air conditioning unit

Abstract

The air conditioning unit includes: a heat pump cycle (10, 10a) having a compressor (11), a heating unit (12, 40, 121) and a low-temperature side water refrigerant heat exchanger (20), a heat medium circuit (50, 50a), and a blower (32). A heat-generating unit (54) is provided in the heat medium circuit (50, 50a). The air conditioning unit performs heating preparation control as follows: when using the heat generated by the heat-generating unit (54) to increase the heating capacity of the heating unit (12, 40, 121), the refrigerant discharge capacity of the compressor (11) is lower than a predetermined reference discharge capacity and the air supply capacity of the blower (32) is lower than a predetermined reference air supply capacity, until the inlet side heat medium temperature (TWin) of the heat medium flowing into the heat medium passage (20b) of the low-temperature side water refrigerant heat exchanger (20) reaches or exceeds the target heat medium temperature (TWinO).

Description

[0001] Cross-reference of related applications

[0002] This application is based on Japanese Patent Application No. 2021-26880, filed on February 23, 2021, the contents of which are incorporated herein by reference. Technical Field

[0003] This invention relates to an air conditioning device having a heat-generating section. Background Technology

[0004] Previously, Patent Document 1 disclosed an air conditioning device for vehicles that has a heat pump cycle and a low-temperature side heat medium circuit.

[0005] Patent Document 1's heat pump cycle includes a heating section and a low-temperature side water refrigerant heat exchanger. The heating section uses high-pressure refrigerant discharged from the compressor as a heat source to heat the air blown into the vehicle interior. The low-temperature side water refrigerant heat exchanger allows the low-pressure refrigerant to exchange heat with the low-temperature side heat medium circulating in the low-temperature side heat medium loop, enabling the low-pressure refrigerant to absorb the heat contained in the low-temperature side heat medium.

[0006] Furthermore, Patent Document 1 includes a low-temperature side heat medium circuit with a heat medium passage for a low-temperature side water refrigerant heat exchanger and an electric heater. The electric heater is a heat-generating component that generates heat for heating the low-temperature side heat medium.

[0007] In the air conditioning device of Patent Document 1, heat generated by an electric heater is moved from the low-pressure side to the high-pressure side by a heat pump cycle, and the heat can be used to improve the heating capacity of the heating unit.

[0008] Existing technical documents

[0009] Patent documents

[0010] Patent Document 1: International Publication No. 2013 / 013790

[0011] However, in the air conditioning device of Patent Document 1, in order to utilize the heat generated by the electric heater to improve the heating capacity of the heating section, the temperature of the low-temperature heat medium with a larger heat capacity must be increased compared to the low-pressure refrigerant.

[0012] Therefore, for example, when the temperature of the low-temperature side heat medium decreases as much as the outside air temperature, the time required to raise the temperature of the low-temperature side heat medium is prolonged, making it impossible to rapidly increase the heating capacity of the heating unit. As a result, the preheating time required to raise the temperature of the supply air to a temperature sufficient for adequate heating of the vehicle interior is prolonged, making it impossible to achieve rapid and responsive air conditioning.

[0013] In view of the above points, the object of the present invention is to provide an air conditioning device that can rapidly increase the heating capacity of the heating unit by using the heat generated by the heating element.

[0014] To achieve the above objectives, an air conditioning device according to one aspect of the present invention includes a heat pump cycle, a heat medium circuit, and a blower.

[0015] A heat pump cycle includes a compressor, a heating element, and a low-temperature side water-cooled refrigerant heat exchanger. The compressor compresses and discharges the refrigerant. The heating element uses the high-pressure refrigerant discharged from the compressor as a heat source to heat the supply air blown into the air-conditioned space. The low-temperature side water-cooled refrigerant heat exchanger allows the low-pressure refrigerant to absorb heat from the heat transfer medium.

[0016] The heating medium is circulated in the heat transfer circuit. The blower blows air into the space to be conditioned.

[0017] The heat medium circuit is equipped with a heat medium passage with a low-temperature side water refrigerant heat exchanger and a heat-generating section for heating the heat medium flowing into the heat medium passage.

[0018] Furthermore, when using the heat generated by the heat-generating section to enhance the heating capacity of the heating section, heating preparation control is performed. In heating preparation control, the refrigerant discharge capacity of the compressor is set below a predetermined reference discharge capacity and the air supply capacity of the blower is set below a predetermined reference air supply capacity until the temperature of the inlet side of the heat medium flowing into the heat medium passage reaches or exceeds the target heat medium temperature.

[0019] Therefore, in the heating preparation control, the refrigerant discharge capacity of the compressor is kept below the baseline discharge capacity until the temperature of the heat medium flowing into the heat medium passage of the low-temperature side water refrigerant heat exchanger becomes above the target heat medium temperature. Thus, an unnecessary increase in the amount of heat absorbed by the low-pressure refrigerant from the heat medium in the low-temperature side water refrigerant heat exchanger can be suppressed.

[0020] Furthermore, in the heating preparation control, the air supply capacity of the blower is kept below a predetermined reference air supply capacity until the temperature of the heat medium flowing into the heat medium passage of the low-temperature side water refrigerant heat exchanger reaches or exceeds the target heat medium temperature. Therefore, an unnecessary increase in the amount of heat dissipated to the supply air in the heating section can be suppressed.

[0021] As a result, by implementing heating preparation control, the temperature of the heat medium can be rapidly increased using the heat generated by the heating element. Furthermore, by causing the low-pressure refrigerant circulating in the heat pump to absorb the heat from the rapidly rising heat medium and move it towards the high-pressure refrigerant, the heating capacity of the heating element can be rapidly increased.

[0022] That is, according to one aspect of the air conditioning device of the present invention, an air conditioning device is provided that can rapidly increase the heating capacity of the heating section by using the heat generated by the heat-generating section. Attached Figure Description

[0023] Figure 1 This is a schematic overall structural diagram of the air conditioning device according to the first embodiment.

[0024] Figure 2 This is a block diagram showing the electrical control unit of the air conditioning device according to the first embodiment.

[0025] Figure 3 This is a flowchart illustrating the control flow in the heating preparation control of the air conditioning unit according to the first embodiment.

[0026] Figure 4 This is a schematic overall structural diagram showing the flow of refrigerant and the like in the heating preparation control of the air conditioning device according to the first embodiment.

[0027] Figure 5 It is a graph showing the changes in the inlet-side heat medium temperature and the target heat medium temperature under comparative conditions of the air conditioning device of the first embodiment.

[0028] Figure 6 It is a graph showing the changes in the inlet-side heat medium temperature and the target heat medium temperature under the first condition of the air conditioning device of the first embodiment.

[0029] Figure 7 It is a graph showing the changes in the inlet-side heat medium temperature and the target heat medium temperature under the second condition of the air conditioning device of the first embodiment.

[0030] Figure 8 This is a schematic overall structural diagram showing the flow of refrigerant and the like in a modified example of the heating preparation control of the air conditioning device according to the first embodiment.

[0031] Figure 9 This is a schematic overall structural diagram illustrating the flow of refrigerant and the like in another variation of the heating preparation control of the air conditioning device according to the first embodiment.

[0032] Figure 10 This is a schematic overall structural diagram of the air conditioning device according to the second embodiment.

[0033] Figure 11 This is a schematic overall structural diagram showing the flow of refrigerant and the like in the heating preparation control of the air conditioning unit according to the third embodiment.

[0034] Figure 12 This is a schematic overall structural diagram showing the flow of refrigerant and the like in the heating preparation control of the air conditioning device according to the fourth embodiment.

[0035] Figure 13 This is a schematic overall structural diagram showing the flow of refrigerant and the like in the heating preparation control of the air conditioning device according to the fifth embodiment. Detailed Implementation

[0036] Hereinafter, several embodiments for carrying out the present invention will be described with reference to the accompanying drawings. In each embodiment, there are cases where the same reference numerals are used to mark the parts corresponding to those described in prior embodiments, and repeated descriptions are omitted. In each embodiment, where only a part of the structure is described, the other previously described embodiments can be applied to the other parts of the structure. Not only are the parts that can be combined specifically indicated in each embodiment able to be combined with each other, but even if not explicitly indicated, embodiments can be partially combined with each other as long as there are no particular obstacles to combination.

[0037] (First Implementation)

[0038] use Figures 1-9 A first embodiment of the air conditioning device 1 according to the present invention will be described. The air conditioning device 1 of this embodiment is applicable to electric vehicles. An electric vehicle is a vehicle that obtains driving force from an electric motor. The air conditioning device 1 in an electric vehicle regulates the air inside the vehicle cabin, which is the space to be conditioned, and regulates the temperature of onboard equipment, which is the object of temperature regulation. Therefore, the air conditioning device 1 of this embodiment is a vehicle air conditioning device with onboard equipment temperature regulation function.

[0039] In the air conditioning device 1 of this embodiment, the vehicle-mounted equipment that is subject to temperature regulation is the battery 80 and the high-voltage electrical equipment 81.

[0040] Battery 80 is a secondary battery that stores electricity supplied to electric vehicle-mounted equipment. In this embodiment, lithium-ion batteries are used as battery 80. Battery 80 is a battery pack formed by connecting multiple battery cells in a stacked configuration in series or parallel.

[0041] The battery 80 generates heat during operation (i.e., during charging and discharging). The output of the battery 80 tends to decrease at low temperatures and deteriorates easily at high temperatures. Therefore, the temperature of the battery 80 needs to be maintained within an appropriate temperature range (above 15°C and below 55°C in this embodiment).

[0042] The high-voltage electrical equipment 81 is an on-board device that operates by being supplied with electricity and generates heat during operation. Specifically, the high-voltage electrical equipment 81 in this embodiment is an inverter and an electric generator.

[0043] An inverter is a power conversion device that converts the frequency of the power supplied from battery 80 to the electric generator, converts the alternating current (AC) power generated by the electric generator into direct current (DC) power, and outputs it to battery 80. The electric generator becomes an electric motor that outputs driving force for driving by supplying power, and becomes a power generation device that generates regenerative power when the vehicle decelerates or travels downhill.

[0044] If the high-voltage electrical equipment 81 becomes too hot, it may lead to circuit deterioration. Therefore, it is necessary to maintain a temperature lower than the reference heat resistance temperature (130°C in this embodiment) that can protect each circuit.

[0045] Therefore, in this embodiment, the appropriate temperature range that enables the battery 80 to operate properly and the appropriate temperature range that enables the high-voltage equipment 81 to operate properly are not entirely the same. In other words, the appropriate temperature range of the battery 80 is different from the appropriate temperature range of the high-voltage equipment 81.

[0046] like Figure 1 As shown in the overall structural diagram, the air conditioning unit 1 includes a heat pump cycle 10, an indoor air conditioning unit 30, a high-temperature side heat medium circuit 40, and a low-temperature side heat medium circuit 50.

[0047] First, the heat pump cycle 10 will be explained. The heat pump cycle 10 is a vapor compression refrigeration cycle device that regulates the temperature of the air blown into the vehicle interior, the high-temperature heat medium circulating in the high-temperature heat medium circuit 40, and the low-temperature heat medium circulating in the low-temperature heat medium circuit 50 for the purpose of air conditioning in the vehicle interior and temperature regulation of on-board equipment.

[0048] The heat pump cycle 10 is configured to switch the refrigerant circuit according to various operating modes described later, in order to regulate the air in the vehicle interior and the temperature of the on-board equipment.

[0049] In heat pump cycle 10, an HFO-based refrigerant (specifically R1234yf) is used as the refrigerant. Heat pump cycle 10 constitutes a subcritical refrigeration cycle where the pressure of the high-pressure refrigerant discharged from compressor 11 does not exceed the critical pressure of the refrigerant. Refrigeration oil for lubricating compressor 11 is mixed into the refrigerant. The refrigeration oil is a PAG oil that is miscible with the liquid refrigerant. A portion of the refrigeration oil circulates in the cycle along with the refrigerant.

[0050] In the heat pump cycle 10, the compressor 11 draws in, compresses, and discharges refrigerant. The compressor 11 is located in the drive unit compartment on the front side of the vehicle compartment. The drive unit compartment forms a space for accommodating at least a portion of equipment used to generate driving force for vehicle movement (e.g., an electric generator).

[0051] The compressor 11 is an electric compressor with a fixed-capacity compressor mechanism driven by an electric motor, which has a fixed discharge capacity. The speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled according to the control signal output from the control device 60 for system control described later.

[0052] The outlet of compressor 11 is connected to the inlet side of refrigerant passage 12a of water refrigerant heat exchanger 12. Water refrigerant heat exchanger 12 has refrigerant passage 12a for circulating high-pressure refrigerant discharged from compressor 11 and heat medium passage 12b for circulating high-temperature heat medium circulating in high-temperature heat medium circuit 40.

[0053] The water refrigerant heat exchanger 12 is a high-temperature water refrigerant heat exchange section that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage 12a and the high-temperature side heat medium flowing through the heat medium passage 12b. In the water refrigerant heat exchanger 12, the heat possessed by the high-pressure refrigerant is dissipated to the heat medium, thereby heating the high-temperature side heat medium.

[0054] The outlet of the refrigerant passage 12a of the water refrigerant heat exchanger 12 is connected to the inlet side of the first refrigerant connector 13a. The first refrigerant connector 13a is a tee connector with three inlet and outlet ports that are interconnected. The first refrigerant connector 13a can be a connector component formed by joining multiple pipes, or a connector component formed by setting multiple refrigerant passages in a metal block or resin block.

[0055] Furthermore, as described later, the heat pump cycle 10 has a second refrigerant connector 13b to a sixth refrigerant connector 13f. The basic structure of the second refrigerant connector 13b to the sixth refrigerant connector 13f is the same as that of the first refrigerant connector 13a.

[0056] These joints, when using one of the three inlet and outlet ports as the inlet and the remaining two as the outlet, become branching points that branch the refrigerant flow. Conversely, when using two of the three inlet and outlet ports as the inlet and the remaining one as the outlet, they become confluence points that merge the refrigerant flow.

[0057] One outlet of the first refrigerant connector 13a is connected to the inlet side of the heating expansion valve 14a. The other outlet of the first refrigerant connector 13a is connected to the inlet side of one of the second refrigerant connectors 13b via the dehumidification passage 22a.

[0058] The dehumidification passage 22a is formed in the refrigerant flow path during parallel dehumidification and heating modes described later, allowing refrigerant to circulate. A dehumidification on / off valve 15a is installed in the dehumidification passage 22a. The dehumidification on / off valve 15a is a solenoid valve that opens and closes the dehumidification passage 22a. The operation of the dehumidification on / off valve 15a is controlled by a voltage output from the control device 60.

[0059] Furthermore, as described later, the heat pump cycle 10 includes a heating on / off valve 15b. The basic structure of the heating on / off valve 15b is the same as that of the dehumidification on / off valve 15a. The dehumidification on / off valve 15a and the heating on / off valve 15b can switch the refrigerant circuit of the heat pump cycle 10 by opening and closing the refrigerant passage. Therefore, the dehumidification on / off valve 15a and the heating on / off valve 15b are refrigerant circuit switching parts for switching the refrigerant circuit.

[0060] The expansion valve 14a for heating is a pressure-reducing unit that, in the heating mode described later, reduces the pressure of the high-pressure refrigerant flowing out of the refrigerant passage 12a of the water refrigerant heat exchanger 12 and regulates the flow rate (mass flow rate) of the refrigerant flowing downstream.

[0061] The heating expansion valve 14a is an electrically operated variable throttling mechanism having a valve core 141a that changes the opening degree of the throttling passage (i.e., valve opening degree) and an electric actuator (specifically a stepper motor) that displaces the valve core 141a. The operation of the heating expansion valve 14a is controlled according to a control signal (specifically a control pulse) output from the control device 60.

[0062] The heating expansion valve 14a has a fully open function. This fully open function is achieved by setting the valve opening to full open through the valve core 141a, thus performing almost no flow regulation or refrigerant pressure reduction function, and only functioning as a refrigerant passage. In addition, the heating expansion valve 14a also has a fully closed function. This fully closed function is achieved by completely closing the throttling path through the valve core 141a, thereby sealing off the refrigerant passage.

[0063] Furthermore, as described later, the heat pump cycle 10 also includes a refrigeration expansion valve 14b and a cooling expansion valve 14c. The basic structure of the refrigeration expansion valve 14b and the cooling expansion valve 14c is the same as that of the heating expansion valve 14a. Therefore, the refrigeration expansion valve 14b has a valve core 141b and has both fully open and fully closed functions. The cooling expansion valve 14c has a valve core 141c and has both fully open and fully closed functions.

[0064] The heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c, through their fully closed functions described above, can switch the refrigerant circuit of the heat pump cycle 10. More specifically, the valve core 141a of the heating expansion valve 14a, the valve core 141b of the cooling expansion valve 14b, and the valve core 141c of the cooling expansion valve 14c also function as refrigerant circuit switching units.

[0065] Of course, a variable throttling mechanism without a fully closed function can also be combined with an on / off valve to form a heating expansion valve 14a, a cooling expansion valve 14b, and a cooling expansion valve 14c. In this case, the on / off valve becomes a refrigerant circuit switching unit.

[0066] The outlet of the heating expansion valve 14a is connected to the refrigerant inlet side of the outdoor heat exchanger 16. Therefore, the valve core 141a of the heating expansion valve 14a is an outdoor unit inlet-side opening and closing part that opens and closes the refrigerant inlet side of the outdoor heat exchanger 16. The outdoor heat exchanger 16 is an outdoor heat exchange unit that allows the refrigerant flowing from the heating expansion valve 14a to exchange heat with outside air blown by a cooling fan (not shown). The outdoor heat exchanger 16 is located at the front of the drive unit compartment. Therefore, when the vehicle is in motion, the driving air can come into contact with the outdoor heat exchanger 16.

[0067] The refrigerant outlet of the outdoor heat exchanger 16 is connected to the inlet side of the third refrigerant connector 13c. One outlet of the third refrigerant connector 13c is connected to one inlet side of the fourth refrigerant connector 13d via a heating passage 22b. The heating passage 22b forms a refrigerant flow path for refrigerant circulation during heating modes, as described later.

[0068] A heating on / off valve 15b and a first check valve 17a are provided in the heating passage 22b. The heating on / off valve 15b is a solenoid valve that opens and closes the heating passage 22b. The first check valve 17a allows refrigerant to flow from the third refrigerant connector 13c to the fourth refrigerant connector 13d, and prohibits refrigerant from flowing from the fourth refrigerant connector 13d to the third refrigerant connector 13c. Therefore, the heating on / off valve 15b and the first check valve 17a constitute the outdoor unit outlet-side opening and closing part that opens and closes the refrigerant outlet side of the outdoor heat exchanger 16.

[0069] The outlet of the third refrigerant connector 13c is connected to the inlet of the second refrigerant connector 13b. A second check valve 17b is provided in the refrigerant passage connecting the outlet of the third refrigerant connector 13c and the inlet of the second refrigerant connector 13b. The second check valve 17b allows refrigerant to flow from the third refrigerant connector 13c to the second refrigerant connector 13b, and prevents refrigerant from flowing from the second refrigerant connector 13b to the third refrigerant connector 13c. Therefore, the second check valve 17b serves as the outdoor unit outlet-side opening and closing part.

[0070] The outlet of the second refrigerant connector 13b is connected to the inlet of the fifth refrigerant connector 13e. One outlet of the fifth refrigerant connector 13e is connected to the inlet of the refrigeration expansion valve 14b. The other outlet of the fifth refrigerant connector 13e is connected to the inlet of the cooling expansion valve 14c.

[0071] The expansion valve 14b for refrigeration is a pressure-reducing section used in refrigeration modes (described later) to reduce refrigerant pressure and regulate the flow rate of refrigerant flowing downstream. The outlet of the expansion valve 14b is connected to the refrigerant inlet side of the indoor evaporator 18. Therefore, the valve core 141b of the expansion valve 14b serves as an indoor unit inlet-side opening and closing section for opening and closing the refrigerant inlet side of the indoor evaporator 18.

[0072] The indoor evaporator 18 is disposed within the air conditioning housing 31 of the indoor air conditioning unit 30, which will be described later. The indoor evaporator 18 is a cooling heat exchanger that exchanges heat between the low-pressure refrigerant, which has been depressurized by the refrigeration expansion valve 14b, and the supply air blown into the vehicle interior. In the indoor evaporator 18, the low-pressure refrigerant evaporates and absorbs heat, thereby cooling the supply air.

[0073] The refrigerant outlet of the indoor evaporator 18 is connected to the inlet side of one of the sixth refrigerant connectors 13f. A third check valve 17c is provided in the refrigerant flow path connecting the refrigerant outlet of the indoor evaporator 18 and the inlet side of one of the sixth refrigerant connectors 13f. The third check valve 17c allows refrigerant to flow from the indoor evaporator 18 side to the sixth refrigerant connector 13f side, and prevents refrigerant from flowing from the sixth refrigerant connector 13f side to the indoor evaporator 18 side. Therefore, the third check valve 17c serves as the indoor unit outlet-side opening and closing part for opening and closing the refrigerant outlet side of the indoor evaporator 18.

[0074] The cooling expansion valve 14c is a cooling pressure reducing unit that reduces the pressure of the refrigerant and regulates the flow rate of the refrigerant flowing downstream, as described later in battery cooling mode, etc. The outlet of the cooling expansion valve 14c is connected to the inlet side of the refrigerant passage 20a of the chiller 20.

[0075] The chiller 20 has a refrigerant passage 20a through which low-pressure refrigerant, after being depressurized by the cooling expansion valve 14c, flows, and a heat medium passage 20b through which low-pressure heat medium circulating in the low-temperature side heat medium circuit 50 flows. The chiller 20 is a low-temperature side water refrigerant heat exchanger that allows heat exchange between the low-pressure refrigerant flowing in the refrigerant passage 20a and the low-temperature side heat medium flowing in the heat medium passage 20b. In the chiller 20, the low-pressure refrigerant evaporates and absorbs heat, thereby cooling the low-temperature side heat medium.

[0076] The outlet of the refrigerant passage 20a of the chiller 20 is connected to the inlet side of the sixth refrigerant connector 13f. Therefore, the indoor evaporator 18 and the chiller 20 are connected in parallel with respect to the refrigerant flow from the fifth refrigerant connector 13e to the sixth refrigerant connector 13f. The outlet of the sixth refrigerant connector 13f is connected to the inlet side of the fourth refrigerant connector 13d.

[0077] The outlet of the fourth refrigerant connector 13d is connected to the inlet side of the receiver 21. The receiver 21 is a low-pressure gas-liquid separator that separates the refrigerant flowing into it into a gas-liquid state and stores the remaining liquid refrigerant in the cycle. The gaseous refrigerant outlet of the receiver 21 is connected to the suction port side of the compressor 11.

[0078] Next, the high-temperature side heat medium circuit 40 will be described. The high-temperature side heat medium circuit 40 is a circuit for circulating high-temperature side heat medium. In the high-temperature side heat medium circuit 40, an aqueous solution of ethylene glycol is used as the high-temperature side heat medium. The high-temperature side heat medium circuit 40 is equipped with a heat medium passage 12b of a water refrigerant heat exchanger 12, a high-temperature side pump 41, a heater core 42, etc.

[0079] The high-temperature side pump 41 is a high-temperature side heat medium pressurization section that draws in and pressurizes the high-temperature side heat medium. The high-temperature side pump 41 pressurizes the high-temperature side heat medium to the inlet side of the heat medium passage 12b of the water refrigerant heat exchanger 12. The high-temperature side pump 41 is an electric water pump whose speed (i.e., pressurization capacity) is controlled according to the control voltage output from the control device 60.

[0080] The outlet of the heat medium passage 12b of the water refrigerant heat exchanger 12 is connected to the heat medium inlet side of the heater core 42. The heater core 42 is disposed within the air conditioning housing 31 of the indoor air conditioning unit 30. The heater core 42 is a heating heat exchange section that allows the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 to exchange heat with the supply air. In the heater core 42, the heat contained in the high-temperature side heat medium is dissipated to the supply air, thereby heating the supply air. The heat medium outlet of the heater core 42 is connected to the suction port side of the high-temperature side pump 41.

[0081] Therefore, in this embodiment, a heating section is formed by each component of the water refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40, which uses the high-pressure refrigerant discharged from the compressor 11 as a heat source to heat the supply air.

[0082] Next, the low-temperature side heat medium circuit 50 will be described. The low-temperature side heat medium circuit 50 is a circuit for circulating the low-temperature side heat medium. The low-temperature side heat medium is a heat medium heated by the heating element described later. In the low-temperature side heat medium circuit 50, a fluid of the same type as the high-temperature side heat medium is used as the low-temperature side heat medium. The low-temperature side heat medium circuit 50 is configured to allow switching of the heat medium circuit according to various operating modes described later.

[0083] The low-temperature side heat medium circuit 50 is equipped with a first low-temperature side pump 51a, a second low-temperature side pump 51b, a first low-temperature side three-way valve 52a, a second low-temperature side three-way valve 52b, a heat medium passage 20b for the chiller 20, a cooling water passage 80a for the battery 80, a cooling water passage 81a for the high-power equipment 81, an electric heater 54, a battery bypass passage 55a, a low-temperature side radiator 56, etc.

[0084] The first cryogenic side pump 51a and the second cryogenic side pump 51b are heat medium pressurization units that draw in and pressurize cryogenic side heat medium. The basic structure of the first cryogenic side pump 51a and the second cryogenic side pump 51b is the same as that of the high-temperature side pump 41. The first cryogenic side pump 51a pressurizes cryogenic side heat medium to the inlet side of the cooling water passage 80a of the battery 80.

[0085] The cooling water passage 80a of the battery 80 is a battery-side heat exchange section that allows multiple battery cells to exchange heat with a low-temperature heat medium. The cooling water passage 80a of the battery 80 accommodates multiple battery cells and is formed within the battery case that forms the casing of the battery 80.

[0086] The outlet of the cooling water passage 80a of the battery 80 is connected to the inlet side of the first low-temperature side three-way valve 52a. The first low-temperature side three-way valve 52a is a three-way flow regulating valve. The first low-temperature side three-way valve 52a allows the low-temperature side hot medium flowing out of the cooling water passage 80a of the battery 80 to flow inward, and allows it to flow out to at least one of the inlet side of the first hot medium connector 53a and the battery bypass passage 55a.

[0087] The first low-temperature side three-way valve 52a can continuously adjust the flow rate ratio of the low-temperature side heat medium flowing out to the first heat medium connector 53a side to the low-temperature side heat medium flowing out to the battery bypass passage 55a side. Furthermore, by adjusting the flow rate ratio, the first low-temperature side three-way valve 52a can cause all the flow rate of the low-temperature side heat medium flowing into the interior to flow out to either the first heat medium connector 53a side or the battery bypass passage 55a side.

[0088] That is, the first low-temperature side three-way valve 52a becomes the heat medium circuit switching part of the circuit structure for switching the heat medium circuit. The operation of the first low-temperature side three-way valve 52a is controlled according to the control signal output from the control device 60.

[0089] Furthermore, a second low-temperature side three-way valve 52b is provided in the low-temperature side heat medium circuit 50. The basic structure of the second low-temperature side three-way valve 52b and the three-way valve for the heat medium circuit used in the embodiments described later is the same as that of the first low-temperature side three-way valve 52a. Therefore, the second low-temperature side three-way valve 52b and the like also serve as heat medium circuit switching parts.

[0090] The first heat medium connector 53a is a tee connector for heat medium. Furthermore, as described later, the low-temperature side heat medium circuit 50 of this embodiment has a second heat medium connector portion 53b to a fourth heat medium connector portion 53d. The basic structure of the first heat medium connector portion 53a to the fourth heat medium connector portion 53d, as well as the heat medium connector portions used in the embodiments described later, is the same as that of the first refrigerant connector portion 13a of the heat pump cycle 10.

[0091] The outlet of the first heat medium connector 53a is connected to the inlet side of the electric heater 54. Therefore, the first low-temperature side three-way valve 52a substantially allows the low-temperature side heat medium flowing into the interior to flow out to at least one of the electric heater 54 side and the battery bypass passage 55a side.

[0092] The battery bypass passage 55a forms a hot medium flow path that allows the low-temperature side hot medium flowing out of the cooling water passage 80a of the battery 80 to bypass the hot medium passage 20b of the electric heater 54 and the chiller 20, and to be directed to the suction port side of the first low-temperature side pump 51a. The outlet of the battery bypass passage 55a is connected to the inlet of one of the second hot medium connectors 53b. The outlet of the second hot medium connector 53b is connected to the suction port side of the first low-temperature side pump 51a.

[0093] The second cryogenic pump 51b pressurizes the cryogenic heat medium to the inlet side of the cooling water passage 81a of the high-voltage electrical equipment 81. The cooling water passage 81a of the high-voltage electrical equipment 81 is a heat exchange section on the high-voltage electrical equipment side that allows heat exchange between the high-voltage electrical equipment 81 and the cryogenic heat medium. The cooling water passage 81a of the high-voltage electrical equipment 81 is formed within the housing or enclosure portion that forms the outer casing of the high-voltage electrical equipment 81.

[0094] The outlet of the cooling water passage 81a of the high-power equipment 81 is connected to the inlet side of the second low-temperature side three-way valve 52b. The second low-temperature side three-way valve 52b allows the low-temperature side heat medium flowing out of the cooling water passage 81a of the high-power equipment 81 to flow inward, and allows it to flow out to at least one of the inlet side of the first heat medium connector 53a and the low-temperature side radiator 56 side.

[0095] Therefore, the second low-temperature side three-way valve 52b essentially causes the low-temperature side heat medium flowing into the interior to flow out to at least one of the electric heater 54 side and the low-temperature side radiator 56 side.

[0096] The second low-temperature side three-way valve 52b can continuously adjust the flow rate ratio of the low-temperature side heat medium flowing to the electric heater 54 side to the low-temperature side heat medium flowing to the low-temperature side radiator 56 side. Furthermore, by adjusting the flow rate ratio, the second low-temperature side three-way valve 52b can make all the flow rate of the low-temperature side heat medium flowing into the interior flow out to either the electric heater 54 side or the battery bypass passage 55a side.

[0097] The low-temperature side radiator 56 is a low-temperature side outside air heat exchange unit that allows outside air to exchange heat with the low-temperature side heat medium flowing out from the second low-temperature side three-way valve 52b. The low-temperature side radiator 56 is arranged together with the outdoor heat exchanger 16 of the heat pump cycle 10 on the front side of the drive unit room.

[0098] The outlet of the low-temperature side radiator 56 is connected to the inlet side of one of the third heat medium connectors 53c. The outlet of the third heat medium connector 53c is connected to the suction port side of the second low-temperature side pump 51b.

[0099] The electric heater 54 is a heat-generating part that generates heat for heating the low-temperature side heat medium. In this embodiment, the electric heater 54 is a PTC heater with a PTC element (i.e., a positive characteristic thermistor), which generates heat by supplying electricity to heat the low-temperature side heat medium flowing through the heating path. The outlet of the heating medium flow path of the electric heater 54 is connected to the inlet side of the heat medium passage 20b of the chiller 20.

[0100] The outlet of the heat medium passage 20b of the chiller 20 is connected to the inlet side of the fourth heat medium connector 53d. One outlet of the fourth heat medium connector 53d is connected to the inlet side of the other side of the second heat medium connector 53b. The other outlet of the fourth heat medium connector 53d is connected to the inlet side of the other side of the third heat medium connector 53c.

[0101] As can be seen from the above description, the high-temperature side heat medium circuit 40 and the low-temperature side heat medium circuit 50 in this embodiment are configured as completely independent heat medium circuits. Therefore, the high-temperature side heat medium and the low-temperature side heat medium will not mix. In addition, the electric heater 54, which serves as the heating element, is only provided in the low-temperature side heat medium circuit 50. The high-temperature side heat medium circuit 40 is only equipped with a water refrigerant heat exchanger 12 as a structure for heating the high-temperature side heat medium.

[0102] Next, the interior air conditioning unit 30 will be described. The interior air conditioning unit 30 is a unit that integrates multiple components to blow air conditioned to an appropriate temperature into appropriate parts of the vehicle interior. The interior air conditioning unit 30 is located inside the instrument panel (instrument panel) at the front of the vehicle interior.

[0103] like Figure 1 As shown, the indoor air conditioning unit 30 is a structure that houses an indoor fan 32, an indoor evaporator 18, a heater core 42, etc., within an air conditioning housing 31 that forms an air passage for supplying air. The air conditioning housing 31 is formed of a resin (e.g., polypropylene) that has a certain degree of elasticity and excellent strength.

[0104] An indoor / outdoor air switching device 33 is disposed at the upstream side of the air supply airflow in the air conditioning housing 31. The indoor / outdoor air switching device 33 switches the introduction of indoor air (i.e., air inside the vehicle) and outdoor air (i.e., air outside the vehicle) into the air conditioning housing 31. The operation of the indoor / outdoor air switching device 33 is controlled according to the control signal output from the control device 60.

[0105] An indoor air supply fan 32 is disposed downstream of the airflow from the indoor / outdoor air switching device 33. The indoor air supply fan 32 blows air drawn in through the indoor / outdoor air switching device 33 into the vehicle interior. The indoor air supply fan 32 is an electric fan driven by a centrifugal multi-bladed fan driven by an electric motor. The rotational speed (i.e., air supply capacity) of the indoor air supply fan 32 is controlled according to the control voltage output from the control device 60.

[0106] An indoor evaporator 18 and a heater core 42 are disposed downstream of the supply airflow of the indoor fan 32. The indoor evaporator 18 is disposed upstream of the supply airflow compared to the heater core 42. In addition, a cold air bypass passage 35 is formed in the air conditioning housing 31 to allow the supply air after passing through the indoor evaporator 18 to flow around the heater core 42.

[0107] An air mixing door 34 is provided on the downstream side of the supply air flow of the indoor evaporator 18 inside the air conditioner housing 31 and on the upstream side of the supply air flow of the heater core 42 and the cold air bypass passage 35.

[0108] The air mixing door 34 is an airflow ratio regulating unit that adjusts the airflow ratio between the supply air passing through the heater core 42 and the supply air passing through the cold air bypass passage 35 in the supply air after passing through the indoor evaporator 18. The air mixing door 34 is driven by an electric actuator for the air mixing door. The operation of the electric actuator for the air mixing door is controlled according to the control signal output from the control device 60.

[0109] A mixing space 36 is provided downstream of the supply air flow of the heater core 42 and the cold air bypass passage 35. The mixing space 36 is a space in which the supply air heated by the heater core 42 is mixed with the supply air that has not been heated by passing through the cold air bypass passage 35. Therefore, in the indoor air conditioning unit 30, the temperature of the supply air (i.e., the air conditioning air) mixed in the mixing space 36 can be adjusted by adjusting the opening of the air mixing door 34.

[0110] At the downstream end of the air supply airflow in the air conditioning housing 31, a plurality of openings (not shown) are formed for blowing the air supply air mixed in the mixing space 36 toward the vehicle interior. The plurality of openings communicate with a plurality of air outlets formed in the vehicle interior. Among the plurality of air outlets are a face air outlet, a foot air outlet, and a defrost air outlet.

[0111] The face air outlet is used to blow air towards the upper body of the occupant. The foot air outlet is used to blow air towards the feet of the occupant. The defrost air outlet is used to blow air towards the windshield of the vehicle.

[0112] Each of these openings is equipped with a blow-out mode door (not shown). The blow-out mode door opens and closes by controlling the openings. The blow-out mode door is driven by an electric actuator. The operation of the electric actuator for the blow-out mode door is controlled according to a control signal output from the control device 60.

[0113] Therefore, in the indoor air conditioning unit 30, by switching the opening hole that opens according to the blowing mode door, the part of the air conditioning air blown out of the vehicle interior can be changed.

[0114] Next, an overview of the electrical control unit of this embodiment will be described. The control device 60 is composed of a well-known microcomputer including a CPU, ROM, RAM, etc., and its peripheral circuitry. The control device 60 performs various calculations and processes based on the control program stored in the ROM, and controls the operation of various controllable devices 11, 14a-14c, 15a, 15b, 32-34, 51a, 51b, 52a, 52b, 54, etc., connected to the output side.

[0115] In addition, such as Figure 2As shown in the block diagram, the input side of the control device 60 is connected to the following sensors: interior air temperature sensor 61, exterior air temperature sensor 62, sunlight sensor 63, first refrigerant temperature sensors 64a to third refrigerant temperature sensors 64c, evaporator temperature sensor 64f, first refrigerant pressure sensors 65a to third refrigerant pressure sensors 65c, high-temperature side heat medium temperature sensor 66a, first low-temperature side heat medium temperature sensor 67a to third low-temperature side heat medium temperature sensor 67c, battery temperature sensor 68, air conditioning fan temperature sensor 69a, and intake air temperature sensor 69b. Furthermore, the detection signals from these sensor groups are input to the control device 60.

[0116] Interior air temperature sensor 61 is an interior air temperature detection unit that detects the interior temperature (interior air temperature) Tr. Outside air temperature sensor 62 is an outside air temperature detection unit that detects the outside temperature (outside air temperature) Tam. Sunlight sensor 63 is a sunlight intensity detection unit that detects the amount of sunlight As shining into the vehicle interior.

[0117] The first refrigerant temperature sensor 64a is a first refrigerant temperature detection unit that detects the temperature of the refrigerant discharged from the compressor 11, i.e., the first refrigerant temperature TR1. The second refrigerant temperature sensor 64b is a second refrigerant temperature detection unit that detects the temperature of the refrigerant flowing out of the refrigerant passage 12a of the water-refrigerant heat exchanger 12, i.e., the second refrigerant temperature TR2. The third refrigerant temperature sensor 64c is a third refrigerant temperature detection unit that detects the temperature of the refrigerant flowing out of the outdoor heat exchanger 16, i.e., the third refrigerant temperature TR3.

[0118] The evaporator temperature sensor 64f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18. In this embodiment, the evaporator temperature sensor 64f specifically detects the temperature of the heat exchange fins of the indoor evaporator 18.

[0119] The first refrigerant pressure sensor 65a is a first refrigerant pressure detection unit that detects the pressure of the refrigerant discharged from the compressor 11, i.e., the first refrigerant pressure PR1. The second refrigerant pressure sensor 65b is a second refrigerant pressure detection unit that detects the pressure of the refrigerant flowing out of the refrigerant passage 12a of the water-refrigerant heat exchanger 12, i.e., the second refrigerant pressure PR2. The third refrigerant pressure sensor 65c is a third refrigerant pressure detection unit that detects the pressure of the refrigerant flowing out of the outdoor heat exchanger 16, i.e., the third refrigerant pressure PR3.

[0120] The high-temperature side heat medium temperature sensor 66a is a high-temperature side heat medium temperature detection unit that detects the temperature of the high-temperature side heat medium flowing into the heater core 42, i.e., the high-temperature side heat medium temperature TWH.

[0121] The first low-temperature side heat medium temperature sensor 67a is a first low-temperature side heat medium temperature detection unit that detects the temperature of the low-temperature side heat medium flowing into the cooling water passage 80a of the battery 80 from the first low-temperature side pump 51a, namely the first low-temperature side heat medium temperature TWL1.

[0122] The second low-temperature side heat medium temperature sensor 67b is a second low-temperature side heat medium temperature detection unit that detects the temperature of the low-temperature side heat medium, i.e., the second low-temperature side heat medium temperature TWL2, which is pumped from the second low-temperature side pump 51b into the cooling water passage 81a of the high-power equipment 81.

[0123] The third low-temperature side heat medium temperature sensor 67c is a chiller inlet side heat medium temperature detection unit that detects the temperature of the low-temperature side heat medium flowing into the heat medium passage 20b of the chiller 20, i.e., the inlet side heat medium temperature TWin.

[0124] The battery temperature sensor 68 is a battery temperature detection unit that detects the battery temperature TB (i.e., the temperature of the battery 80). In this embodiment, the battery temperature sensor 68 has multiple temperature detection units that detect the temperature of multiple parts of the battery 80. Therefore, in the control device 60, the temperature difference between each individual battery cell forming the battery 80 can be detected. Furthermore, the average value of the detection values ​​from the multiple temperature sensors is used as the battery temperature TB.

[0125] Air conditioning air temperature sensor 69a is an air conditioning air temperature detection unit that detects the temperature of the supply air blown from the mixing space 36 into the vehicle interior, i.e., the supply air temperature TAV. Intake air temperature sensor 69b is an intake air temperature detection unit that detects the temperature of the supply air flowing into the heater core 42, i.e., the intake air temperature TAin.

[0126] Moreover, such as Figure 2 As shown, the input side of the control device 60 is connected to the air conditioning control panel 70. The air conditioning control panel 70 is located near the instrument panel at the front of the vehicle interior. Operation signals from various operation switches located on the air conditioning control panel 70 are input to the control device 60.

[0127] The various operating switches installed on the control panel 70 for air conditioning include automatic switch, air conditioning switch, air volume setting switch, temperature setting switch, etc.

[0128] The automatic switch is an operating unit for the user to set or deactivate the automatic control of the vehicle's air conditioning. The air conditioning switch is an operating unit for the user to request cooling of the supplied air through the indoor evaporator 18. The fan speed setting switch is an operating unit for the user to manually set the fan speed of the indoor air supply fan 32. The temperature setting switch is an operating unit for the user to set the set temperature Tset inside the vehicle.

[0129] Furthermore, the control device 60 of this embodiment is a component that integrates a control unit for controlling various controllable devices connected to its output side. Moreover, the structure (i.e., hardware and software) within the control device 60 that controls the operation of each controllable device constitutes the control unit for controlling the operation of each controllable device.

[0130] For example, the structure in the control device 60 that controls the refrigerant discharge capacity (specifically, the rotational speed of the compressor 11) of the compressor 11 constitutes a discharge capacity control unit 60a. Furthermore, the structure that controls the air supply capacity (specifically, the rotational speed of the indoor air supply fan 32) of the indoor air supply fan 32 constitutes an air supply capacity control unit 60b. Additionally, the structure that controls the heating capacity of the electric heater 54 constitutes a heating capacity control unit 60c.

[0131] Next, the operation of the air conditioning unit 1 with the above-described structure will be explained. As described above, the air conditioning unit 1 is capable of regulating the air inside the vehicle and the temperature of the vehicle's equipment. To this end, in the air conditioning unit 1, various operating modes are executed by switching the circuit structure of the heat pump cycle 10 and the circuit structure of the low-temperature side heat medium circuit 50.

[0132] The air conditioning unit 1 has two operating modes: an operating mode for air conditioning inside the vehicle and an operating mode for temperature regulation of the vehicle equipment. The air conditioning unit 1 can appropriately combine the air conditioning operating mode and the temperature regulation operating mode for execution.

[0133] Therefore, in air conditioning unit 1, it is possible to regulate the air inside the vehicle without regulating the temperature of the vehicle's onboard equipment. Furthermore, it is possible to regulate the temperature of the vehicle's onboard equipment without regulating the air inside the vehicle. Additionally, it is possible to regulate the temperature of the vehicle's onboard equipment while simultaneously regulating the air inside the vehicle.

[0134] First, the operating modes for air conditioning will be explained. The operating modes for air conditioning in this embodiment are (A1) cooling mode, (A2) series dehumidification and heating mode, (A3) parallel dehumidification and heating mode, and (A4) heating mode.

[0135] (A1) Cooling mode is an operating mode that cools the vehicle interior by cooling the supplied air and blowing it into the vehicle interior.

[0136] (A2) The series dehumidification and heating mode is an operation mode that dehumidifies and heats the vehicle interior by reheating the cooled and dehumidified supply air and blowing it out into the vehicle interior.

[0137] (A3) Parallel dehumidification and heating mode is an operation mode that dehumidifies and heats the vehicle interior by reheating the cooled and dehumidified supply air with a higher heating capacity than the series dehumidification and heating mode and blowing it out into the vehicle interior.

[0138] (A4) Heating mode is an operating mode that heats the vehicle interior by heating the supplied air and blowing it into the vehicle interior.

[0139] The switching of the air conditioning operating mode is performed by executing the air conditioning control program stored in the control device 60. The air conditioning control program is executed when the automatic switch on the operation panel 70 is turned on and the automatic control operation of the vehicle's air conditioning is set.

[0140] In the main program of the air conditioning control program, the detection signals from the aforementioned sensor group and the operation signals from the operation switches on the operation panel 70 are read in at predetermined intervals. Then, based on the read detection signals and operation information, the target temperature of the air blown into the vehicle interior, i.e., the target blowing temperature TAO, is calculated.

[0141] More specifically, the target blowout temperature TAO is calculated using the following formula F1.

[0142] TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×As+C…(F1)

[0143] In addition, Tset is the set temperature inside the vehicle interior, set via the temperature setting switch on the operation panel 70. Tr is the interior air temperature detected by the interior air temperature sensor 61. Tam is the outside air temperature detected by the outside air temperature sensor 62. As is the amount of sunlight detected by the sunlight sensor 63. Kset, Kr, Kam, and Ks are control gains, and C is a constant used for correction.

[0144] Then, with the air conditioning switch on the control panel 70 turned on, and the target blowing temperature TAO being lower than the predetermined target cooling heat medium temperature KTAO1, the air conditioning operation mode is switched to cooling mode.

[0145] In addition, when the air conditioner switch is turned on, if the target blowout temperature TAO is higher than the target cooling heat medium temperature KTAO1 and the outside air temperature Tam is higher than the predetermined dehumidification and heating target heat medium temperature KTAO2, the air conditioning operation mode is switched to series dehumidification and heating mode.

[0146] In addition, when the air conditioner is switched on, if the target blowout temperature TAO is above the target cooling heat medium temperature KTAO1 and the outside air temperature Tam is below the target dehumidification and heating heat medium temperature KTAO2, the air conditioning operation mode is switched to parallel dehumidification and heating mode.

[0147] In addition, when the cooling switch of the air conditioner is not turned on, the air conditioning operation mode is switched to heating mode.

[0148] Therefore, the cooling mode is mainly used when the outside air temperature is high, such as in summer. The series dehumidification and heating mode is mainly used in spring or autumn. The parallel dehumidification and heating mode is mainly used when a higher heating capacity than the series dehumidification and heating mode is needed to heat the supply air, such as in early spring or late autumn. The heating mode is mainly used when the outside air temperature is low in winter. The following is a detailed explanation of the operation of each air conditioning mode.

[0149] (A1) Cooling Mode

[0150] In cooling mode, control device 60 sets heating expansion valve 14a to fully open and cooling expansion valve 14b to a throttling state to reduce refrigerant pressure. Cooling expansion valve 14c is controlled according to the temperature regulation operating mode. This is also the case in other air conditioning operating modes. Additionally, control device 60 closes dehumidification valve 15a and heating valve 15b.

[0151] Therefore, in the heat pump cycle 10 of the cooling mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: water refrigerant heat exchanger 12, fully open heating expansion valve 14a, outdoor heat exchanger 16, cooling expansion valve 14b, indoor evaporator 18, liquid receiver 21, and the suction port of the compressor 11.

[0152] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotational speed of the compressor 11 so that the evaporator temperature Tefin detected by the evaporator temperature sensor 64f is close to the target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target blow-out temperature TEO and with reference to the control mapping diagram pre-stored in the control device 60.

[0153] In addition, the control device 60 controls the throttling opening of the refrigeration expansion valve 14b so that the subcooling degree SC3 of the refrigerant flowing into the refrigeration expansion valve 14b is close to the target subcooling degree SCO3.

[0154] The subcooling degree SC3 of the refrigerant flowing into the refrigeration expansion valve 14b is calculated using the third refrigerant temperature TR3 detected by the third refrigerant temperature sensor 64c and the third refrigerant pressure PR3 detected by the third refrigerant pressure sensor 65c. The target subcooling degree SCO3 is determined based on the outside air temperature Tam and with reference to the control mapping diagram pre-stored in the control device 60, in a manner that makes the coefficient of performance (COP) of the cycle approach its maximum value.

[0155] In addition, the control device 60 controls the high-temperature side pump 41 to achieve a predetermined pressure delivery capacity.

[0156] Therefore, in the high-temperature side heat medium circuit 40 of the cooling mode, the high-temperature side heat medium, which is pressurized from the high-temperature side pump 41, circulates in the order of heat medium passage 12b of the water refrigerant heat exchanger 12, heater core 42, and suction port of the high-temperature side pump 41.

[0157] Furthermore, the control device 60 determines the rotational speed of the indoor fan 32 in a manner close to the target air delivery capacity determined by the air delivery capacity control unit 60b. Therefore, the air delivery capacity control unit 60b is the target air delivery capacity determination unit. More specifically, the air delivery capacity control unit 60b determines the speed based on the target blowout temperature TAO and by referring to a control mapping diagram pre-stored in the control device 60.

[0158] In the control mapping diagram used for the indoor fan 32, the air supply capacity is determined to be maximized when the target outlet temperature TAO is in the extremely low temperature region (i.e., during maximum cooling) or the extremely high temperature region (i.e., during maximum heating). Furthermore, the air supply capacity is determined to decrease as the target outlet temperature TAO moves from the extremely low or extremely high temperature region towards the intermediate temperature region. Finally, the air supply capacity is determined to be minimized when the target outlet temperature TAO is in the intermediate temperature region.

[0159] Additionally, the control device 60 controls the opening degree of the air mixing door 34 so that the supply air temperature TAV detected by the air conditioning air temperature sensor 69a is close to the target blowing temperature TAO. Furthermore, the control device 60 determines the opening and closing action of the blowing mode door based on the target blowing temperature TAO and with reference to the control mapping pre-stored in the control device 60.

[0160] Therefore, in the heat pump cycle 10 of the cooling mode, a vapor compression refrigeration cycle is configured to make the water refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as condensers (in other words, radiators) to dissipate heat from the refrigerant and condense it, and make the indoor evaporator 18 function as an evaporator to evaporate the refrigerant.

[0161] As a result, in the heat pump cycle 10 of the cooling mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. Then, the supply air is cooled by the indoor evaporator 18.

[0162] In addition, in the high-temperature side heat medium circuit 40 of the cooling mode, the heat medium heated by the water refrigerant heat exchanger 12 is supplied to the heater core 42.

[0163] In addition, in the cooling mode of the indoor air conditioning unit 30, the supply air blown from the indoor fan 32 is cooled in the indoor evaporator 18. The supply air cooled in the indoor evaporator 18 is temperature-regulated by adjusting the opening of the air mixing door 34 to be close to the target blowing temperature TAO. Furthermore, by blowing the temperature-regulated supply air into the vehicle interior, cooling of the vehicle interior is achieved.

[0164] (A2) Series dehumidification and heating mode

[0165] In the series dehumidification and heating mode, the control device 60 sets the heating expansion valve 14a to a throttling state and the cooling expansion valve 14b to a throttling state. Additionally, the control device 60 closes the dehumidification on / off valve 15a and the heating on / off valve 15b.

[0166] Therefore, in the heat pump cycle 10 of the series dehumidification and heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in sequence through the water refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the cooling expansion valve 14b, the indoor evaporator 18, the liquid receiver 21, and the suction port of the compressor 11.

[0167] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the compressor 11 in the same way as the cooling mode.

[0168] Furthermore, the control device 60 determines the throttling opening of the heating expansion valve 14a and the cooling expansion valve 14b in a manner that brings the COP close to its maximum value, based on the target outlet temperature TAO and referring to a control mapping diagram pre-stored in the control device 60. In the control mapping diagram of the series dehumidification heating mode, the throttling opening of the heating expansion valve 14a is decreased and the throttling opening of the cooling expansion valve 14b is increased as the target outlet temperature TAO increases.

[0169] In addition, the control device 60 controls the operation of the high-temperature side pump 41 and the like in the high-temperature side heat medium circuit 40 in the same way as in the cooling mode. Furthermore, the control device 60 controls the operation of the indoor air conditioning unit 30's indoor fan 32 and the like in the cooling mode.

[0170] Therefore, in the heat pump cycle 10 of the series dehumidification and heating mode, a vapor compression refrigeration cycle is configured, in which the water refrigerant heat exchanger 12 functions as a condenser and the indoor evaporator 18 functions as an evaporator. Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, the outdoor heat exchanger 16 functions as a condenser. Conversely, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, the outdoor heat exchanger 16 functions as an evaporator.

[0171] As a result, in the heat pump cycle 10 of the series dehumidification and heating mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. Then, the supply air is cooled by the indoor evaporator 18.

[0172] In addition, in the high-temperature side heat medium circuit 40 of the series dehumidification and heating mode, the heat medium heated by the water refrigerant heat exchanger 12 is supplied to the heater core 42.

[0173] Furthermore, in the indoor air conditioning unit 30 operating in series dehumidification and heating mode, the supply air blown from the indoor fan 32 is cooled and dehumidified in the indoor evaporator 18. The supply air, after being cooled and dehumidified in the indoor evaporator 18, is temperature-regulated by adjusting the opening of the air mixing door 34 to approach the target outlet temperature (TAO). Dehumidification and heating of the vehicle interior are achieved by blowing temperature-regulated supply air into the vehicle interior.

[0174] Furthermore, in the heat pump cycle 10 of the series dehumidification and heating mode, as the target outlet temperature TAO increases, the throttling opening of the heating expansion valve 14a decreases, while the throttling opening of the cooling expansion valve 14b increases. Thus, as the target outlet temperature TAO increases, the heating capacity of the supply air in the heater core 42 can be improved.

[0175] More specifically, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, the temperature difference between the saturation temperature of the refrigerant in the outdoor heat exchanger 16 and the outside air temperature Tam can be reduced as the target outlet temperature TAO increases. Therefore, with the increase of the target outlet temperature TAO, the amount of heat dissipated by the refrigerant in the outdoor heat exchanger 16 to the outside air can be reduced, while the amount of heat dissipated from the refrigerant to the heat medium in the water refrigerant heat exchanger 12 can be increased.

[0176] Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, the temperature difference between the outside air temperature Tam and the refrigerant in the outdoor heat exchanger 16 can be widened as the target outlet temperature TAO increases. Therefore, with the increase of the target outlet temperature TAO, the heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 16 can increase, and the heat dissipation from the refrigerant to the heat medium in the water refrigerant heat exchanger 12 can increase.

[0177] As a result, in the series dehumidification and heating mode, the heating capacity of the supply air in the heater core 42 can be improved as the target blow-out temperature TAO increases.

[0178] (A3) Parallel dehumidification and heating mode

[0179] In parallel dehumidification and heating mode, the control device 60 sets the heating expansion valve 14a to a throttling state and the cooling expansion valve 14b to a throttling state. Additionally, the control device 60 opens the dehumidification on / off valve 15a and the heating on / off valve 15b.

[0180] Therefore, in the heat pump cycle 10 of the parallel dehumidification and heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates sequentially through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the receiver 21, and the suction port of the compressor 11. Simultaneously, the refrigerant circuit is switched to a refrigerant circuit that circulates sequentially through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the dehumidification passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the receiver 21, and the suction port of the compressor 11. That is, the refrigerant circuit is switched to a refrigerant circuit in which the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel with respect to the refrigerant flow.

[0181] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotational speed of the compressor 11 so that the first refrigerant pressure PR1 detected by the first refrigerant pressure sensor 65a approaches the target condensing pressure PDO.

[0182] The target condensing pressure PDO is determined such that the high-temperature side heat medium temperature TWH detected by the high-temperature side heat medium temperature sensor 66a is close to a predetermined target high-temperature side heat medium temperature TWHO (approximately 50°C in this embodiment). The target high-temperature side heat medium temperature TWHO is set such that the temperature of the supply air can be raised to a temperature sufficient to achieve adequate heating of the vehicle interior by the heater core 42 constituting the heating unit.

[0183] Furthermore, the control device 60 determines the throttling opening of the heating expansion valve 14a and the cooling expansion valve 14b in a manner that brings the COP close to its maximum value, based on the target outlet temperature TAO and referring to a control mapping diagram pre-stored in the control device 60. In the control mapping diagram of the parallel dehumidification heating mode, the throttling opening of the heating expansion valve 14a is decreased and the throttling opening of the cooling expansion valve 14b is increased as the target outlet temperature TAO increases.

[0184] In addition, the control device 60 controls the operation of the high-temperature side pump 41 and the like in the high-temperature side heat medium circuit 40 in the same way as in the cooling mode. Furthermore, the control device 60 controls the operation of the indoor air conditioning unit 30's indoor fan 32 and the like in the cooling mode.

[0185] Therefore, in the heat pump cycle 10 of the parallel dehumidification and heating mode, a vapor compression refrigeration cycle is configured, in which the water refrigerant heat exchanger 12 functions as a condenser, and the outdoor heat exchanger 16 and the indoor evaporator 18 function as evaporators. As a result, in the heat pump cycle 10 of the parallel dehumidification and heating mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. Furthermore, the supply air is cooled by the indoor evaporator 18.

[0186] In addition, in the high-temperature side heat medium circuit 40 of the parallel dehumidification and heating mode, the heat medium heated by the water refrigerant heat exchanger 12 is supplied to the heater core 42.

[0187] In addition, in the parallel dehumidification and heating mode of the indoor air conditioning unit 30, the supply air blown from the indoor fan 32 is cooled and dehumidified in the indoor evaporator 18. After being cooled and dehumidified in the indoor evaporator 18, the supply air is temperature-regulated by adjusting the opening of the air mixing door 34 to approach the target blowing temperature TAO. Then, by blowing the temperature-regulated supply air into the vehicle interior, dehumidification and heating of the vehicle interior are achieved.

[0188] Furthermore, in the heat pump cycle 10 of the parallel dehumidification and heating mode, the throttling opening of the heating expansion valve 14a can be further reduced compared to the throttling opening of the cooling expansion valve 14b. As a result, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be lowered to a temperature lower than the refrigerant evaporation temperature in the indoor evaporator 18.

[0189] Therefore, in parallel dehumidification and heating mode, compared to series dehumidification and heating mode, the heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 16 increases, and the heat dissipation from the refrigerant to the heat medium in the water refrigerant heat exchanger 12 increases. As a result, in parallel dehumidification and heating mode, compared to series dehumidification and heating mode, the heating capacity of the supply air in the heater core 42 can be increased.

[0190] (A4) Heating Mode

[0191] In heating mode, the control device 60 sets the heating expansion valve 14a to a throttling state and the cooling expansion valve 14b to a fully closed state. Additionally, the control device 60 closes the dehumidification on / off valve 15a and opens the heating on / off valve 15b.

[0192] Therefore, in the heat pump cycle 10 of the heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of water refrigerant heat exchanger 12, heating expansion valve 14a, outdoor heat exchanger 16, heating passage 22b, receiver 21, and compressor 11 suction port.

[0193] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the compressor 11 in the same way as in the parallel dehumidification and heating mode.

[0194] In addition, the control device 60 controls the throttling opening of the heating expansion valve 14a so that the subcooling degree SC2 of the refrigerant flowing into the heating expansion valve 14a is close to the target subcooling degree SCO2.

[0195] The subcooling degree SC2 of the refrigerant flowing into the heating expansion valve 14a is calculated using the second refrigerant temperature TR2 detected by the second refrigerant temperature sensor 64b and the second refrigerant pressure PR2 detected by the second refrigerant pressure sensor 65b. Based on the second refrigerant temperature TR2 and referring to the control mapping diagram pre-stored in the control device 60, the target subcooling degree SCO2 is determined in a manner that brings the COP close to its maximum value.

[0196] In addition, the control device 60 controls the operation of the high-temperature side pump 41 and the like in the high-temperature side heat medium circuit 40 in the same way as in the cooling mode. Furthermore, the control device 60 controls the operation of the indoor air conditioning unit 30's indoor fan 32 and the like in the cooling mode.

[0197] Therefore, in the heat pump cycle 10 of the heating mode, a vapor compression refrigeration cycle is configured, in which the water refrigerant heat exchanger 12 functions as a condenser and the outdoor heat exchanger 16 functions as an evaporator. As a result, in the heat pump cycle 10 of the heating mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12.

[0198] In addition, in the high-temperature side heat medium circuit 40 of the heating mode, the heat medium heated by the water refrigerant heat exchanger 12 is supplied to the heater core 42.

[0199] In addition, in the heating mode of the indoor air conditioning unit 30, the supply air blown from the indoor fan 32 passes through the indoor evaporator 18. The supply air after passing through the indoor evaporator 18 is regulated by adjusting the opening of the air mixing door 34 to be close to the target blowing temperature TAO. Furthermore, heating of the vehicle interior is achieved by blowing the temperature-regulated supply air into the vehicle interior.

[0200] Next, the operating mode for temperature regulation will be explained. In the operating mode for temperature regulation, the temperature of the battery 80 and the high-voltage equipment 81, which are the objects of temperature regulation, is regulated.

[0201] As described above, in this embodiment, the appropriate temperature range of the battery 80 and the appropriate temperature of the power equipment 81 are different. Therefore, in the temperature regulation operation mode, the battery operation mode for regulating the temperature of the battery 80 and the power equipment operation mode for regulating the temperature of the power equipment 81 are executed in combination.

[0202] As for the operating modes of the battery, there are (B1) battery warm-up mode, (B2) battery temperature equalization mode and (B3) battery cooling mode.

[0203] (B1) The battery warm-up mode is an operation mode in which the battery 80 is warmed up by the low-temperature side heat medium heated by the electric heater 54.

[0204] (B2) Battery temperature equalization mode is an operating mode that equalizes the temperature of each cell in the battery 80.

[0205] (B3) The battery cooling mode is the operating mode in which the battery 80 is cooled by the heat medium cooled by the cooler 20.

[0206] In addition, the operating modes for high-voltage electrical equipment include (C1) high-voltage electrical equipment warm-up mode, (C2) high-voltage electrical equipment waste heat recovery mode, and (C3) high-voltage electrical equipment cooling mode.

[0207] (C1) The power equipment warm-up mode is the operation mode of power equipment 81 that is warmed up by the low-temperature side heat medium heated by the electric heater 54.

[0208] (C2) The waste heat recovery mode of the high-power equipment is an operation mode in which the heat generated by the high-power equipment 81 is absorbed by the low-pressure refrigerant through the chiller 20.

[0209] (C3) The power equipment cooling mode is the operation mode of power equipment 81 which is cooled by the heat medium cooled by the low-temperature side radiator 56.

[0210] Switching between operating modes for temperature regulation is performed by executing a temperature regulation control program stored in the control device 60. This temperature regulation control program is executed regardless of whether the user requests air conditioning in the vehicle interior, and is also executed when the vehicle system is started, or when the battery 80 is being charged from an external power source.

[0211] In the temperature control program, the detection signals from the aforementioned sensor group are read in at predetermined intervals. Then, the operating mode for temperature control is switched based on the read detection signals.

[0212] More specifically, in the temperature regulation control program, the battery operating mode is switched based on the battery temperature TB detected by the battery temperature sensor 68 and with reference to a control mapping diagram pre-stored in the control device 60. In the control mapping diagram, as the battery temperature TB rises, the mode is switched in the following order: (B1) battery warm-up mode, (B2) battery temperature equalization mode, and (B3) battery cooling mode.

[0213] Furthermore, in the temperature regulation control program, the operating mode for the high-voltage equipment is switched based on the second low-temperature side heat medium temperature TWL2 detected by the second low-temperature side heat medium temperature sensor 67b and with reference to the control mapping diagram pre-stored in the control device 60. In the control mapping diagram, as the second low-temperature side heat medium temperature TWL2 rises, the operation mode is switched in the following order: (C1) high-voltage equipment warm-up mode, (C2) high-voltage equipment waste heat recovery mode, and (C3) high-voltage equipment cooling mode.

[0214] However, if the battery operation mode and the high-voltage equipment operation mode cannot be executed simultaneously due to the condition of the circuit structure of the low-temperature side heat medium circuit 50, the battery operation mode takes priority. For example, if both the (B3) battery cooling mode and the (C1) high-voltage equipment warm-up mode are selected at the same time, the (C1) high-voltage equipment warm-up mode is not executed, and the (B3) battery cooling mode is executed instead. The detailed operation of each temperature regulation operation mode will be explained below.

[0215] (B1) Battery Warm-up Mode

[0216] In battery warm-up mode, control device 60 sets cooling expansion valve 14c to the fully closed state. Therefore, in battery warm-up mode, refrigerant does not flow into the chiller 20.

[0217] Additionally, the control device 60 controls the operation of the first cryogenic side three-way valve 52a to allow the cryogenic side heat medium flowing from the cooling water passage 80a of the battery 80 to flow towards the electric heater 54. Furthermore, the control device 60 controls the operation of the electric heater 54 to enable it to perform a predetermined heating capacity. Additionally, the control device 60 controls the operation of the first cryogenic side pump 51a to enable it to perform a predetermined pressure delivery capacity.

[0218] Therefore, in the low-temperature side heat medium circuit 50 of the battery warm-up mode, the low-temperature side heat medium pressurized from the first low-temperature side pump 51a is switched to circulate in the following order: cooling water passage 80a of the battery 80, electric heater 54, heat medium passage 20b of the chiller 20, and suction port of the first low-temperature side pump 51a.

[0219] Therefore, in the low-temperature side heat transfer medium circuit 50 of the battery warm-up mode, the low-temperature side heat transfer medium heated by the electric heater 54 is drawn into the first low-temperature side pump 51a. The low-temperature side heat transfer medium pumped from the first low-temperature side pump 51a flows into the cooling water passage 80a of the battery 80, dissipating heat to each cell of the battery 80. Thus, the battery 80 is warmed up.

[0220] (B2) Battery temperature equalization mode

[0221] In battery temperature equalization mode, control device 60 controls the operation of the first low-temperature side three-way valve 52a to allow the low-temperature side heat medium flowing out from the cooling water passage 80a of the battery 80 to flow out to the battery bypass passage 55a. Additionally, control device 60 controls the operation of the first low-temperature side pump 51a to enable it to perform a predetermined pressure delivery capacity.

[0222] Therefore, in the low-temperature side heat medium circuit 50 of the battery temperature equalization mode, the low-temperature side heat medium pressurized from the first low-temperature side pump 51a is switched to circulate in the order of the cooling water passage 80a of the battery 80, the battery bypass passage 55a, and the suction port of the high-temperature side pump 41.

[0223] Therefore, in the low-temperature side heat medium circuit 50 of the battery temperature equalization mode, the low-temperature side heat medium, which is pumped from the first low-temperature side pump 51a, flows through the cooling water passage 80a of the battery 80 to equalize the temperature of each battery cell forming the battery 80.

[0224] Here, the battery temperature equalization mode is an operating mode aimed at equalizing the temperature of each individual cell in battery 80. Therefore, even if the battery temperature equalization mode is selected based on the battery temperature TB, the battery temperature equalization mode can be stopped if temperature equalization of battery 80 is not required. A case where temperature equalization of battery 80 is not required includes situations where the temperature difference ΔTB between individual cells is smaller than a predetermined target temperature difference ΔKTB between individual cells.

[0225] (B3) Battery Cooling Mode

[0226] The battery cooling mode is an operating mode in which the battery 80 is cooled by a heat transfer medium cooled by the motor 20. Therefore, when the compressor 11 of the heat pump cycle 10 operates as in air conditioning, the control device 60 sets the cooling expansion valve 14c of the heat pump cycle 10 to a throttling state. Furthermore, when the air conditioning operating mode is (A4) heating mode, the control device 60 opens the dehumidification on / off valve 15a and the heating on / off valve 15b.

[0227] Therefore, in the heat pump cycle 10 of the battery cooling mode, the low-pressure refrigerant, after being depressurized by the cooling expansion valve 14c, flows into the refrigerant passage 20a of the chiller 20. The refrigerant flowing out of the refrigerant passage 20a of the chiller 20 flows into the receiver 21 via the sixth refrigerant connector 13f and the fourth refrigerant connector 13d.

[0228] Furthermore, when the battery cooling mode is executed during the (A4) heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates sequentially through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the receiver 21, and the suction port of the compressor 11. Simultaneously, the refrigerant circuit is switched to a refrigerant circuit that circulates sequentially through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the dehumidification passage 22a, the cooling expansion valve 14c, the chiller 20, the receiver 21, and the suction port of the compressor 11. That is, the outdoor heat exchanger 16 and the chiller 20 are connected in parallel with respect to the refrigerant flow in the refrigerant circuit.

[0229] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the throttling opening of the cooling expansion valve 14c so that the first low-temperature side heat medium temperature TWL1 detected by the first low-temperature side heat medium temperature sensor 67a is close to the battery target temperature TWLO1. The battery target temperature TWLO1 is set to enable the battery 80 to operate properly.

[0230] Additionally, the control device 60 controls the operation of the first cryogenic side three-way valve 52a to allow the cryogenic side heat medium flowing from the cooling water passage 80a of the battery 80 to flow towards the electric heater 54. Furthermore, the control device 60 stops the power supply to the electric heater 54. Additionally, the control device 60 controls the operation of the first cryogenic side pump 51a to ensure it performs a predetermined pressure delivery capacity.

[0231] Therefore, in the low-temperature side heat medium circuit 50 of the battery cooling mode, the low-temperature side heat medium pressurized from the first low-temperature side pump 51a is switched to circulate in the following order: cooling water passage 80a of the battery 80, electric heater 54, heat medium passage 20b of the chiller 20, and suction port of the first low-temperature side pump 51a.

[0232] Therefore, in the battery-cooled heat pump cycle 10 of the air conditioner, a vapor compression refrigeration cycle is configured, in which either the water refrigerant heat exchanger 12 or the outdoor heat exchanger 16 functions as a condenser, and at least the chiller 20 functions as an evaporator. As a result, in the battery-cooled heat pump cycle 10 of the air conditioner, the low-temperature side heat medium is cooled by the chiller 20.

[0233] Additionally, in the low-temperature side heat transfer medium circuit 50, the low-temperature side heat transfer medium, after being cooled by the chiller 20, is drawn into the first low-temperature side pump 51a. The low-temperature side heat transfer medium pressurized from the first low-temperature side pump 51a flows into the cooling water passage 80a of the battery 80, absorbing heat from each individual cell of the battery 80. Thus, the battery 80 is cooled.

[0234] Next, the battery cooling mode in non-air conditioning will be explained. In the battery cooling mode in non-air conditioning, the control device 60 sets the heating expansion valve 14a to the fully open state, the cooling expansion valve 14b to the fully closed state, and the cooling expansion valve 14c to the throttling state. In addition, the control device 60 closes the dehumidification on / off valve 15a and the heating on / off valve 15b.

[0235] Therefore, in the battery cooling mode 10 in non-air conditioning, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the following order: water refrigerant heat exchanger 12, fully open heating expansion valve 14a, outdoor heat exchanger 16, cooling expansion valve 14c, chiller 20, receiver 21, and the suction port of compressor 11.

[0236] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotational speed of the compressor 11 to enable it to perform its discharge capacity for a predetermined battery cooling mode. In addition, the control device 60 controls the throttling opening of the cooling expansion valve 14c to bring the temperature of the first low-temperature side heat medium TWL1 close to the target temperature TWLO1 for the battery.

[0237] Furthermore, the control device 60 controls the operation of the first low-temperature side three-way valve 52a, etc., in the same way as in the battery cooling mode of the air conditioner. Therefore, in the low-temperature side heat medium circuit 50 of the non-air conditioner battery cooling mode, the circuit is switched to circulate the low-temperature side heat medium in the same order as in the battery cooling mode of the air conditioner.

[0238] Therefore, in the battery-cooled heat pump cycle 10 in non-air-conditioned conditions, a vapor compression refrigeration cycle is configured, in which the outdoor heat exchanger 16 functions as a condenser and the chiller 20 functions as an evaporator. As a result, in the battery-cooled heat pump cycle 10 in non-air-conditioned conditions, the low-temperature side heat medium is cooled by the chiller 20.

[0239] In addition, the battery 80 is cooled in the same way as the battery cooling mode in the air conditioning in the low-temperature side heat medium circuit 50.

[0240] (C1) Power Equipment Warm-up Mode

[0241] In the high-voltage equipment warm-up mode, the control device 60 sets the cooling expansion valve 14c to the fully closed state. Therefore, in the high-voltage equipment warm-up mode, refrigerant does not flow into the chiller 20.

[0242] Additionally, the control device 60 controls the operation of the second cryogenic side three-way valve 52b to allow the cryogenic side heat medium flowing from the cooling water passage 81a of the high-voltage equipment 81 to flow towards the electric heater 54. Furthermore, the control device 60 controls the operation of the electric heater 54 to enable it to perform a predetermined heating capacity. Additionally, the control device 60 controls the operation of the second cryogenic side pump 51b to enable it to perform a predetermined pressure delivery capacity.

[0243] Therefore, in the low-temperature side heat medium circuit 50 of the power equipment warm-up mode, the low-temperature side heat medium pressurized from the second low-temperature side pump 51b is switched to circulate in the order of cooling water passage 81a of the power equipment 81, electric heater 54, heat medium passage 20b of the chiller 20, and suction port of the second low-temperature side pump 51b.

[0244] Therefore, in the low-temperature side heat medium circuit 50 of the high-voltage equipment warm-up mode, the low-temperature side heat medium heated by the electric heater 54 is drawn into the second low-temperature side pump 51b. The low-temperature side heat medium pressurized from the second low-temperature side pump 51b flows into the cooling water passage 81a of the high-voltage equipment 81, dissipating heat to the high-voltage equipment 81. Thus, the high-voltage equipment 81 is warmed up.

[0245] (C2) Waste heat recovery mode for high-power electrical equipment

[0246] The waste heat recovery mode for high-voltage electrical equipment is an operating mode that utilizes the waste heat from the high-voltage electrical equipment 81 as a heating source for the supplied air. Therefore, the waste heat recovery mode for high-voltage electrical equipment is implemented in air conditioning.

[0247] In the waste heat recovery mode of the high-power equipment, the cooling expansion valve 14c of the heat pump cycle 10 is set to a throttling state. Furthermore, when the air conditioning operation mode is (A4) heating mode, the control device 60 opens the dehumidification on / off valve 15a and the heating on / off valve 15b.

[0248] Therefore, in the heat pump cycle 10 of the high-power equipment waste heat recovery mode, the low-pressure refrigerant after being depressurized by the cooling expansion valve 14c flows into the refrigerant passage 20a of the chiller 20. The refrigerant flowing out of the refrigerant passage 20a of the chiller 20 flows into the liquid receiver 21 via the sixth refrigerant connector 13f and the fourth refrigerant connector 13d.

[0249] Furthermore, when executing the waste heat recovery mode of the high-voltage electrical equipment in the (A4) heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates sequentially through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the receiver 21, and the suction port of the compressor 11. Simultaneously, the refrigerant circuit is switched to a refrigerant circuit that circulates sequentially through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the dehumidification passage 22a, the cooling expansion valve 14c, the chiller 20, the receiver 21, and the suction port of the compressor 11. That is, the outdoor heat exchanger 16 and the chiller 20 are switched to a refrigerant circuit connected in parallel with respect to the refrigerant flow.

[0250] Furthermore, the control device 60 appropriately controls the operation of other controlled equipment. For example, the control device 60 controls the throttling opening of the cooling expansion valve 14c to bring the temperature of the second low-temperature side heat medium TWL2 close to the target temperature TWLO2 for the power equipment. The target temperature TWLO2 for the power equipment is set to enable the power equipment 81 to operate properly.

[0251] Additionally, the control device 60 controls the operation of the second cryogenic side three-way valve 52b to allow the cryogenic side heat medium flowing from the cooling water passage 81a of the high-voltage equipment 81 to flow towards the electric heater 54. Furthermore, the control device 60 stops the power supply to the electric heater 54. Additionally, the control device 60 controls the operation of the second cryogenic side pump 51b to ensure it performs a predetermined pressure delivery capacity.

[0252] Therefore, in the low-temperature side heat medium circuit 50 of the high-power equipment waste heat recovery mode, the low-temperature side heat medium pressurized from the second low-temperature side pump 51b is switched to circulate in the order of cooling water passage 81a of the high-power equipment 81, electric heater 54, heat medium passage 20b of the chiller 20, and suction port of the second low-temperature side pump 51b.

[0253] Therefore, in the heat pump cycle 10 of the high-power equipment waste heat recovery mode in air conditioning, a vapor compression refrigeration cycle is configured, in which either the water refrigerant heat exchanger 12 or the outdoor heat exchanger 16 functions as a condenser, and at least the chiller 20 functions as an evaporator. As a result, in the heat pump cycle 10 of the high-power equipment waste heat recovery mode in air conditioning, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. Furthermore, the low-temperature side heat medium's heat (i.e., the waste heat from the high-power equipment 81) is absorbed by the low-pressure refrigerant through the chiller 20.

[0254] Additionally, in the low-temperature side heat medium circuit 50, the low-temperature side heat medium, after being cooled by the chiller 20, is drawn into the second low-temperature side pump 51b. The low-temperature side heat medium pressurized from the second low-temperature side pump 51b flows into the cooling water passage 81a of the power equipment 81, absorbing the waste heat of the power equipment 81.

[0255] Here, the high-voltage electrical equipment waste heat recovery mode is an operating mode aimed at effectively utilizing the waste heat of the high-voltage electrical equipment 81 as a heat source for heating. Therefore, even if the high-voltage electrical equipment waste heat recovery mode is selected based on the second low-temperature side heat medium temperature TWL2, the high-voltage electrical equipment waste heat recovery mode can be stopped if waste heat recovery is not required.

[0256] In cases where waste heat recovery is not required, there are situations where the high-temperature side temperature difference ΔTWH, obtained by subtracting the high-temperature side heat medium temperature TWH from the target high-temperature side heat medium temperature TWHO, is less than or equal to the baseline high-temperature side temperature difference KΔTWH2 used for recovery.

[0257] (C3) Cooling mode for high-power equipment

[0258] In the high-power equipment cooling mode, the control device 60 controls the operation of the second low-temperature side three-way valve 52b to allow the low-temperature side heat medium flowing out from the cooling water passage 81a of the high-power equipment 81 to flow to the low-temperature side radiator 56. Additionally, the control device 60 controls the operation of the second low-temperature side pump 51b to enable it to perform a predetermined pressure delivery capacity.

[0259] Therefore, in the low-temperature side heat medium circuit 50 of the power equipment cooling mode, the low-temperature side heat medium pressurized from the second low-temperature side pump 51b is switched to circulate in sequence through the cooling water passage 81a of the power equipment 81, the low-temperature side radiator 56, and the suction port of the second low-temperature side pump 51b.

[0260] Therefore, in the low-temperature side heat medium circuit 50 of the high-voltage equipment cooling mode, the low-temperature side heat medium, which is cooled by heat exchange between the low-temperature side radiator 56 and the external gas, is drawn into the second low-temperature side pump 51b. The low-temperature side heat medium pressurized from the second low-temperature side pump 51b flows into the cooling water passage 81a of the high-voltage equipment 81. As a result, the high-voltage equipment 81 is cooled.

[0261] As described above, in the air conditioning device 1 of this embodiment, by appropriately combining the operation mode for air conditioning and the operation mode for temperature regulation, comfortable air conditioning inside the vehicle and appropriate temperature regulation of multiple vehicle-mounted devices can be achieved.

[0262] However, in the air conditioning device 1 of this embodiment, when the air conditioning is performed inside the vehicle, the temperature of the supply air is adjusted by heating the supply air with the heating unit. Therefore, in order to achieve fast and responsive air conditioning, it is preferable that the heating unit is in a state where it can exert its full heating capacity when the air conditioning of the vehicle is started.

[0263] In this embodiment, the heating section is formed by the water refrigerant heat exchanger 12 of the heat pump cycle 10 and the constituent devices of the high-temperature side heat medium circuit 40. Therefore, the heating capacity of the heating section can be defined by the temperature of the high-temperature side heat medium flowing into the heater core 42, i.e., the high-temperature side heat medium temperature TWH.

[0264] Therefore, in the heating unit of this embodiment, it is preferable that when the air conditioning in the vehicle compartment is started, the high-temperature side heat medium temperature TWH corresponding to the actual heating capacity of the heating unit is a target high-temperature side heat medium temperature TWHO or higher corresponding to the reference heating capacity of the heating unit.

[0265] Therefore, in this embodiment, execution Figure 3 The control flow shown utilizes the heat generated by the electric heater 54, which serves as the heating element, to perform heating preparation control to enhance the heating capacity of the heating element when the air conditioning in the vehicle compartment is started. Figure 3 The control flow shown is a subroutine of the main program of the air conditioning control program, and it is executed every specified cycle. Figure 3 The control steps shown in the flowchart are the functional implementation parts of the control device 60.

[0266] First, in step S1, it is determined whether the high-temperature side temperature difference ΔTWH obtained by subtracting the high-temperature side temperature TWH from the target high-temperature side heat medium temperature TWHO is greater than or equal to the predetermined reference high-temperature side temperature difference KΔTWH (15°C in this embodiment).

[0267] As described above, the heating capacity of the heating unit in this embodiment can be defined by the high-temperature side heat medium temperature TWH. Therefore, in step S1, if it is determined that the high-temperature side temperature difference ΔTWH is greater than or equal to the reference high-temperature side temperature difference KΔTWH, it is determined that the heating unit has not reached a state where it can exert sufficient heating capacity for air conditioning in the vehicle interior, and the process proceeds to step S2. In steps S2 to S7, heating preparation control is performed.

[0268] On the other hand, in step S1, if it is determined that the temperature difference ΔTWH on the high-temperature side is smaller than the reference temperature difference KΔTWH on the high-temperature side, it is determined that the heating unit is in a state where it can exert sufficient heating capacity, and the process returns to the main program.

[0269] In step S2, in order to perform heating preparation control, the loop structure of the heat pump cycle 10 is switched, the loop structure of the low-temperature side heat medium loop is switched, and the operation control of various constituent equipment is performed.

[0270] Specifically, in the heating preparation control, the control device 60 sets the heating expansion valve 14a to a fully closed state, the cooling expansion valve 14b to a fully closed state, and the cooling expansion valve 14c to a throttling state. Additionally, the control device 60 opens the dehumidification on / off valve 15a and closes the heating on / off valve 15b.

[0271] Therefore, in the heat pump cycle 10 for heating preparation control, such as Figure 4 As shown by the dashed arrow, the refrigerant circuit is switched to circulate in the following order: refrigerant discharged from compressor 11 through water refrigerant heat exchanger 12, dehumidification passage 22a, cooling expansion valve 14c, chiller 20, receiver 21, and compressor 11 suction port.

[0272] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotational speed of the compressor 11 so that the discharge capacity of the compressor 11 is below a predetermined reference discharge capacity for heating preparation control. The reference discharge capacity for heating preparation control is set to a value lower than the discharge capacity performed in the normal air conditioning operating mode. In this embodiment, specifically, the rotational speed of the compressor 11 is set to 0 rpm. That is, in step S2 of this embodiment, the compressor 11 is stopped.

[0273] In addition, the control device 60 controls the throttling opening of the cooling expansion valve 14c to become a predetermined reference opening for heating preparation control.

[0274] In addition, the control device 60 controls the operation of the high-temperature side pump 41 so that it can exert a predetermined pressure delivery capacity.

[0275] Therefore, in the high-temperature side heat medium circuit 40 during heating preparation control, such as Figure 4 As shown by the solid arrow, the high-temperature side heat medium, which is pumped by the high-temperature side pump 41, circulates in the order of heat medium passage 12b of the water refrigerant heat exchanger 12, heater core 42, and suction port of the high-temperature side pump 41.

[0276] Additionally, the control device 60 controls the operation of the second cryogenic side three-way valve 52b to allow the cryogenic side heat medium flowing from the cooling water passage 81a of the high-voltage equipment 81 to flow towards the electric heater 54. Furthermore, the control device 60 controls the operation of the electric heater 54 to enable it to perform a predetermined heating capacity. Additionally, the control device 60 controls the operation of the second cryogenic side pump 51b to enable it to perform a predetermined pressure delivery capacity.

[0277] Therefore, in the low-temperature side heat medium circuit 50 during heating preparation control, such as Figure 4 As shown by the solid arrow, the cryogenic heat medium pumped by the second cryogenic pump 51b circulates in the following order: cooling water passage 81a of the power equipment 81, electric heater 54, heat medium passage 20b of the chiller 20, and suction port of the second cryogenic pump 51b. That is, in the cryogenic heat medium circuit 50 under heating preparation control, the circuit is switched to allow the cryogenic heat medium heated by the electric heater 54 to flow around the cooling water passage 80a of the battery 80.

[0278] Therefore, in the low-temperature side heat medium circuit 50 during heating preparation control, the low-temperature side heat medium pumped from the second low-temperature side pump 51b is heated as it passes through the electric heater 54.

[0279] Furthermore, the control device 60 controls the rotational speed of the indoor fan 32 to ensure that the air delivery capacity of the indoor fan 32 is below a predetermined reference air delivery capacity for heating preparation control. The reference air delivery capacity for heating preparation control is set to a value lower than the air delivery capacity performed in normal air conditioning operation mode. In this embodiment, specifically, the rotational speed of the indoor fan 32 is set to 0 rpm. That is, in step S2, the indoor fan 32 is stopped.

[0280] Next, in step S3, the target heat transfer medium temperature TWinO is determined. Therefore, step S3 is the target heat transfer medium temperature determination unit. The target heat transfer medium temperature TWinO is determined to be a value that, even if the low-pressure refrigerant absorbs heat from the low-temperature side heat transfer medium in the chiller 20, the inlet side heat transfer medium temperature TWin will not decrease compared to the lower limit heat transfer medium temperature TWmin (15°C in this embodiment). The lower limit heat transfer medium temperature TWmin is set as the lowest temperature of the low-pressure side heat transfer medium that can be used as a heat source for air conditioning.

[0281] More specifically, in step S3, the target heat transfer medium temperature TWinO is determined based on the intake air temperature TAin detected by the intake air temperature sensor 69b and the target air delivery capacity determined by the air delivery capacity control unit 60b, and with reference to a control mapping diagram pre-stored in the control device 60. In the control mapping diagram for heating preparation control, the target heat transfer medium temperature TWinO is determined to increase as the intake air temperature TAin decreases. Furthermore, the target heat transfer medium temperature TWinO is determined to increase as the target air delivery capacity increases.

[0282] Next, in step S4, it is determined whether the inlet-side heat medium temperature TWin detected by the third low-temperature side heat medium temperature sensor 67c is above the target heat medium temperature TWinO.

[0283] In step S4, if it is determined that the inlet side heat medium temperature TWin is above the target heat medium temperature TWinO, it is determined that even if the speed of compressor 11 increases, the inlet side heat medium temperature TWin will not be lower than the lower limit heat medium temperature TWmin, and then proceed to step S5.

[0284] On the other hand, in step S4, if it is determined that the inlet side heat medium temperature TWin has not reached the target heat medium temperature TWinO, it is determined that if the speed of compressor 11 increases, the inlet side heat medium temperature TWin may be lower than the lower limit heat medium temperature TWmin, and the process returns to step S2.

[0285] In step S5, the rotational speed of compressor 11 is increased. More specifically, in this embodiment, compressor 11 is operated and controlled in the same way as in heating mode (A4). Therefore, in the heating preparation control of this embodiment, when the inlet-side heat medium temperature Twin reaches or exceeds the target heat medium temperature TwinO, the refrigerant discharge capacity of compressor 11 is increased.

[0286] Therefore, in heat pump cycle 10, the refrigerant, such as Figure 4 The cycle is circulated as indicated by the dashed arrow. Furthermore, in the heat pump cycle 10, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 functions as a condenser and the chiller 20 functions as an evaporator.

[0287] Therefore, in the heat pump cycle 10 during heating preparation control, the heat of the low-temperature side heat medium is absorbed by the low-pressure refrigerant via the chiller 20. Additionally, the high-temperature side heat medium is heated via the water refrigerant heat exchanger 12.

[0288] Next, in step S6, it is determined whether the high-temperature side heat medium temperature TWH is above the target high-temperature side heat medium temperature TWHO.

[0289] In step S6, if it is determined that the high-temperature side heat medium temperature TWH is higher than or equal to the target high-temperature side heat medium temperature TWHO, then the heating capacity of the heating unit is determined to be higher than or equal to the reference heating capacity, and the process proceeds to step S7. On the other hand, if it is determined in step S6 that the high-temperature side heat medium temperature TWH is lower than the target high-temperature side heat medium temperature TWHO, then the heating capacity of the heating unit is determined to be lower than or equal to the reference heating capacity, and the process returns to step S5.

[0290] In step S7, the rotational speed of the indoor fan 32 is increased. More specifically, in this embodiment, the indoor fan 32 is operated and controlled in the same way as in the cooling mode. Therefore, in the heating preparation control of this embodiment, when the inlet-side heat medium temperature TWin reaches or exceeds the target heat medium temperature TWinO and the heating capacity of the heating unit reaches or exceeds the reference heating capacity, the indoor fan 32 is operated to increase the air supply capacity of the indoor fan 32.

[0291] Therefore, in the indoor air conditioning unit 30, part or all of the supply air delivered from the indoor fan 32 is heated as it passes through the heater core 42. As a result, the temperature-conditioned supply air is blown into the vehicle interior, enabling air conditioning within the vehicle interior.

[0292] As described above, in the air conditioning unit 1 of this embodiment, since heating preparation control is performed, the heat generated by the electric heater 54 can rapidly increase the heating capacity of the heating section (in this embodiment, the temperature of the high-temperature side heat medium TWH). As a result, the air conditioning unit 1 can achieve rapid and highly responsive air conditioning.

[0293] More specifically, in the heating preparation control of this embodiment, as described in step S5, the compressor 11 is stopped until the inlet-side heat medium temperature Twin reaches or exceeds the target heat medium temperature TWinO. Then, when the inlet-side heat medium temperature Twin reaches or exceeds the target heat medium temperature TWinO, the compressor 11 is activated to increase the refrigerant discharge capacity of the compressor 11.

[0294] Therefore, it is possible to suppress the unnecessary increase in heat absorption by the low-pressure refrigerant from the low-temperature side heat medium in the chiller 20 until the inlet side heat medium temperature Twin reaches or exceeds the target heat medium temperature TwinO. Thus, the heat generated by the electric heater 54 can rapidly raise the inlet side heat medium temperature Twin, which is the temperature of the low-temperature side heat medium.

[0295] The result, such as Figure 5 and Figure 6As shown, it can shorten the preheating time TW required to raise the high-temperature side heat medium temperature TWH to the target high-temperature side heat medium temperature TWHO.

[0296] Here, Figure 5 This is a graph showing the changes in the high-temperature side heat medium temperature TWH and the inlet side heat medium temperature TWin under comparative conditions where the compressor 11 and the indoor fan 32 operate immediately after the electric heater 54 is energized. Additionally, in Figures 5-7 At the point where time 0 seconds has elapsed, the electric heater 54 is energized.

[0297] in addition, Figure 6 This is a graph showing the changes in the high-temperature side heat medium temperature TWH and the inlet side heat medium temperature TWin under the first condition that the compressor 11 and the indoor fan 32 operate when the inlet side heat medium temperature TWin is above the target heat medium temperature TWinO after the electric heater 54 is energized. Additionally, in Figure 6 In this process, the target heat medium temperature TWinO is determined to be approximately the lower limit heat medium temperature TWmin + 20℃.

[0298] Furthermore, in the heating preparation control of this embodiment, as explained in step S7, the indoor fan 32 is stopped until the inlet-side heat medium temperature Twin reaches or exceeds the target heat medium temperature TwinO and the high-temperature-side heat medium temperature TWH reaches or exceeds the target high-temperature-side heat medium temperature TWHO. Then, when the inlet-side heat medium temperature Twin reaches or exceeds the target heat medium temperature TwinO and the high-temperature-side heat medium temperature TWH reaches or exceeds the target high-temperature-side heat medium temperature TWHO, the indoor fan 32 is activated.

[0299] Therefore, before the inlet-side heat medium temperature TWin reaches or exceeds the target heat medium temperature TWinO and the high-temperature-side heat medium temperature TWH reaches or exceeds the target high-temperature-side heat medium temperature TWHO, the heater core 42 constituting the heating section can suppress an unnecessary increase in heat dissipation from the high-temperature-side heat medium to the supply air. Thus, the heat generated by the electric heater 54 can rapidly raise the inlet-side heat medium temperature TWin.

[0300] The result is, as Figure 7 As shown, the preheating time TW can be further shortened.

[0301] Here, Figure 7This is a graph showing the changes in the high-temperature side heat medium temperature TWH and the inlet side heat medium temperature TWin under the second condition: after the electric heater 54 is energized, the compressor 11 is activated when the inlet side heat medium temperature TWin reaches or exceeds the target heat medium temperature TWinO; subsequently, the indoor fan 32 is activated when the high-temperature side heat medium temperature TWH reaches or exceeds the target high-temperature side heat medium temperature TWHO. Additionally, in Figure 7 In this process, the target heat medium temperature TWinO is determined to be approximately the lower limit heat medium temperature TWmin + 10℃.

[0302] Furthermore, as explained in step S1, the heating preparation control in this embodiment is performed when the high-temperature side temperature difference ΔTWH is above the baseline high-temperature side temperature difference KΔTWH. Therefore, the heating preparation control in this embodiment is performed when the heating capacity of the heating unit is insufficient. As a result, it is possible to suppress the frequent stopping of the indoor air supply fan 32 due to unnecessary heating preparation control, that is, it is possible to suppress the stopping of air conditioning in the vehicle interior.

[0303] Furthermore, in the heating preparation control of this embodiment, as explained in step S2, the second low-temperature side three-way valve 52b, which serves as a heat medium circuit switching unit, switches the circuit structure of the low-temperature side heat medium circuit 50. Specifically, the low-temperature side heat medium circuit 50 is switched to a circuit in which the low-temperature side heat medium heated by the electric heater 54 flows around the cooling water passage 80a of the battery 80.

[0304] Therefore, by suppressing the heat absorption of the low-temperature side heat medium heated by the electric heater 54 by the battery 80 with a relatively large heat capacity, the temperature of the inlet side heat medium TWin can rise rapidly. Furthermore, the preheating time TW can be further shortened.

[0305] Furthermore, in the heating preparation control of this embodiment, as explained in step S2, the refrigeration expansion valve 14b is set to a fully closed state. Moreover, a third check valve 17c, configured to close the refrigerant outlet side, is provided on the refrigerant outlet side of the indoor evaporator 18.

[0306] Therefore, even if the refrigerant pressure in the refrigerant passage 20a increases due to the inflow of the low-temperature side heat medium heated by the electric heater 54 into the heat medium passage 20b of the chiller 20, the backflow of refrigerant from the chiller 20 side into the indoor evaporator 18 can be suppressed. As a result, the phenomenon of so-called refrigerant intrusion, where refrigerant remains in the indoor evaporator 18, can be suppressed.

[0307] Similarly, in the heating preparation control of this embodiment, as explained in step S2, the heating expansion valve 14a is set to a fully closed state, and the heating on / off valve 15b is closed. Furthermore, a first check valve 17a and a second check valve 17b configured to close the refrigerant outlet side are provided on the refrigerant outlet side of the outdoor heat exchanger 16.

[0308] Therefore, even if the refrigerant pressure in the refrigerant passage 20a increases due to the low-temperature side heat medium flowing into the heat medium passage 20b of the chiller 20 after being heated by the electric heater 54, the backflow of refrigerant from the chiller 20 side into the outdoor heat exchanger 16 can be suppressed. As a result, the intrusion of refrigerant into the outdoor heat exchanger 16 can be suppressed.

[0309] Furthermore, in step S3, which is the target heat medium temperature determination unit in this embodiment, the target heat medium temperature TWinO is determined in a manner that increases as the intake air temperature TAin decreases. Additionally, the target heat medium temperature TWinO is determined in a manner that increases as the target air supply capacity increases.

[0310] Therefore, when the indoor air supply fan 32 is operating, as the heat dissipation from the high-temperature side heat medium to the supply air in the heater core 42 increases, the target heat medium temperature TWinO can rise. Therefore, as... Figure 7 As shown, it can suppress the increase of the temperature drop ΔTL of the high-temperature side heat medium TWH immediately after the indoor air blower 32 is activated.

[0311] Furthermore, in the heating preparation control of this embodiment, as explained in step S2, although it is described that the refrigerant circuit of the heat pump cycle 10 is switched to make the refrigerant as Figure 4 Examples of refrigerant loops as shown by the dashed arrows are provided, but this is not a limitation.

[0312] For example, as a variation of the heating preparation control, in step S2, the control device 60 sets the heating expansion valve 14a to a throttling state, the cooling expansion valve 14b to a fully closed state, and the cooling expansion valve 14c to a throttling state. Then, the control device 60 opens the dehumidification on / off valve 15a and the heating on / off valve 15b.

[0313] Therefore, in the modified heat pump cycle 10, such as Figure 8As shown by the dashed arrow, the refrigerant circuit is switched to circulate sequentially from the compressor 11 through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the receiver 21, and the suction inlet of the compressor 11. Simultaneously, the refrigerant circuit is switched to circulate sequentially from the compressor 11 through the water-refrigerant heat exchanger 12, the first refrigerant connector 13a, the dehumidification passage 22a, the cooling expansion valve 14c, the chiller 20, the receiver 21, and the suction inlet of the compressor 11. That is, the refrigerant circuit is switched so that the outdoor heat exchanger 16 and the chiller 20 are connected in parallel with respect to the refrigerant flow.

[0314] Furthermore, the control device 60 appropriately controls the operation of other controlled equipment in the heat pump cycle 10. For example, the control device 60 controls the throttling opening of the heating expansion valve 14a so that the refrigerant evaporation temperature in the outdoor heat exchanger 16 is lower than the outside air temperature Tam. Other operations are the same as the heating preparation control in the first embodiment described above.

[0315] Therefore, in the modified heating preparation control, not only can heat generated by the electric heater 54 through the chiller 20 be absorbed, but also heat absorbed from the outside air by the outdoor heat exchanger 16 can be used to heat the high-temperature side heat medium. As a result, the heating capacity of the heating unit can be increased more rapidly. The modified heating preparation control is effective when the outside temperature Tam is higher than the refrigerant evaporation temperature in the chiller 20.

[0316] In addition, such as Figure 9 As shown in the overall structural diagram, in the case where the outdoor heat exchanger 16 is equipped with a damper device 16a, as another variation of the heating preparation control, in step S2, the control device 60 sets the heating expansion valve 14a to the fully open state, the cooling expansion valve 14b to the fully closed state, and the cooling expansion valve 14c to the throttling state. Furthermore, the control device 60 closes the dehumidification on / off valve 15a and the heating on / off valve 15b. Additionally, the control device 60 sets the damper device 16a to the fully closed state.

[0317] The damper device 16a regulates the flow rate of outside air into the outside air passage of the outdoor heat exchanger 16, continuously adjusting the amount of heat exchange between the refrigerant in the outdoor heat exchanger 16 and the outside air. By setting the damper device 16a to a fully closed state, closing the outside air passage of the outdoor heat exchanger 16, heat exchange between the refrigerant in the outdoor heat exchanger 16 and the outside air can also be stopped. The operation of the damper device 16a is controlled according to the control signal output from the control device 60.

[0318] Therefore, in another variation of the heat pump cycle 10, such as Figure 9As shown by the dashed arrow, the refrigerant circuit is switched to circulate in the following order: refrigerant discharged from compressor 11 through water-refrigerant heat exchanger 12, fully open heating expansion valve 14a, outdoor heat exchanger 16, cooling expansion valve 14c, chiller 20, receiver 21, and compressor 11 suction inlet. Other operations are the same as in the embodiment described above.

[0319] In another variation, since the damper device 16a is set to a fully closed state, no heat exchange between the refrigerant and the exterior occurs in the outdoor heat exchanger 16. Therefore, the heat pump cycle 10 of the heating preparation control in this other variation operates in the same way as in the first embodiment. Thus, according to the heating preparation control of this other variation, the same effect as the heating preparation control of the first embodiment can be obtained.

[0320] (Second Implementation)

[0321] In this embodiment, an example in which the structure of the heating section of the heat pump cycle 10 is modified compared to the air conditioning device 1 of the first embodiment will be described. Specifically, in the heat pump cycle 10 of this embodiment, as... Figure 10 As shown in the overall structural diagram, the water refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 are abolished, and the indoor condenser 121 is used as the heating part.

[0322] The indoor condenser 121 is a heat exchanger used to heat the supply air by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and the supply air. The indoor condenser 121 is disposed in the air conditioning housing 31 of the indoor air conditioning unit 30 in the same manner as the heater core 42.

[0323] In addition, the second refrigerant temperature sensor 64b of this embodiment detects the temperature of the refrigerant flowing out of the indoor condenser 121 as the second refrigerant temperature TR2. The second refrigerant pressure sensor 65b of this embodiment detects the pressure of the refrigerant flowing out of the indoor condenser 121 as the second refrigerant pressure PR2. The structure of the other parts of the air conditioning unit 1 is the same as that of the first embodiment.

[0324] Furthermore, in this embodiment, the target condensing pressure PDO used in parallel heating mode, etc., is determined to be a value close to the target condensing temperature TDO (approximately 50°C in this embodiment).

[0325] In this embodiment, the heating element is formed by an indoor condenser 121. Therefore, the heating capacity of the heating element can be defined by a second refrigerant pressure PR2 corresponding to the refrigerant condensation pressure in the indoor condenser 121 or a second refrigerant temperature TR2 corresponding to the refrigerant condensation temperature in the indoor condenser 121.

[0326] Therefore, in the heating unit of this embodiment, when starting air conditioning in the vehicle interior, it is preferable that the second refrigerant temperature TR2, which corresponds to the actual heating capacity of the heating unit, is at or above the target condensing temperature TDO, which corresponds to the reference heating capacity of the heating unit. Alternatively, it is preferable that the second refrigerant pressure PR2, which corresponds to the actual heating capacity of the heating unit, is at or above the target condensing pressure PDO, which corresponds to the reference heating capacity of the heating unit.

[0327] Therefore, in step S1 of the heating preparation control in this embodiment, it is determined whether the pressure difference ΔPH obtained by subtracting the second refrigerant pressure PR2 from the target condensing pressure PDO is greater than or equal to a predetermined reference pressure difference KΔPH. Here, in the refrigerant of this embodiment, the temperature at the pressure obtained by subtracting the reference pressure difference KΔPH from the target condensing pressure PDO is set to be approximately 15°C lower than the target condensing temperature TDO.

[0328] In step S1, if the pressure difference ΔPH is determined to be greater than or equal to the reference pressure difference KΔPH, it is determined that the heating element is not in a state where it can exert sufficient heating capacity, and the process proceeds to step S2. On the other hand, if the pressure difference ΔPH is determined to be less than the reference pressure difference KΔPH in step S1, it is determined that the heating element is in a state where it can exert sufficient heating capacity, and the process returns to the main program.

[0329] Similarly, in step S6 of the heating preparation control in this embodiment, it is determined whether the second refrigerant pressure PR2 is above the target condensing pressure PDO.

[0330] In step S6, if it is determined that the second refrigerant pressure PR2 is above the target condensing pressure PDO, it is determined that the heating capacity of the heating unit is above the reference heating capacity, and the process proceeds to step S7. On the other hand, if it is determined in step S6 that the second refrigerant pressure PR2 is below the target condensing pressure PDO, it is determined that the heating capacity of the heating unit is not above the reference heating capacity, and the process returns to step S5. The operation of the other parts of the air conditioning unit 1 is the same as in the first embodiment.

[0331] Therefore, the air conditioning unit 1 according to this embodiment can achieve the same effects as the first embodiment. That is, in the air conditioning unit 1 of this embodiment, it is also possible to perform comfortable air conditioning in the vehicle interior and appropriate temperature adjustment for multiple vehicle-mounted devices. Furthermore, the heat generated by the electric heater 54 can rapidly increase the heating capacity of the heating element (target condensing pressure PDO in this embodiment). As a result, it is possible to achieve air conditioning with rapid effect and high responsiveness.

[0332] (Third Implementation)

[0333] In this embodiment, such as Figure 11The overall structural diagram illustrates an example in which an inlet-side connection passage 91 and an outlet-side connection passage 92 are added to the air conditioning device 1 of the first embodiment. The inlet-side connection passage 91 and the outlet-side connection passage 92 form a heat medium flow path that connects the high-temperature side heat medium circuit 40 and the low-temperature side heat medium circuit 50.

[0334] Furthermore, in this embodiment, a high-temperature side three-way valve 43 is provided in the high-temperature side heat medium circuit 40, from the outlet of the heat medium passage 12b of the water refrigerant heat exchanger 12 to the heater core 42. The high-temperature side three-way valve 43 allows the high-temperature side heat medium flowing out of the heat medium passage 12b of the water refrigerant heat exchanger 12 to flow inward, and to flow out to at least one of the heater core 42 side and the inlet side connecting passage 91 side.

[0335] The high-temperature side three-way valve 43 can continuously adjust the flow rate ratio of the high-temperature side heat medium flowing out to the heater core 42 side to the high-temperature side heat medium flowing out to the inlet side connection passage 91 side. Moreover, by adjusting the flow rate ratio, the high-temperature side three-way valve 43 can make all the flow rate of the high-temperature side heat medium flowing into the interior flow out to either the heater core 42 side or the inlet side connection passage 91 side.

[0336] The inlet of the inlet-side connection passage 91 is connected to the outlet of one of the high-temperature side three-way valves 43. In addition, the outlet of the inlet-side connection passage 91 is connected to an inlet of the fifth heat medium connector 53e, which is located in the heat medium flow path from the outlet of the first low-temperature side pump 51a of the low-temperature side heat medium circuit 50 to the inlet of the cooling water passage 80a of the battery 80.

[0337] The inlet of the outlet-side connection passage 92 is connected to an outlet of the sixth heat medium connector 53f in the heat medium flow path from the outlet of the cooling water passage 80a of the battery 80 in the low-temperature side heat medium circuit 50 to the inlet of the first low-temperature side three-way valve 52a. Additionally, the outlet of the outlet-side connection passage 92 is connected to an inlet of the seventh heat medium connector 53g in the heat medium flow path from the outlet of the high-temperature side three-way valve 43 in the high-temperature side heat medium circuit 40 to the heat medium inlet of the heater core 42. The structure of the other parts of the air conditioning unit 1 is the same as in the first embodiment.

[0338] Next, the operation of the air conditioning unit 1 of this embodiment in the above structure will be described. In the air conditioning unit 1 of this embodiment, during normal operation, the control device 60 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out from the heat medium passage 12b of the water refrigerant heat exchanger 12 flows out to the heater core 42 side.

[0339] Therefore, when executing the air conditioning operation mode and the temperature regulation operation mode, the circuit structure of the heat pump cycle 10, the high-temperature side heat medium circuit 40, and the low-temperature side heat medium circuit 50 is the same as in the first embodiment. Therefore, in the air conditioning device 1 of this embodiment, by appropriately combining the air conditioning operation mode and the temperature regulation operation mode, it is also possible to achieve comfortable air conditioning in the vehicle interior and appropriate temperature regulation for multiple vehicle-mounted devices.

[0340] Furthermore, in the air conditioning unit 1 of this embodiment, heating preparation control can be performed in the same manner as in the first embodiment. Therefore, the heating capacity of the heating unit can be rapidly increased by utilizing the heat generated by the electric heater 54. As a result, air conditioning with rapid effect and high responsiveness can be achieved.

[0341] However, the heating preparation control is implemented to rapidly increase the heating capacity of the heating unit when the air conditioning in the vehicle cabin is turned on. Therefore, heating preparation control is mostly performed before the air conditioning is turned on when the outside temperature is low. At such low outside temperatures, the battery may also need to be warmed up.

[0342] In response, the low-temperature side heat medium circuit 50 in the heating preparation control is switched to a circuit in which the low-temperature side heat medium heated by the electric heater 54 flows around the cooling water passage 80a of the battery 80. Therefore, it is impossible to perform the warm-up of the battery 80 that can be performed by allowing the low-temperature side heat medium heated by the electric heater 54 to flow into the cooling water passage 80a of the battery 80.

[0343] Therefore, in this embodiment, during the execution of heating preparation control, when the battery temperature TB is below the predetermined reference warm-up temperature KTBL, the control device 60 controls the operation of the high-temperature side three-way valve 43 to allow the high-temperature side heat medium flowing out from the heat medium passage 12b of the water refrigerant heat exchanger 12 to flow out to the inlet side connection passage 91. The reference warm-up temperature KTBL is set as the temperature at which it is determined that the battery 80 needs to be warmed up.

[0344] Therefore, in the air conditioning device 1 of this embodiment, when the battery 80 needs to be warmed up during the execution of heating preparation control, such as Figure 11 As shown by the solid arrow, the high-temperature side heat medium, pumped by the high-temperature side pump 41, circulates sequentially through the heat medium passage 12b of the water refrigerant heat exchanger 12, the high-temperature side three-way valve 43, the inlet side connection passage 91, the cooling water passage 80a of the battery 80, the outlet side connection passage 92, the heater core 42, and the suction port of the high-temperature side pump 41.

[0345] Therefore, in step S5 of the heating preparation control described in the first embodiment, if the compressor 11 is activated, the high-temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Furthermore, the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 can flow into the cooling water passage 80a of the battery 80 via the high-temperature side three-way valve 43 and the inlet side connection passage 91. Thus, the battery 80 can be warmed up.

[0346] The high-temperature side heat medium flowing out of the cooling water passage 80a of the battery 80 flows into the heater core 42 via the outlet side connection passage 92. During heating preparation control, the indoor air supply fan 32 is stopped until the high-temperature side heat medium temperature TWH reaches or exceeds the target high-temperature side heat medium temperature TWHO. Therefore, the high-temperature side heat medium flowing into the heater core 42 does not exchange heat with the supply air and flows out of the heater core 42, and is drawn into the high-temperature side pump 41.

[0347] The other operations are the same as in the first embodiment. Therefore, according to this embodiment, the air conditioning device 1 can warm up the battery 80 during the execution of heating preparation control.

[0348] (Fourth Implementation)

[0349] In this embodiment, for Figure 12 The air conditioning unit 1a shown in the overall structural diagram will be described below. The air conditioning unit 1a of this embodiment is used as a vehicle air conditioning unit with onboard equipment temperature control function, similar to that of the first embodiment. The air conditioning unit 1a includes a heat pump cycle 10a, an indoor air conditioning unit 30, a high-temperature side heat medium circuit 40a, and a low-temperature side heat medium circuit 50a, etc.

[0350] Here, the structure of the indoor air conditioning unit 30 of the air conditioning device 1a is the same as in the first embodiment. Therefore, in Figure 12 For clarity, the illustration of the indoor air conditioning unit 30 is omitted. Therefore, the indoor evaporator 18 of the heat pump cycle 10a and the heater core 42 of the high-temperature side heat medium circuit 40a are arranged in the air conditioning housing 31 of the indoor air conditioning unit 30 in the same manner as in the first embodiment.

[0351] In the heat pump cycle 10a of this embodiment, compared with the heat pump cycle 10 described in the first embodiment, the first refrigerant connector 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the liquid receiver 21, etc. are eliminated.

[0352] In heat pump cycle 10a, the outlet of refrigerant passage 12a of water refrigerant heat exchanger 12 is connected to the inlet side of liquid collector 23. Liquid collector 23 is a high-pressure side gas-liquid separator that separates the high-pressure refrigerant flowing out of refrigerant passage 12a of water refrigerant heat exchanger 12 from gas to liquid and stores the remaining liquid refrigerant in the cycle. The refrigerant outlet of liquid collector 23 is connected to the inlet side of fifth refrigerant connector 13e.

[0353] The structure of other heat pump cycles 10a is the same as that of the heat pump cycle 10 described in the first embodiment.

[0354] In addition, the high-temperature side heat medium circuit 40a in this embodiment is equipped with a heat medium passage 12b of a water refrigerant heat exchanger 12, a high-temperature side pump 41, a heater core 42, a high-temperature side three-way valve 43, a high-temperature side radiator 44, etc.

[0355] In this embodiment, the high-temperature side three-way valve 43 allows the high-temperature side heat medium flowing out from the heat medium passage 12b of the water refrigerant heat exchanger 12 to flow inward and to flow out to at least one of the heater core 42 side and the high-temperature side radiator 44 side.

[0356] The high-temperature side three-way valve 43 can continuously adjust the flow rate ratio of the high-temperature side heat medium flowing out to the heater core 42 side to the high-temperature side heat medium flowing out to the high-temperature side radiator 44 side. Moreover, by adjusting the flow rate ratio, the high-temperature side three-way valve 43 can make all the flow rate of the high-temperature side heat medium flowing into the interior flow out to either the heater core 42 side or the high-temperature side radiator 44 side.

[0357] The high-temperature side radiator 44 is a high-temperature side external air heat exchange unit that allows external air to exchange heat with the high-temperature side heat medium flowing out from the high-temperature side three-way valve 43.

[0358] The heat medium outlet of the high-temperature side radiator 44 is connected to one inlet side of the eighth heat medium connector 53h. Furthermore, the heat medium outlet of the heater core 42 in this embodiment is connected to the other inlet side of the eighth heat medium connector 53h. The outlet of the eighth heat medium connector 53h is connected to the suction port side of the high-temperature side pump 41.

[0359] The structure of the other high-temperature side heat medium circuit 40a is the same as that of the high-temperature side heat medium circuit 40 described in the first embodiment.

[0360] In addition, the low-temperature side heat medium circuit 50a in this embodiment is equipped with a first low-temperature side pump 51a, a second low-temperature side pump 51b, a first low-temperature side three-way valve 52a to a third low-temperature side three-way valve 52c, a heat medium passage 20b for the chiller 20, a cooling water passage 80a for the battery 80, a cooling water passage 81a for the high-power equipment 81, an electric heater 54, a bypass passage 55b for the high-power equipment, and a low-temperature side radiator 56.

[0361] In the low-temperature side heat medium circuit 50a, the outlet of the first low-temperature side pump 51a is connected to the inlet side of the heat medium passage 20b of the chiller 20. The outlet of the heat medium passage 20b of the chiller 20 is connected to the inlet side of the first low-temperature side three-way valve 52a.

[0362] In this embodiment, the first low-temperature side three-way valve 52a allows the low-temperature side hot medium flowing out from the hot medium passage 20b of the chiller 20 to flow inward, and then flows out to at least one of the electric heater 54 side and the inlet side of the third low-temperature side three-way valve 52c.

[0363] The first low-temperature side three-way valve 52a can continuously adjust the flow rate ratio of the low-temperature side heat medium flowing to the electric heater 54 side to the low-temperature side heat medium flowing to the third low-temperature side three-way valve 52c side. Furthermore, by adjusting the flow rate ratio, the first low-temperature side three-way valve 52a can make all the flow rate of the low-temperature side heat medium flowing into it flow out to either the electric heater 54 side or the third low-temperature side three-way valve 52c side.

[0364] The outlet of the heating flow path of the electric heater 54 is connected to the inlet side of one of the ninth heat medium connectors 53i. The outlet of the ninth heat medium connector 53i is connected to the suction port side of the first cryogenic pump 51a.

[0365] The third low-temperature side three-way valve 52c allows the low-temperature side hot medium flowing out from the first low-temperature side three-way valve 52a to flow inward, and allows it to flow out to at least one of the inlet side of the cooling water passage 80a of the battery 80 and the tenth hot medium connector 53j.

[0366] The third low-temperature side three-way valve 52c can continuously adjust the flow rate ratio of the low-temperature side heat medium flowing out to the cooling water passage 80a side of the battery 80 to the low-temperature side heat medium flowing out to the tenth heat medium connector 53j side. Furthermore, by adjusting the flow rate ratio, the third low-temperature side three-way valve 52c can make all the flow rate of the low-temperature side heat medium flowing into the interior flow out to either the cooling water passage 80a side of the battery 80 or the tenth heat medium connector 53j side.

[0367] The outlet of the cooling water passage 80a of the battery 80 is connected to the inlet side of one of the eleventh heat medium connectors 53k. The outlet of the eleventh heat medium connector 53k is connected to the inlet side of the other of the ninth heat medium connectors 53i.

[0368] Additionally, in the low-temperature side heat medium circuit 50a, the outlet of the second low-temperature side pump 51b is connected to the inlet side of the cooling water passage 81a of the high-voltage electrical equipment 81. The outlet of the cooling water passage 81a of the high-voltage electrical equipment 81 is connected to the inlet side of the second low-temperature side three-way valve 52b.

[0369] The second low-temperature side three-way valve 52b of this embodiment allows the low-temperature side hot medium flowing out from the cooling water passage 81a of the power equipment 81 to flow inward, and to flow out to at least one of the inlet side of the tenth hot medium connector 53j and the bypass passage 55b side of the power equipment.

[0370] The second low-temperature side three-way valve 52b can continuously adjust the flow rate ratio between the flow rate flowing to the tenth hot medium connector 53j and the flow rate of the low-temperature side hot medium flowing to the high-voltage equipment bypass passage 55b. Moreover, by adjusting the flow rate ratio, the second low-temperature side three-way valve 52b can cause all the flow rate of the low-temperature side hot medium flowing into it to flow out to either the tenth hot medium connector 53j or the high-voltage equipment bypass passage 55b.

[0371] The high-voltage equipment bypass passage 55b is a passage that guides the low-temperature side heat medium flowing from the cooling water passage 81a of the high-voltage equipment 81, bypassing the low-temperature side radiator 56, etc., and directing it to the suction port side of the second low-temperature side pump 51b. The outlet of the high-voltage equipment bypass passage 55b is connected to the inlet of one of the twelfth heat medium connector 53m. The outlet of the twelfth heat medium connector 53m is connected to the suction port side of the second low-temperature side pump 51b.

[0372] The outlet of the tenth heat medium connector 53j is connected to the heat medium inlet side of the low-temperature radiator 56. The heat medium outlet of the low-temperature radiator 56 is connected to the inlet side of the thirteenth heat medium connector 53n. One outlet of the thirteenth heat medium connector 53n is connected to the inlet side of the other side of the twelfth heat medium connector 53m. The other outlet of the thirteenth heat medium connector 53n is connected to the inlet side of the other side of the eleventh heat medium connector 53k.

[0373] The structure of the other low-temperature side heat medium circuit 50a is the same as that of the low-temperature side heat medium circuit 50 described in the first embodiment.

[0374] Next, the operation of the air conditioning unit 1a of this embodiment with the above-described structure will be explained. In the air conditioning unit 1a of this embodiment, the operating modes for air conditioning are (A1) cooling mode, (A2) dehumidification and heating mode, and (A3) heating mode. The switching of the air conditioning operating modes is the same as in the first embodiment, and is performed by executing the air conditioning control program stored in the control device 60. Hereinafter, the detailed operation of each air conditioning operating mode will be explained.

[0375] (A1) Cooling Mode

[0376] In cooling mode, the control device 60 sets the cooling expansion valve 14b to a throttling state. The cooling expansion valve 14c is controlled in the same way as in the first embodiment, according to the operating mode for temperature regulation.

[0377] Therefore, in the heat pump cycle 10a of the cooling mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of water refrigerant heat exchanger 12, liquid collector 23, refrigeration expansion valve 14b, indoor evaporator 18, and compressor 11 suction port.

[0378] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the compressor 11 in the same way as in the cooling mode of the first embodiment. Regarding the cooling expansion valve 14c, the throttling opening is controlled in such a way that the superheat SH of the refrigerant on the outlet side of the indoor evaporator 18 is close to a predetermined reference superheat KSH.

[0379] Additionally, the control device 60 controls the operation of the high-temperature side pump 41 to enable it to achieve a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the high-temperature side three-way valve 43 to bring the high-temperature side heat medium temperature TWH close to the target high-temperature side heat medium temperature TWHO.

[0380] Therefore, in the high-temperature side heat medium circuit 40a of the cooling mode, the high-temperature side heat medium pressurized from the high-temperature side pump 41 circulates in the order of water refrigerant heat exchanger 12, heater core 42, and the suction port of the high-temperature side pump 41. Simultaneously, the high-temperature side heat medium pressurized from the high-temperature side pump 41 circulates in the order of water refrigerant heat exchanger 12, high-temperature side radiator 44, and the suction port of the high-temperature side pump 41. That is, the circuit is switched to a parallel connection between the heater core 42 and the high-temperature side radiator 44 relative to the high-temperature side heat medium flow.

[0381] Here, in cooling mode, the amount of heat exchange between the high-temperature side heat medium in heater core 42 and the supply air is minimal. Therefore, in cooling mode, almost all the flow of the high-temperature side heat medium flowing out of the heat medium passage 12b of the water refrigerant heat exchanger 12 flows towards the high-temperature side radiator 44. Other operations are the same as in the cooling mode described in the first embodiment.

[0382] Therefore, in the heat pump cycle 10a in cooling mode, a vapor compression refrigeration cycle is configured, in which the water refrigerant heat exchanger 12 functions as a condenser and the indoor evaporator 18 functions as an evaporator. As a result, in the heat pump cycle 10a in cooling mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. Furthermore, the supply air is cooled by the indoor evaporator 18.

[0383] In addition, in the high-temperature side heat medium circuit 40a of the cooling mode, the heat medium heated by the water refrigerant heat exchanger 12 is supplied to the heater core 42 according to the flow ratio control of the high-temperature side three-way valve 43.

[0384] In addition, in the cooling mode of the indoor air conditioning unit 30, the supply air blown from the indoor fan 32 is cooled in the indoor evaporator 18. The supply air cooled in the indoor evaporator 18 is temperature-regulated by adjusting the opening of the air mixing door 34 to be close to the target blowing temperature TAO. Furthermore, by blowing the temperature-regulated supply air into the vehicle interior, cooling of the vehicle interior is achieved.

[0385] (A2) Dehumidification and heating mode

[0386] In dehumidification and heating mode, the control device 60 sets the refrigeration expansion valve 14b to throttling mode and the cooling expansion valve 14c to throttling mode.

[0387] Therefore, in the heat pump cycle 10a of the dehumidification and heating mode, the refrigerant circuit is switched to circulate sequentially from the compressor 11 through the water-refrigerant heat exchanger 12, the liquid collector 23, the refrigeration expansion valve 14b, the indoor evaporator 18, and the suction inlet of the compressor 11. Simultaneously, the refrigerant circuit is switched to circulate sequentially from the compressor 11 through the water-refrigerant heat exchanger 12, the liquid collector 23, the cooling expansion valve 14c, the chiller 20, and the suction inlet of the compressor 11. That is, the refrigerant circuit is switched so that the indoor evaporator 18 and the chiller 20 are connected in parallel with respect to the refrigerant flow.

[0388] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the compressor 11 is controlled in the same way as in the parallel dehumidification and heating mode of the first embodiment. In addition, the control device 60 controls the throttling opening of the cooling expansion valve 14c so that the refrigerant evaporation temperature in the chiller 20 is lower than the outside air temperature Tam.

[0389] Additionally, the control device 60 controls the operation of the high-temperature side pump 41 to enable it to achieve a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the high-temperature side three-way valve 43 to bring the high-temperature side heat medium temperature TWH close to the target high-temperature side heat medium temperature TWHO.

[0390] Therefore, in the high-temperature side heat medium circuit 40a of the dehumidification and heating mode, the circuit is switched to a circuit in which the high-temperature side heat medium circulates in the same order as in the cooling mode.

[0391] In addition, the control device 60 controls the first cryogenic side pump 51a to enable it to perform a predetermined pressure delivery capacity.

[0392] Additionally, the control device 60 controls the operation of the first low-temperature side three-way valve 52a to allow the low-temperature side hot medium flowing from the hot medium passage 20b of the chiller 20 to flow out to the third low-temperature side three-way valve 52c. Furthermore, the control device 60 controls the operation of the third low-temperature side three-way valve 52c to allow the low-temperature side hot medium flowing from the first low-temperature side three-way valve 52a to flow out to the tenth hot medium connector 53j. Finally, the control device 60 controls the operation of the second low-temperature side three-way valve 52b to allow the low-temperature side hot medium flowing from the third low-temperature side three-way valve 52c to flow out to the low-temperature side radiator 56.

[0393] Therefore, in the low-temperature side heat medium circuit 50a of the dehumidification and heating mode, the low-temperature side heat medium pressurized from the first low-temperature side pump 51a is switched to circulate in the following order: heat medium passage 20b of the chiller 20, first low-temperature side three-way valve 52a, third low-temperature side three-way valve 52c, low-temperature side radiator 56, and suction port of the first low-temperature side pump 51a. Other operations are the same as in the cooling mode.

[0394] Therefore, in the heat pump cycle 10a of the dehumidification and heating mode, a vapor compression refrigeration cycle is formed in which the water refrigerant heat exchanger 12 functions as a condenser and the indoor evaporator 18 and the chiller 20 function as evaporators.

[0395] As a result, in the heat pump cycle 10a of the dehumidification and heating mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. The supply air is cooled by the indoor evaporator 18. Furthermore, the low-pressure refrigerant absorbs heat from the low-temperature side heat medium by the chiller 20, making the temperature of the low-temperature side heat medium lower than the outside air temperature.

[0396] In addition, in the high-temperature side heat medium circuit 40a of the dehumidification and heating mode, the heat medium heated by the water refrigerant heat exchanger 12 is supplied to the heater core 42 according to the flow ratio control of the high-temperature side three-way valve 43.

[0397] Additionally, in the low-temperature side heat medium circuit 50a of the dehumidification and heating mode, the low-temperature side heat medium cooled by the chiller 20 flows into the low-temperature side radiator 56 via the first low-temperature side three-way valve 52a and the third low-temperature side three-way valve 52c. The low-temperature side heat medium flowing into the low-temperature side radiator 56 absorbs heat from the outside air. After the temperature rises due to heat absorption from the outside air in the low-temperature side radiator 56, the low-temperature side heat medium is drawn into the first low-temperature side pump 51a and pressurized into the heat medium passage 20b of the chiller 20.

[0398] In addition, in the dehumidification and heating mode of the indoor air conditioning unit 30, the supply air blown from the indoor fan 32 is cooled and dehumidified in the indoor evaporator 18. After being cooled and dehumidified in the indoor evaporator 18, the supply air is temperature-regulated to be close to the target blowing temperature TAO by adjusting the opening of the air mixing door 34. Then, by blowing the temperature-regulated supply air into the vehicle interior, dehumidification and heating of the vehicle interior are achieved.

[0399] (A3) Heating Mode

[0400] In heating mode, the control device 60 sets the refrigeration expansion valve 14b to a fully closed state and the cooling expansion valve 14c to a throttling state.

[0401] Therefore, in the heat pump cycle 10a of the heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of water refrigerant heat exchanger 12, liquid collector 23, cooling expansion valve 14c, chiller 20, and the suction port of compressor 11.

[0402] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the compressor 11 in the same way as the heating mode of the first embodiment. In addition, the control device 60 controls the throttling opening of the cooling expansion valve 14c so that the superheat SH of the refrigerant on the outlet side of the chiller 20 is close to a predetermined reference superheat KSH.

[0403] Additionally, the control device 60 controls the operation of the high-temperature side pump 41 to enable it to achieve a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the high-temperature side three-way valve 43 to bring the high-temperature side heat medium temperature TWH close to the target high-temperature side heat medium temperature TWHO.

[0404] Therefore, in the high-temperature side heat medium circuit 40a of the heating mode, the circuit is switched to a circuit in which the high-temperature side heat medium circulates in the same order as in the cooling mode.

[0405] Here, in heating mode, the heat exchange between the high-temperature side heat medium in heater core 42 and the supply air increases. Therefore, in heating mode, almost all the flow of the high-temperature side heat medium flowing out from the heat medium passage 12b of the water refrigerant heat exchanger 12 flows to the heater core 42 side through the high-temperature side three-way valve 43.

[0406] In addition, the control device 60 controls the operation of the first low-temperature side pump 51a to enable it to perform a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the first low-temperature side three-way valve 52a to the third low-temperature side three-way valve 52c in the same manner as in the dehumidification and heating mode.

[0407] Therefore, in the low-temperature side heat medium circuit 50a of the heating mode, the circuit is switched to circulate the low-temperature side heat medium in the same sequence as in the dehumidification heating mode. Other operations are the same as in the heating mode described in the first embodiment.

[0408] Therefore, in the heat pump cycle 10a in heating mode, a vapor compression refrigeration cycle is configured, in which the water refrigerant heat exchanger 12 functions as a condenser and the chiller 20 functions as an evaporator. As a result, in the heat pump cycle 10a in heating mode, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. Furthermore, the chiller 20 causes the low-pressure refrigerant to absorb heat from the low-temperature side heat medium, making the temperature of the low-temperature side heat medium lower than the outside air temperature.

[0409] In addition, in the high-temperature side heat medium circuit 40a of the heating mode, the heat medium heated by the water refrigerant heat exchanger 12 is supplied to the heater core 42 according to the flow ratio control of the high-temperature side three-way valve 43.

[0410] Additionally, in the low-temperature side heat medium circuit 50a of the heating mode, the low-temperature side heat medium cooled by the chiller 20 flows into the low-temperature side radiator 56 via the first low-temperature side three-way valve 52a and the third low-temperature side three-way valve 52c. The low-temperature side heat medium flowing into the low-temperature side radiator 56 absorbs heat from the outside air. The low-temperature side heat medium flowing out of the low-temperature side radiator 56 is drawn into the first low-temperature side pump 51a and pressurized into the heat medium passage 20b of the chiller 20.

[0411] In addition, in the heating mode of the indoor air conditioning unit 30, the supply air blown from the indoor fan 32 passes through the indoor evaporator 18. The supply air after passing through the indoor evaporator 18 is temperature-regulated by adjusting the opening of the air mixing door 34 to be close to the target blowing temperature TAO. Then, heating of the vehicle interior is achieved by blowing the temperature-regulated supply air into the vehicle interior.

[0412] Next, the operating modes for temperature regulation will be explained. In this embodiment, the operating modes for the battery are (B1) battery temperature equalization mode and (B2) battery cooling mode. Additionally, the operating mode for high-voltage equipment is (C1) high-voltage equipment cooling mode. The detailed operation of each operating mode for temperature regulation will be explained below.

[0413] (B1) Battery temperature equalization mode

[0414] The battery temperature equalization mode is executed when the temperature difference ΔTB between individual battery cells is greater than or equal to the temperature difference ΔKTB between the target cells.

[0415] In battery temperature equalization mode, control device 60 controls the operation of the first low-temperature side pump 51a to enable it to perform a predetermined pressure delivery capacity. It also controls the operation of the first low-temperature side three-way valve 52a to allow the low-temperature side hot medium flowing from the heat medium passage 20b of the chiller 20 to flow out to the third low-temperature side three-way valve 52c. Furthermore, control device 60 controls the operation of the third low-temperature side three-way valve 52c to allow the low-temperature side hot medium flowing from the first low-temperature side three-way valve 52a to flow out to the cooling water passage 80a of the battery 80.

[0416] Therefore, in the low-temperature side heat medium circuit 50a of the battery temperature equalization mode, the low-temperature side heat medium pressurized from the first low-temperature side pump 51a is switched to circulate in sequence through the heat medium passage 20b of the chiller 20, the first low-temperature side three-way valve 52a, the third low-temperature side three-way valve 52c, the cooling water passage 80a of the battery 80, and the suction port of the first low-temperature side pump 51a.

[0417] Therefore, in the low-temperature side heat medium circuit 50a of the battery temperature equalization mode, the low-temperature side heat medium pumped from the first low-temperature side pump 51a flows through the cooling water passage 80a of the battery 80 to equalize the temperature of each battery cell forming the battery 80.

[0418] (B2) Battery Cooling Mode

[0419] The battery cooling mode is executed when the battery temperature TB is above a predetermined reference cooling temperature KTBH. The battery cooling mode is an operating mode in which the battery 80 is cooled by a low-temperature heat transfer medium cooled by the motor 20. Therefore, even in cooling mode, when the compressor 11 of the heat pump cycle 10a is operating as in an air conditioner, the control device 60 sets the cooling expansion valve 14c of the heat pump cycle 10a to a throttling state.

[0420] Therefore, in the heat pump cycle 10a of the battery cooling mode, the low-pressure refrigerant, after being depressurized by the cooling expansion valve 14c, flows into the refrigerant passage 20a of the chiller 20. The refrigerant flowing out of the refrigerant passage 20a of the chiller 20 is drawn into the compressor 11 via the sixth refrigerant connector 13f.

[0421] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the cooling expansion valve 14c in the same way as in the dehumidification and heating mode.

[0422] Additionally, the control device 60 controls the operation of the first cryogenic side pump 51a to achieve a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the first cryogenic side three-way valve 52a to allow the cryogenic side hot medium flowing from the hot medium passage 20b of the chiller 20 to flow towards the third cryogenic side three-way valve 52c. Finally, the control device 60 controls the operation of the third cryogenic side three-way valve 52c to bring the temperature TWL1 of the first cryogenic side hot medium close to the target temperature TWLO1 for the battery.

[0423] Therefore, in the low-temperature side heat medium circuit 50a of the battery cooling mode, the circuit is switched to a sequence in which the low-temperature side heat medium pressurized by the first low-temperature side pump 51a circulates through the heat medium passage 20b of the chiller 20, the first low-temperature side three-way valve 52a, the third low-temperature side three-way valve 52c, the cooling water passage 80a of the battery 80, and the suction port of the first low-temperature side pump 51a. Simultaneously, the circuit is switched to a sequence in which the low-temperature side heat medium pressurized by the first low-temperature side pump 51a circulates through the heat medium passage 20b of the chiller 20, the first low-temperature side three-way valve 52a, the third low-temperature side three-way valve 52c, the low-temperature side radiator 56, and the suction port of the first low-temperature side pump 51a. That is, the circuit is switched to a parallel connection between the cooling water passage 80a of the battery 80 and the low-temperature side radiator 56 relative to the low-temperature side heat medium flow.

[0424] Therefore, in the heat pump cycle 10a of the battery cooling mode in air conditioning, a vapor compression refrigeration cycle is configured in which the water refrigerant heat exchanger 12 functions as a condenser and at least the chiller 20 functions as an evaporator.

[0425] Furthermore, in the low-temperature side heat medium circuit 50a, the low-temperature side heat medium, after being cooled by the chiller 20, flows into both the cooling water passage 80a of the battery 80 and the low-temperature side radiator 56 according to the flow ratio control of the first low-temperature side three-way valve 52a. The low-temperature side heat medium flowing into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. Thus, the battery 80 is cooled.

[0426] Next, the battery cooling mode in non-air conditioning will be explained. In the battery cooling mode in non-air conditioning, the control device 60 sets the cooling expansion valve 14b to a fully closed state and the cooling expansion valve 14c to a throttling state.

[0427] Therefore, in the heat pump cycle 10a of the battery cooling mode in non-air conditioning, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates in the order of water refrigerant heat exchanger 12, liquid collector 23, cooling expansion valve 14c, chiller 20, and the suction port of compressor 11.

[0428] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotational speed of the compressor 11 to enable it to achieve a predetermined discharge capacity. In addition, the control device 60 controls the throttling opening of the cooling expansion valve 14c to bring the temperature of the first low-temperature side heat medium TWL1 close to the target temperature TWLO1 for the battery.

[0429] Additionally, the control device 60 controls the operation of the high-temperature side pump 41 to enable it to perform a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the high-temperature side three-way valve 43 to allow the high-temperature side heat medium flowing in from the heat medium passage 12b of the water refrigerant heat exchanger 12 to flow out towards the high-temperature side radiator 44.

[0430] Therefore, in the high-temperature side heat medium circuit 40a of the battery cooling mode in non-air conditioning, the circuit is switched to a sequential circulation of the high-temperature side heat medium pressurized by the high-temperature side pump 41 through the heat medium passage 12b of the water refrigerant heat exchanger 12, the high-temperature side three-way valve 43, the high-temperature side radiator 44, and the suction port of the high-temperature side pump 41.

[0431] Additionally, the control device 60 controls the operation of the first cryogenic side pump 51a to enable it to perform a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the first cryogenic side three-way valve 52a and the third cryogenic side three-way valve 52c in the same way as the battery cooling mode in the air conditioning system.

[0432] Therefore, in the low-temperature side heat medium circuit 50a of the battery cooling mode in non-air conditioning, the low-temperature side refrigerant pumped from the first low-temperature side pump 51a is switched to circulate in the same way as in the battery cooling mode of air conditioning.

[0433] Therefore, in the battery-cooled heat pump cycle 10a in non-air-conditioned conditions, a vapor compression refrigeration cycle is configured, in which the water refrigerant heat exchanger 12 functions as a condenser and the chiller 20 functions as an evaporator. As a result, in the battery-cooled heat pump cycle 10a in non-air-conditioned conditions, the high-temperature side heat medium is heated by the water refrigerant heat exchanger 12. Furthermore, the low-pressure side heat medium is cooled by the chiller 20.

[0434] Additionally, in the high-temperature side heat medium circuit 40a, the high-temperature side heat medium, heated by the water refrigerant heat exchanger 12, is pressurized to the high-temperature side radiator 44 via the high-temperature side three-way valve 43. The high-temperature side heat medium flowing into the high-temperature side radiator 44 is cooled by dissipating heat to the outside air.

[0435] Furthermore, in the low-temperature side heat transfer medium circuit 50a, similar to the battery cooling mode in air conditioning, the low-temperature side heat transfer medium cooled by the chiller 20 flows into the cooling water passage 80a of the battery 80. The low-temperature side heat transfer medium flowing into the cooling water passage 80a of the battery 80 absorbs heat from the battery 80. As a result, the battery 80 is cooled.

[0436] (C1) Cooling mode for high-power equipment

[0437] The high-power equipment cooling mode is executed when the temperature of the second low-temperature side heat medium TWL2 is above the predetermined reference high-power equipment cooling temperature KTWL2. The high-power equipment cooling mode is an operating mode in which the high-power equipment 81 is cooled by the low-temperature side heat medium cooled by the low-temperature side radiator 56.

[0438] In the high-power equipment cooling mode, the control device 60 controls the operation of the second cryogenic side pump 51b to enable it to achieve a predetermined pressure delivery capacity. Additionally, the control device 60 controls the operation of the second cryogenic side three-way valve 52b to bring the temperature of the second cryogenic side heat medium TWL2 close to the target temperature TWLO2 for the high-power equipment.

[0439] Therefore, in the low-temperature side heat medium circuit 50a of the high-voltage equipment cooling mode, the circuit is switched to a sequence in which the low-temperature side heat medium pressurized by the second low-temperature side pump 51b circulates through the cooling water passage 81a of the high-voltage equipment 81, the second low-temperature side three-way valve 52b, the high-voltage equipment bypass passage 55b, and the suction port of the second low-temperature side pump 51b. Simultaneously, the circuit is switched to a sequence in which the low-temperature side heat medium pressurized by the second low-temperature side pump 51b circulates through the cooling water passage 81a of the high-voltage equipment 81, the second low-temperature side three-way valve 52b, the low-temperature side radiator 56, and the suction port of the second low-temperature side pump 51b. That is, the circuit is switched to a parallel connection between the high-voltage equipment bypass passage 55b and the low-temperature side radiator 56 relative to the low-temperature side heat medium flow.

[0440] Therefore, in the low-temperature side heat medium circuit 50a of the high-voltage equipment cooling mode, at least a portion of the low-temperature side heat medium pressurized from the second low-temperature side pump 51b flows into the low-temperature side radiator 56. The low-temperature side heat medium flowing into the low-temperature side radiator 56 is cooled by heat exchange with the outside air. The low-temperature side heat medium flowing out of the low-temperature side radiator 56 merges and mixes with the low-temperature side heat medium flowing through the high-voltage equipment bypass passage 55b at the twelfth heat medium joint 53m.

[0441] At this time, through the flow ratio control of the second low-temperature side three-way valve 52b, the temperature of the low-temperature side heat medium mixed at the twelfth heat medium joint 53m is close to the target temperature TWLO2 for the high-voltage electrical equipment. The low-temperature side heat medium mixed at the twelfth heat medium joint 53m is drawn into the second low-temperature side pump 51b. The low-temperature side heat medium pressurized from the second low-temperature side pump 51b flows into the cooling water passage 81a of the high-voltage electrical equipment 81. As a result, the high-voltage electrical equipment 81 is cooled.

[0442] As described above, the air conditioning device 1a according to this embodiment can perform comfortable air conditioning inside the vehicle and appropriate temperature adjustment for multiple vehicle-mounted devices by appropriately combining the operation mode for air conditioning and the operation mode for temperature adjustment.

[0443] Furthermore, the air conditioning unit 1a in this embodiment, like the first embodiment, is capable of performing heating preparation control.

[0444] Specifically, in step S2 of the heating preparation control in this embodiment, in order to perform heating preparation control, the control device 60 sets the refrigeration expansion valve 14b to a fully closed state and the cooling expansion valve 14c to a throttling state.

[0445] Therefore, in the heat pump cycle 10a for heating preparation control, such as Figure 12 As shown by the dashed arrow, the refrigerant circuit is switched to circulate in the order of refrigerant discharged from compressor 11 through water refrigerant heat exchanger 12, liquid collector 23, cooling expansion valve 14c, chiller 20, and compressor 11 suction port.

[0446] Additionally, the control device 60 controls the operation of the high-temperature side pump 41 to enable it to perform a predetermined pressure delivery capacity. Furthermore, the control device 60 controls the operation of the high-temperature side three-way valve 43 to allow the high-temperature side heat medium flowing from the heat medium passage 12b of the water refrigerant heat exchanger 12 to flow towards the heater core 42.

[0447] Therefore, in the high-temperature side heat medium circuit 40a during heating preparation control, such as Figure 12 As shown by the solid arrow, the high-temperature side heat medium, which is pumped by the high-temperature side pump 41, circulates in the order of heat medium passage 12b of the water refrigerant heat exchanger 12, heater core 42, and suction port of the high-temperature side pump 41.

[0448] Additionally, the control device 60 controls the operation of the first cryogenic side pump 51a to enable it to perform a predetermined pressure delivery capacity. The control device 60 also controls the operation of the first cryogenic side three-way valve 52a to allow the cryogenic side heat medium flowing from the heat medium passage 20b of the chiller 20 to flow into the cooling water passage 80a of the battery 80.

[0449] Therefore, in the low-temperature side heat medium circuit 50a for heating preparation control, such as Figure 12 As shown by the solid arrow, the low-temperature side heat medium pumped by the first low-temperature side pump 51a circulates in the order of heat medium passage 20b of the chiller 20, electric heater 54, and suction port of the first low-temperature side pump 51a. That is, in the low-temperature side heat medium circuit 50a under heating preparation control, the circuit is switched to allow the low-temperature side heat medium heated by the electric heater 54 to flow around the cooling water passage 80a of the battery 80.

[0450] The other heating preparation control operations are the same as in the first embodiment. Therefore, the same effect as in the first embodiment can be obtained in the heating preparation control of the air conditioning unit 1a in this embodiment. That is, the heating capacity of the heating unit can be rapidly increased by using the heat generated by the electric heater 54. As a result, air conditioning with rapid effect and high responsiveness can be achieved.

[0451] (Fifth Implementation)

[0452] In this embodiment, such as Figure 13 As shown in the overall structural diagram, an example in which an inlet-side connection passage 91a and an outlet-side connection passage 92a are added to the air conditioning device 1a according to the fourth embodiment will be described. The inlet-side connection passage 91a and the outlet-side connection passage 92a form a heat medium flow path that connects the high-temperature side heat medium circuit 40a and the low-temperature side heat medium circuit 50a.

[0453] Furthermore, in the high-temperature side heat medium circuit 40a of this embodiment, a high-temperature side four-way valve 43a is provided instead of a high-temperature side three-way valve 43. The high-temperature side four-way valve 43a allows the high-temperature side heat medium flowing out from the heat medium passage 12b of the water refrigerant heat exchanger 12 to flow into the interior, and to flow out to at least one of the heater core 42 side, the high-temperature side radiator 44 side, and the inlet side connection passage 91a side.

[0454] The high-temperature side four-way valve 43a can regulate the flow rate ratio of the high-temperature side heat medium flowing to the heater core 42 side, the high-temperature side heat medium flowing to the high-temperature side radiator 44 side, and the high-temperature side heat medium flowing to the inlet side connection passage 91a side. Furthermore, the high-temperature side four-way valve 43a can adjust the flow rate ratio to allow all the flow of the high-temperature side heat medium flowing into the interior to flow out to any one of the heater core 42 side, the high-temperature side radiator 44 side, and the inlet side connection passage 91a side.

[0455] That is, the high-temperature side four-way valve 43a is a switching part of the hot medium circuit. The operation of the high-temperature side four-way valve 43a is controlled by the control signal output from the control device 60.

[0456] Furthermore, in the high-temperature side heat medium circuit 40a, a first four-way connector 53q is provided instead of the eighth heat medium connector 53h. The first four-way connector 53q is a four-way connector with four inflow outlets that are interconnected. As the first four-way connector 53q, a connector component formed in the same manner as the first refrigerant connector 13a can be used.

[0457] Furthermore, in this embodiment, the low-temperature side heat medium circuit 50a is provided with a fourteenth heat medium connector 53p. The fourteenth heat medium connector 53p is disposed in the heat medium flow path from the outlet of the third low-temperature side three-way valve 52c to the inlet of the cooling water passage 80a of the battery 80.

[0458] Furthermore, in the low-temperature side heat medium circuit 50a, a second four-way connector 53r is provided instead of the eleventh heat medium connector 53k. The basic structure of the second four-way connector 53r is the same as that of the first four-way connector 53q.

[0459] The inlet of the inlet-side connecting passage 91a is connected to one outlet of the high-temperature four-way valve 43a. Additionally, the outlet of the inlet-side connecting passage 91a is connected to one inlet of the fourteenth heat medium connector 53p. The inlet of the outlet-side connecting passage 92a is connected to one outlet of the second four-way connector 53r. The outlet of the outlet-side connecting passage 92a is connected to one inlet of the first four-way connector 53q. The structure of the other parts of the air conditioning unit 1a is the same as in the fourth embodiment.

[0460] Next, the operation of the air conditioning unit 1a of this embodiment with the above-described structure will be explained. In the air conditioning unit 1a of this embodiment, during normal operation, the control device 60 controls the operation of the high-temperature side four-way valve 43a to make the high-temperature side heat medium circuit 40a the same circuit as in the fourth embodiment. Therefore, during normal operation, the high-temperature side heat medium will not flow out from the high-temperature side four-way valve 43a to the inlet side connection passage 91a.

[0461] Therefore, in the air conditioning unit 1a of this embodiment, comfortable air conditioning of the vehicle interior and appropriate temperature adjustment of multiple vehicle-mounted devices can be achieved by appropriately combining the air conditioning operation mode and the temperature adjustment operation mode. Furthermore, similar to the fourth embodiment, the heating capacity of the heating unit can be rapidly increased by performing heating preparation control. As a result, rapid and highly responsive air conditioning can be achieved.

[0462] In addition, in this embodiment, when the heating preparation control is executed and the battery temperature TB is below the predetermined reference warm-up temperature KTBL, the control device 60 controls the operation of the high-temperature side four-way valve 43a so that the high-temperature side heat medium flowing out from the heat medium passage 12b of the water refrigerant heat exchanger 12 flows out to both the heater core 42 side and the inlet side connection passage 91a side.

[0463] Therefore, in the air conditioning device 1a of this embodiment, when the battery 80 needs to be warmed up during the execution of heating preparation control, such as Figure 13 As shown by the solid arrow, the circuit is switched to a sequential circulation of the high-temperature side heat medium pressurized by the high-temperature side pump 41 through the heat medium passage 12b of the water-refrigerant heat exchanger 12, the high-temperature side four-way valve 43a, the heater core 42, and the suction port of the high-temperature side pump 41. Simultaneously, the circuit is switched to a sequential circulation of the high-temperature side heat medium pressurized by the high-temperature side pump 41 through the heat medium passage 12b of the water-refrigerant heat exchanger 12, the high-temperature side four-way valve 43a, the inlet-side connection passage 91a, the cooling water passage 80a of the battery 80, the outlet-side connection passage 92a, and the suction port of the high-temperature side pump 41. That is, the circuit is switched so that the heater core 42 and the cooling water passage 80a of the battery 80 are connected in parallel with respect to the high-temperature side heat medium flow.

[0464] Therefore, in step S5 of the heating preparation control described in the first embodiment, when the compressor 11 is operated, the high-temperature side heat medium can be heated by the water refrigerant heat exchanger 12. Furthermore, at least a portion of the high-temperature side heat medium heated by the water refrigerant heat exchanger 12 can flow into the cooling water passage 80a of the battery 80 via the high-temperature side four-way valve 43a and the inlet-side connection passage 91a. Thus, the battery 80 can be warmed up.

[0465] The high-temperature side heat medium flowing out from the cooling water passage 80a of the battery 80 is drawn into the high-temperature side pump 41 via the outlet side connection passage 92a.

[0466] The other operations are the same as in the first embodiment. Therefore, the air conditioning device 1a according to this embodiment can warm up the battery 80 during the execution of heating preparation control.

[0467] The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the spirit of the present invention as follows.

[0468] In the above embodiments, examples of applying the air conditioning devices 1 and 1a according to the present invention to electric vehicles have been described, but the application of the air conditioning device 1 is not limited thereto. For example, it can also be applied to hybrid vehicles that obtain driving force from an electric motor and an internal combustion engine (i.e., an engine), and further, it can be applied to plug-in hybrid vehicles that can charge the battery with electricity supplied from an external power source when the vehicle is parked.

[0469] In addition, it can also be applied to stationary air conditioning units with temperature control functions that simultaneously regulate the indoor air and the temperature of the object being regulated (such as computers, computer server devices, and other electrical equipment).

[0470] Furthermore, while the above embodiments illustrate examples of using an inverter and a generator as power supply equipment 81, the power supply equipment 81 is not limited to these. For example, the power supply equipment 81 may also include a charging device, a power control unit (PCU), a drive shaft, a control device for ADAS, etc.

[0471] The charging device is an on-board charger for recharging the battery to 80% capacity and generating regenerative power. The power control unit is a power control device that performs power conversion and distribution. The driveshaft is a power transmission mechanism that integrates the gearbox, differential gears, etc. The control device used in ADAS (Advanced Driver Assistance Systems) is a control device used in advanced driver assistance systems. When applied to stationary air conditioning systems, it can also cool other heat-generating equipment.

[0472] The structures of heat pump cycles 10 and 10a are not limited to the structures disclosed in the above embodiments.

[0473] For example, in the above embodiment, although an example of using a third check valve 17c with a small refrigerant passage cross-sectional area as the indoor unit outlet side opening and closing part is described, the evaporator pressure regulating valve can also be combined with a regular check valve to form the indoor unit outlet side opening and closing part.

[0474] The evaporating pressure regulating valve is a variable throttling mechanism that varies the valve opening to suppress frosting on the indoor evaporator 18 and maintain the refrigerant evaporation pressure in the indoor evaporator 18 above a predetermined set pressure. As an evaporating pressure regulating valve, a mechanical mechanism that increases the valve opening as the refrigerant flow rate inside increases can be employed.

[0475] Furthermore, although the example of using a water refrigerant heat exchanger 12 and a liquid collector 23 was described in the second embodiment, it is not limited to this. For example, a so-called sub-cooling type heat exchanger may also be used, which has a condenser section for condensing the refrigerant, a liquid receiving section for separating the refrigerant gas and liquid after condensation in the condenser section and accumulating the liquid phase refrigerant, and a subcooling section for subcooling the liquid phase refrigerant flowing out from the liquid receiving section.

[0476] Alternatively, within the range where the aforementioned effects can be achieved, multiple constituent devices can be integrated or separated. For example, the fourth refrigerant connector 13d and the sixth refrigerant connector 13f can be integrated in the same way as the first four-way connector 53q.

[0477] Furthermore, while the above embodiments illustrate the use of R1234yf as a refrigerant, the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc., may also be used. Alternatively, a mixed refrigerant, combining multiple refrigerants from these sources, may also be used. Moreover, carbon dioxide may be used as a refrigerant to construct a supercritical refrigeration cycle where the high-pressure side refrigerant pressure is above the refrigerant's critical pressure.

[0478] The structures of the high-temperature side heat medium circuits 40 and 40a and the low-temperature side heat medium circuits 50 and 50a are not limited to the structures disclosed in the above embodiments.

[0479] For example, in the above embodiment, although a PTC heater was described as the example of the electric heater 54 used as the wound heating unit, it is not limited to this. For example, nickel-chromium alloy wire, carbon fiber heaters, etc., may also be used. Furthermore, a high-power electrical device may be used as the wound heating unit. For example, an ADAS control device may be used as the wound heating unit, and the heat generation can be adjusted by performing inefficient operation.

[0480] Furthermore, within the scope of achieving the aforementioned effects, multiple constituent devices can be integrated or separated. For example, the first low-temperature side three-way valve 52a, the second low-temperature side three-way valve 52b, and the first hot medium connector 53a of the first to third embodiments can be integrated into a five-way valve having five hot medium inflow and outflow outlets. Alternatively, two three-way connectors can be combined to form a first four-way connector 53q and a second four-way connector 53r.

[0481] Furthermore, while the above embodiments illustrate the use of aqueous ethylene glycol as both the high-temperature and low-temperature heat transfer mediums, the embodiments are not limited to this. Other heat transfer mediums that can be used include solutions containing dimethyl polysiloxane or nanofluids, antifreeze, aqueous liquid refrigerants containing alcohols, and liquid media containing oils.

[0482] The operation of air conditioning units 1 and 1a is not limited to the aforementioned operating modes. Air conditioning units 1 and 1a can also be configured to perform other operating modes. As long as air conditioning units 1 and 1a have at least an operating mode that heats the supply air in the heating section, the heating capacity of the heating section based on the aforementioned heating preparation control can be rapidly increased.

[0483] Furthermore, although the example of stopping the compressor 11 in step S2 of the heating preparation control described above has been given, it is not limited to this. For example, the reference discharge capacity for heating preparation control may be a lower limit of the range that the compressor 11 speed (refrigerant discharge capacity) can reach during normal operation, or a value lower than the lower limit.

[0484] Furthermore, although the example of stopping the indoor fan 32 in step S2 of the heating preparation control described above has been given, it is not limited to this. For example, the reference air supply capacity for heating preparation control may be a lower limit of the range that the indoor fan 32 speed (air supply capacity) can reach during normal operation, or a value lower than the lower limit.

[0485] Although the invention has been described with reference to embodiments, it should be understood that the invention is not limited to those embodiments or structures. The invention also includes various modifications and variations within the same scope. Furthermore, various combinations, methods, and even other combinations and methods comprising only one element, or more than one element, also fall within the scope and spirit of the invention.

Claims

1. An air conditioning device, characterized in that, have: A heat pump cycle having a compressor, a heating unit and a low-temperature side water refrigerant heat exchanger, wherein the compressor compresses and discharges refrigerant, the heating unit uses the high-pressure refrigerant discharged from the compressor as a heat source to heat the supply air blown into the air-conditioned space, and the low-temperature side water refrigerant heat exchanger allows the low-pressure refrigerant to absorb heat from the heat medium; A heat medium circuit, which supplies the circulation of the heat medium; as well as A blower blows the supplied air toward the space to be conditioned. The heat medium circuit is equipped with a heat medium passage for the low-temperature side water refrigerant heat exchanger and a heat-generating section for heating the heat medium flowing into the heat medium passage. When using the heat generated by the heat-generating section to improve the heating capacity of the heating section, the following heating preparation control is performed: the refrigerant discharge capacity of the compressor is lower than a predetermined reference discharge capacity and the air supply capacity of the blower is lower than a predetermined reference air supply capacity, until the temperature of the heat medium at the inlet side of the heat medium flowing into the heat medium passage becomes higher than the target heat medium temperature.

2. The air conditioning device according to claim 1, characterized in that, In the heating preparation control, when the temperature of the inlet-side heat medium is above the target heat medium temperature, the refrigerant discharge capacity of the compressor is increased.

3. The air conditioning device according to claim 2, characterized in that, In the heating preparation control, when the temperature of the inlet-side heat medium is above the target heat medium temperature and the heating capacity of the air supply in the heating unit is above a predetermined reference heating capacity, the air supply capacity of the blower is increased.

4. The air conditioning device according to any one of claims 1 to 3, characterized in that, When the value obtained by subtracting the actual heating capacity of the heating unit from its reference heating capacity is above a predetermined reference value, the heating preparation control is executed.

5. The air conditioning device according to any one of claims 1 to 3, characterized in that, The heat pump cycle includes an indoor evaporator, an indoor unit inlet-side opening and closing section, and an indoor unit outlet-side opening and closing section. The indoor evaporator facilitates heat exchange between the low-pressure refrigerant and the supply air. The indoor unit inlet-side opening and closing section controls the refrigerant inlet side of the indoor evaporator, and the indoor unit outlet-side opening and closing section controls the refrigerant outlet side of the indoor evaporator. The indoor evaporator and the low-temperature side water refrigerant heat exchanger are connected in parallel with respect to the flow of the refrigerant. The inlet-side opening and closing portion and the outlet-side opening and closing portion of the indoor unit are configured to close the refrigerant inlet side and the refrigerant outlet side of the indoor evaporator when the heating preparation control is executed.

6. The air conditioning device according to any one of claims 1 to 3, characterized in that, The heat transfer circuit switching section is equipped with a cooling water passage and a switching circuit structure for the battery. When performing the heating preparation control, the heat medium circuit switching unit switches to a circuit in which the heat medium flows around the cooling water passage.

7. The air conditioning device according to any one of claims 1 to 3, characterized in that, It includes a target heat medium temperature determining unit, which determines the target heat medium temperature. The target heat medium temperature determination unit determines the target heat medium temperature in such a way that the target heat medium temperature rises as the temperature of the supply air flowing into the heating unit decreases.

8. The air conditioning device according to any one of claims 1 to 3, characterized in that, have: A target heat medium temperature determining unit determines the target heat medium temperature; and The target air delivery capacity determining unit determines the target air delivery capacity of the blower. The target heat medium temperature determination unit determines the target heat medium temperature in a manner that the target heat medium temperature increases as the target air supply capacity increases.

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