absorbing hot gas heating mode

[0494] In the heat pump cycle 10c of the first heat-absorbing hot gas heating mode and the second heat-absorbing hot gas heating mode, the control device 60 controls the operations of the refrigeration expansion valve 14b, the cooling expansion valve 14c, and the bypass side flow control valve 14d in the same manner as in the hot gas heating mode.

[0495] In addition, in the high-temperature side heat medium circuit 30c of the first heat-absorbing hot gas heating mode and the second heat-absorbing hot gas heating mode, the control device 60 controls the operations of the high-temperature side pump 31 and the high-temperature side three-way flow control valve 33 in the same manner as in the independent refrigeration mode.

[0496] In addition, in the low-temperature side heat medium circuit 40c of the first heat-absorbing hot gas heating mode and the second heat-absorbing hot gas heating mode, the control device 60 controls the operation of the low-temperature side three-way flow control valve 47 so that all the flow rate of the low-temperature side heat medium flowing out from the cooler 20 flows into the first low-temperature side heat medium three-way joint 46a. In addition, the control device 60 stops the third low-temperature side pump 41c.

[0497] In addition, the control device 60 controls the operations of the first low-temperature side pump 41a, the second low-temperature side pump 41b, the heat medium three-way valve 42, and the heat medium four-way valve 43 in the same manner as in the first embodiment.

[0498] Therefore, in the first heat-absorbing hot gas heating mode and the second heat-absorbing hot gas heating mode, similar to the first embodiment, it is possible to heat the interior of the vehicle with a heating capacity higher than that of the hot gas heating mode without increasing the rotational speed of the compressor 11.

[0499] (f) Heat-absorbing hot gas heating preparation mode

[0500] In the heat pump cycle 10c of the first heat-absorbing hot gas heating mode and the second heat-absorbing hot gas heating mode, the control device 60 controls the operations of the refrigerant expansion valve 14b, the cooling expansion valve 14c, and the bypass side flow rate adjustment valve 14d in the same manner as in the hot gas heating mode.

[0501] In addition, in the high-temperature side heat medium circuit 30c of the first heat-absorbing hot gas heating mode and the second heat-absorbing hot gas heating mode, the control device 60 controls the operations of the high-temperature side pump 31 and the high-temperature side three-way flow rate adjustment valve 33 in the same manner as in the independent refrigeration mode.

[0502] In addition, in the low-temperature side heat medium circuit 40c of the first heat-absorbing hot gas heating mode and the second heat-absorbing hot gas heating mode, the control device 60 controls the operation of the low-temperature side three-way flow rate adjustment valve 47 so that all the flow rate of the low-temperature side heat medium flowing out from the cooler 20 flows into the first low-temperature side heat medium three-way joint 46a. In addition, the control device 60 stops the third low-temperature side pump 41c.

[0503] In addition, the control device 60 controls the operations of the first low-temperature side pump 41a, the second low-temperature side pump 41b, the heat medium three-way valve 42, and the heat medium four-way valve 43 in the same manner as in the first embodiment.

[0504] Therefore, in the first heat-absorbing hot gas heating preparation mode and the second heat-absorbing hot gas heating preparation mode, similar to the first embodiment, it is possible to increase the inflow temperature TWLC of the low-temperature side heat medium and continue heating equivalent to that of the hot gas heating mode.

[0505] As described above, in the vehicle air conditioner 1c of the present embodiment, by switching the operation mode, it is possible to perform comfortable air conditioning in the vehicle interior and appropriately adjust the temperature of the battery 70 as an in-vehicle device.

[0506] Moreover, in the vehicle air conditioner 1c, the heat-absorbing hot gas heating mode can be executed, so the same effects as those of the first embodiment can be obtained. In the heat-absorbing hot gas heating mode, it is possible to increase the heating capacity of the supply air more than that of the hot gas heating mode without increasing the rotational speed of the compressor 11.

[0507] The present disclosure is not limited to the above-described embodiments, and various modifications can be made as follows without departing from the gist of the present disclosure.

[0508] In the above-described embodiment, an example in which the heat pump cycle device according to the present disclosure is applied to a vehicle air conditioner has been described, but the application target of the heat pump cycle device is not limited to the vehicle air conditioner. For example, as an object to be heated, it can also be applied to a water heater device for heating domestic hot water, etc.

[0509] The structure of the heat pump cycle device according to the present disclosure is not limited to the structure disclosed in the above-described embodiment.

[0510] In the above-described embodiment, an example in which the battery 70, which is the temperature adjustment object of the vehicle air conditioner, is used as a low controllability heat generating part has been described, but the low controllability heat generating part is not limited to the battery 70. For example, in the case where the heat pump cycle device is applied to a vehicle air conditioner, an electric generator, an inverter, a PCU, a control device for ADAS, etc., which are cooling objects, can be used as the low controllability heat generating part.

[0511] The electric generator is an electric motor having a function of an electric motor that outputs driving force for traveling and a function of a generator. The inverter supplies power to the electric generator and the like. The PCU is an electronic control unit that performs power conversion and power distribution. The control device for ADAS is a control device for an advanced driving assistance system.

[0512] Moreover, the battery, the electric generator, the inverter, the PCU, ADAS, etc. can control the calorific value by performing inefficient operation. Therefore, the battery, the electric generator, the inverter, the PCU, ADAS, etc. can be used as a high controllability heat generating part.

[0513] In the above-described embodiment, an example in which the calorific value control unit 60b controls the calorific value of the high controllability heat generating part has been described, but the calorific value control unit 60b can of course also control the calorific values of both the high controllability heat generating part and the low controllability heat generating part.

[0514] In the heat pump cycles 10 to 10c of the above-described embodiment, an example in which a heating part is formed by using the water refrigerant heat exchanger 13 and the respective constituent devices of the high-temperature side heat medium circuits 30 and 30c has been described, but it is not limited thereto.

[0515] For example, as the heating part, an indoor condenser can be adopted. The indoor condenser is a heat exchange part for heating for heat-exchanging the discharged refrigerant on one side branched at the first three-way joint 12a and the blown air that has passed through the indoor evaporator 18. Moreover, the indoor condenser can be disposed in the air passage of the indoor air conditioner unit 50 in the same manner as the heater core 32.

[0516] In addition, in the heat pump cycles 10 to 10c of the above-described embodiments, an example in which the sixth three-way joint 12f as a mixing unit is arranged on the upstream side of the refrigerant flow of the cooler 20 has been described, but it is not limited thereto.

[0517] For example, in the heat pump cycle 10 of the first embodiment, it may also be arranged on the downstream side of the refrigerant flow of the cooler 20. In addition, in the heat pump cycle 10 of the second embodiment, it may also be arranged on the downstream side of the heating passage 84a of the refrigerant electric heater 84. Even with such a structure, the heat generated by the refrigerant electric heater 84 can be absorbed by the refrigerant flowing out of the cooling expansion valve 14c in the heating passage 84a.

[0518] In addition, in the first to fourth embodiments, a dedicated mixer that uniformly mixes the refrigerant flowing out of the bypass side flow rate adjustment valve 14d and the refrigerant flowing out of the cooling expansion valve 14c may be arranged instead of the sixth three-way joint 12f. In addition, in the first and second embodiments, the sixth three-way joint 12f may be abolished and the end of the bypass passage 21c may be directly connected to the accumulator 23.

[0519] In addition, in the above-described embodiments, an example in which the second check valve 16b is adopted has been described, but an evaporation pressure adjustment valve may be adopted instead of the second check valve 16b. The evaporation pressure adjustment valve is a variable throttling mechanism that maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a temperature equal to or higher than a specified temperature (for example, the temperature of the indoor evaporator 18 can be suppressed).

[0520] As the evaporation pressure adjustment valve, a variable throttling mechanism constituted by a mechanical mechanism in which the valve opening increases as the pressure of the refrigerant on the refrigerant outlet side of the indoor evaporator 18 rises may also be adopted. In addition, as the evaporation pressure adjustment valve, a variable throttling mechanism constituted by an electrical mechanism similar to that of the heating expansion valve 14a or the like may also be adopted.

[0521] 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-described embodiments. Various detection units may be added as needed.

[0522] In addition, in the above-described embodiments, an example in which R1234yf is used as the refrigerant has been described, but it is not limited thereto. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may also be used. Alternatively, a mixed refrigerant obtained by mixing several of these refrigerants may also be used. In addition, carbon dioxide may also be used as the refrigerant to constitute a transcritical refrigeration cycle in which the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant.

[0523] In addition, in the above-described embodiments, an example in which PAG oil is used as the refrigeration oil has been described, but it is not limited thereto. For example, POE (i.e., polyol ester) or the like may also be used.

[0524] In addition, in the above-described embodiments, examples in which an ethylene glycol aqueous solution is used as the low-temperature side heat medium and the high-temperature side heat medium have been described, but it is not limited thereto. As the high-temperature side heat medium and the low-temperature side heat medium, for example, a solution containing dimethylpolysiloxane or nanofluid, an aqueous liquid refrigerant containing antifreeze, alcohol, etc., a liquid medium containing oil, etc. may also be used.

[0525] The control method of the heat pump cycle device according to the present disclosure is not limited to the control method disclosed in the above-described embodiments.

[0526] In the above-described embodiments, an example in which the upper limit rotation speed determining unit 60e decreases the upper limit rotation speed Nclmt as the vehicle speed Vv decreases has been described, but it is not limited thereto. For example, the upper limit rotation speed determining unit 60e also decreases the upper limit rotation speed Nclmt as the rotation speed of the indoor blower 52 decreases within the range below the maximum rotation speed Ncmax.

[0527] In the above-described embodiments, an example in which the rotation speeds of the first low-temperature side pump 41a and the second low-temperature side pump 41b, which are the heat medium flow rate adjusting units, increase as the inflow temperature TWLC rises in the endothermic hot gas heating mode has been described, but it is not limited thereto.

[0528] For example, instead of the heat medium three-way valve 42, a three-way flow rate adjusting valve having the same structure as the low-temperature side three-way flow rate adjusting valve 47 described in the fourth embodiment may be used, and the flow rate of the low-temperature side heat medium in the heat medium passage flowing into the cooler 20 is increased as the inflow temperature TWLC rises. In this case, the three-way flow rate adjusting valve becomes the heat medium flow rate adjusting unit.

[0529] In the above-described embodiments, the vehicle air conditioners 1 to 1c capable of executing various operation modes have been described, but the heat pump cycle device according to the present disclosure does not need to be capable of executing all of the above operation modes.

[0530] As long as the heat pump cycle device according to the present disclosure is capable of executing the endothermic hot gas heating mode, the effects described in the above-described embodiments can be obtained. That is, the heating ability of the blown air can be improved without increasing the rotation speed of the compressor 11.

[0531] Furthermore, it may also be capable of executing other operation modes. For example, in the vehicle air conditioners 1 to 1b of the first to third embodiments, the hot gas dehumidification heating mode may also be executed.

[0532] Specifically, in the independent hot-gas dehumidifying and heating mode, the control device 60 is switched to circulate the refrigerant in the same way as in the hot-gas heating mode, and the refrigerant expansion valve 14b for refrigeration is set to a throttling state so that the low-pressure refrigerant flows into the refrigerant circuit of the indoor evaporator 18. That is, it is switched to a refrigerant circuit in which the indoor evaporator 18 and the cooler 20 are connected in parallel with respect to the flow of the refrigerant. Therefore, the supply air can be cooled and dehumidified in the indoor evaporator 18.

[0533] In the independent hot-gas dehumidifying and heating mode, the refrigerant with a relatively high enthalpy can flow into the sixth three-way joint 12f through the bypass passage 21c. Therefore, even if the refrigerant discharge capacity of the compressor 11 is increased, the decrease in the suction refrigerant pressure Ps can be suppressed. As a result, the amount of heat dissipated from the discharged refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 13 can be increased without causing frosting of the indoor evaporator 18.

[0534] That is, in the independent hot-gas dehumidifying and heating mode, the dehumidifying and heating of the vehicle interior can be performed with a heating capacity higher than that in the independent dehumidifying and heating mode. Moreover, similar to the cooling dehumidifying and heating modes of the first to third embodiments, by controlling the operation of each component device of the low-temperature side heat medium circuit 40, the cooling hot-gas dehumidifying and heating mode can be executed.

[0535] In addition, when the heat pump cycles 10 and 10b of the first to third embodiments are provided with the above-mentioned evaporation pressure regulating valve, the parallel dehumidifying and heating mode can also be executed.

[0536] Specifically, in the independent parallel dehumidifying and heating mode, the control device 60 is switched to circulate the refrigerant in the same way as in the outside-air heat-absorbing and heating mode, the high-pressure side on-off valve 22a is opened, and the refrigerant expansion valve 14b for refrigeration is set to a throttling state so that the low-pressure refrigerant flows into the refrigerant circuit of the indoor evaporator 18. That is, it is switched to a refrigerant circuit in which the indoor evaporator 18 and the outdoor heat exchanger 15 are connected in parallel with respect to the flow of the refrigerant. Therefore, the supply air can be cooled and dehumidified in the indoor evaporator 18.

[0537] In the independent parallel dehumidifying and heating mode, due to the action of the evaporation pressure regulating valve, the evaporation pressure of the refrigerant in the outdoor heat exchanger 15 can be made lower than the evaporation pressure of the refrigerant in the indoor evaporator 18. As a result, the amount of heat dissipated from the discharged refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 13 can be increased without causing frosting of the indoor evaporator 18.

[0538] That is, in the independent parallel dehumidifying and heating mode, the dehumidifying and heating inside the vehicle compartment can be performed with a heating capacity higher than that in the independent dehumidifying and heating mode. Further, by setting the cooling expansion valve 14c in a throttling state, the operations of the respective components of the low-temperature side heat medium circuit 40 are controlled in the same manner as in the cooling dehumidifying and heating modes of the first to third embodiments, whereby the cooling parallel dehumidifying and heating mode can be executed.

[0539] In addition, an equipment cooling mode in which the air inside the vehicle compartment is not conditioned and only the battery 70 is cooled can also be executed. Specifically, when the equipment cooling mode is executed, the control device 60 switches the refrigerant circuit of the heat pump cycle 10 in the same manner as in the cooling refrigeration mode, and sets the refrigeration expansion valve 14b in a fully closed state. Further, the control device 60 can stop the indoor blower 52.

[0540] The methods disclosed in the above-described respective embodiments can be appropriately combined within the range in which they can be implemented. For example, the refrigerant electric heater 84 described in the second embodiment can be employed, and the heating passage 84a can be arranged in the heat pump cycles 10 to 10c in the same manner as in the second embodiment.

[0541] In addition, the low-temperature side heat medium circuit 40 described in the first embodiment can be applied to the vehicle air conditioner 1a described in the second embodiment. In this case, power may be supplied to the heat medium electric heater 44 in the same manner as to the refrigerant electric heater 84.

[0542] The features of the heat pump cycle device disclosed in this specification are as follows.

[0543] (Item 1)

[0544] A heat pump cycle device includes:

[0545] a compressor (11) that compresses and discharges a refrigerant;

[0546] a branch portion (12a) that branches the flow of the refrigerant discharged from the compressor;

[0547] a heating portion (13, 30, 30c) that uses the refrigerant flowing out from one of the outlets of the branch portion as a heat source to heat a heating object;

[0548] a heating portion side decompression portion (14c) that decompresses the refrigerant flowing out from the heating portion;

[0549] a bypass passage (21c) through which the other refrigerant branched at the branch portion flows;

[0550] A bypass-side flow rate adjustment unit (14d) that adjusts the flow rate of the refrigerant flowing through the bypass passage;

[0551] A confluence unit (12f) that causes the flow of the refrigerant flowing out from the bypass-side flow rate adjustment unit and the flow of the refrigerant flowing out from the heating unit-side pressure reduction unit to merge and flow out toward the suction port side of the compressor;

[0552] A heat generation unit (44, 70, 84) that generates heat; and

[0553] A heat absorption unit (20, 84a) that causes at least the heat generated by the heat generation unit (44, 70, 84) to be absorbed by the refrigerant flowing out from the heating unit-side pressure reduction unit.

[0554] (Item 2)

[0555] The heat pump cycle device described in Item 1, wherein

[0556] It includes a heat medium circuit (40, 40c) through which the heat medium heated by the heat generation unit circulates,

[0557] The heat absorption unit is a heat exchange unit that causes heat exchange between the heat medium and the refrigerant,

[0558] When the inflow temperature (TWLC) of the heat medium flowing into the heat absorption unit becomes equal to or higher than the target heat medium temperature (TWLCO), the heat medium circuit causes the heat medium to flow into the heat absorption unit.

[0559] (Item 3)

[0560] The heat pump cycle device described in Item 2, wherein

[0561] It includes a heat generation amount control unit (60b) that controls the heat generation amount of the heat generation unit,

[0562] The heat generation amount control unit controls the heat generation amount of the heat generation unit in such a way that the inflow temperature (TWLC) becomes equal to or higher than the target heat medium temperature (TWLCO).

[0563] (Item 4)

[0564] The heat pump cycle device described in Item 3, wherein

[0565] The heat medium circuit has a heat medium circuit switching unit (42, 43, 47) and a heat medium bypass passage (45). The heat medium circuit switching unit switches the circuit structure of the heat medium circuit, and the heat medium bypass passage allows the heat medium heated by the heat generation unit to flow around the heat absorption unit.

[0566] When the inflow temperature (TWLC) is lower than the target heat medium temperature (TWLCO), the heat medium circuit switching unit switches to a circuit in which the heat medium heated in the heating unit flows into the heat medium bypass path.

[0567] (Item 5)

[0568] The heat pump cycle device according to Item 3 or 4, wherein

[0569] The heat medium circuit has a heat medium circuit switching unit (42, 43, 47) that switches the circuit structure of the heat medium circuit.

[0570] The heating unit has a highly controllable heating unit (44) and a lowly controllable heating unit (70).

[0571] The controllability of the calorific value of the lowly controllable heating unit is lower than that of the highly controllable heating unit.

[0572] When the inflow temperature (TWLC) becomes equal to or higher than the target heat medium temperature (TWLCO), the heat medium circuit switching unit switches to a circuit in which the heat medium flowing out of the lowly controllable heating unit is heated in the highly controllable heating unit, and then the heat medium heated in the highly controllable heating unit flows into the heat absorption unit.

[0573] (Item 6)

[0574] The heat pump cycle device according to any one of Items 2 to 5, wherein

[0575] The heat medium circuit has a heat medium flow rate adjustment unit (41a, 41b) that adjusts the inflow rate of the heat medium flowing into the heat absorption unit.

[0576] The heat medium flow rate adjustment unit increases the inflow rate as the inflow temperature (TWLC) rises.

[0577] (Item 7)

[0578] The heat pump cycle device according to any one of Items 1 to 6, further comprising:

[0579] An upper limit rotation speed determination unit (60e) that determines the upper limit rotation speed (Nclmt) of the compressor; and

[0580] A calorific value control unit (60b) that controls the calorific value of the heating unit.

[0581] The calorific value control unit controls the operation of the heating unit so that the total calorific value of the heating unit increases as the upper limit rotational speed (Nclmt) decreases.

[0582] This disclosure is described based on embodiments, but it should be understood that this disclosure is not limited to these embodiments and structures. This disclosure also includes various modifications and variations within an equivalent range. In addition, various combinations, manners, and even other combinations and manners that include only one element, more than one element, or less than one element among them also fall within the scope and ideological scope of this disclosure.

Claims

1. A heat pump cycle device, characterized in that, It has: A compressor (11) that compresses and discharges a refrigerant; A branch portion (12a) that branches the flow of the refrigerant discharged from the compressor; A heating portion (13, 30, 30c) that heats an object to be heated using the refrigerant flowing out from one outlet of the branch portion as a heat source; A decompression portion on the heating portion side (14c) that decompresses the refrigerant flowing out from the heating portion; A bypass passage (21c) through which the other refrigerant branched out at the branch portion flows; A flow rate adjustment portion on the bypass side (14d) that adjusts the flow rate of the refrigerant flowing through the bypass passage; A confluence portion (12f) that causes the flow of the refrigerant flowing out from the bypass side flow rate adjustment portion and the flow of the refrigerant flowing out from the heating portion side decompression portion to merge and flow out toward the suction port side of the compressor; A heat generating portion (44, 70, 84) that generates heat; And A heat absorbing portion (20, 84a) that causes at least the heat generated by the heat generating portion (44, 70, 84) to be absorbed by the refrigerant flowing out from the heating portion side decompression portion.

2. The heat pump cycle device according to claim 1, characterized in that, It is provided with a heat medium circuit (40, 40c) through which the heat medium heated by the heat generating portion circulates, The heat absorbing portion is a heat exchange portion that exchanges heat between the heat medium and the refrigerant, When the inflow temperature (TWLC) of the heat medium flowing into the heat absorbing portion becomes equal to or higher than the target heat medium temperature (TWLCO), the heat medium circuit causes the heat medium to flow into the heat absorbing portion.

3. The heat pump cycle device according to claim 2, characterized in that, It is provided with a heat generation amount control portion (60b) that controls the heat generation amount of the heat generating portion, The heat generation amount control portion controls the heat generation amount of the heat generating portion in such a way that the inflow temperature (TWLC) becomes equal to or higher than the target heat medium temperature (TWLCO).

4. The heat pump cycle device according to claim 3, characterized in that, The heat medium circuit has a heat medium circuit switching portion (42, 43, 47) and a heat medium bypass passage (45). The heat medium circuit switching portion switches the circuit structure of the heat medium circuit, and the heat medium bypass passage allows the heat medium heated by the heat generating portion to flow around the heat absorbing portion. When the inflow temperature (TWLC) is lower than the target heat medium temperature (TWLCO), the heat medium circuit switching portion switches to a circuit in which the heat medium heated by the heat generating portion flows into the heat medium bypass passage.

5. The heat pump cycle device according to claim 3, characterized in that, The heat medium circuit has a heat medium circuit switching portion (42, 43, 47) that switches the circuit structure of the heat medium circuit, The heat generating portion has a highly controllable heat generating portion (44) and a lowly controllable heat generating portion (70), The controllability of the heat generation amount of the lowly controllable heat generating portion is lower than that of the highly controllable heat generating portion. When the inflow temperature (TWLC) becomes equal to or higher than the target heat medium temperature (TWLCO), the heat medium circuit switching unit switches to a circuit in which the heat medium flowing out from the low controllability heating unit is heated in the high controllability heating unit and then the heat medium heated in the high controllability heating unit flows into the heat absorption unit.

6. The heat pump cycle device according to claim 2, characterized in that, The heat medium circuit has heat medium flow rate adjustment units (41a, 41b) that adjust the inflow rate of the heat medium flowing into the heat absorption unit. The heat medium flow rate adjustment units increase the inflow rate as the inflow temperature (TWLC) rises.

7. The heat pump cycle device according to any one of claims 1 to 6, characterized in that, It includes: an upper limit rotation speed determination unit (60e) that determines the upper limit rotation speed (Nclmt) of the compressor; and a heat generation amount control unit (60b) that controls the heat generation amount of the heating unit. The heat generation amount control unit controls the operation of the heating unit so that the total heat generation amount of the heating unit increases as the upper limit rotation speed (Nclmt) decreases.

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