Air conditioning device

Abstract

To provide an air conditioner which can enhance heating ability of a heating part speedily by using heat generated by a heat creation part.SOLUTION: An air conditioner comprises: a heat pump cycle 10 which includes a compressor 11, and a water refrigerant heat exchanger 12 and a chiller 20 composing a heating part; a low temperature side thermal medium circuit 50 in which an electric heater 54 being a heat creation part and a thermal medium passage 20b of the chiller 20 are disposed; and an indoor blower 32 which sends blowing wind toward an air conditioning object space. It executes heating preparation control which sets refrigerant discharge capacity of the compressor 11 to be reference ejection or less and sets blowing capacity of the indoor blower 32 to be reference blowing capacity or less by using heat generated by the electric heater 54 until inlet side thermal medium temperature TWin of heat medium flowing into the thermal medium passage 20b reaches target thermal medium temperature TWinO or more when enhancing heating capacity of the heating part.SELECTED DRAWING: Figure 4

Description

[Technical field]

[0001] The present invention relates to an air conditioner having a heat generating section that generates heat. [Background technology]

[0002] 2. Description of the Related Art Patent Document 1 discloses a conventional air conditioner for a vehicle that includes a heat pump cycle and a low-temperature side heat medium circuit.

[0003] The heat pump cycle of Patent Document 1 has a heating section and a low-temperature side water-refrigerant heat exchanger. The heating section uses the high-pressure refrigerant discharged from the compressor as a heat source to heat the air to be blown into the vehicle cabin. The low-temperature side water-refrigerant heat exchanger exchanges heat between the low-pressure refrigerant and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit, and causes the low-pressure refrigerant to absorb heat from the low-temperature side heat medium.

[0004] Furthermore, a heat medium passage of a low-temperature side water-refrigerant heat exchanger and an electric heater are arranged in the low-temperature side heat medium circuit of Patent Document 1. The electric heater is a heat generating unit that generates heat for heating the low-temperature side heat medium.

[0005] In the air conditioner of Patent Document 1, heat generated by an electric heater is transferred from the low pressure side to the high pressure side by a heat pump cycle, and can be used to improve the heating capacity of a heating section. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] International Publication No. 2013 / 013790 Summary of the Invention [Problem to be solved by the invention]

[0007] However, in the air conditioning device of Patent Document 1, in order to improve the heating capacity of the heating section by utilizing the heat generated by the electric heater, the temperature of the low-temperature side heat medium, which has a relatively large heat capacity, must be raised higher than the temperature of the low-pressure refrigerant.

[0008] For this reason, when the temperature of the low-temperature side heat medium is low, for example, when the outside air temperature is low, it takes a long time to raise the temperature of the low-temperature side heat medium, making it impossible to quickly improve the heating capacity of the heating unit. As a result, the warm-up time required to raise the temperature of the blown air to a temperature that can adequately heat the vehicle cabin becomes long, making it impossible to realize air conditioning that is fast-acting and highly responsive.

[0009] In view of the above, an object of the present invention is to provide an air conditioner that can quickly increase the heating capacity of a heating unit by using heat generated by a heat generating unit. [Means for solving the problem]

[0010] In order to achieve the above object, an air conditioner according to a first aspect of the present invention includes a heat pump cycle (10, 10a), a heat medium circuit (50, 50a), and a blower (32).

[0011] The heat pump cycle includes a compressor (11), a heating section (12, 40, 121), and a low-temperature side water-refrigerant heat exchanger (20). The compressor compresses and discharges a refrigerant. The heating section uses the high-pressure refrigerant discharged from the compressor as a heat source to heat the air to be blown into the space to be air-conditioned. The low-temperature side water-refrigerant heat exchanger causes the low-pressure refrigerant to absorb heat contained in the heat medium.

[0012] The heat medium circuit circulates the heat medium. The blower blows air toward the space to be air-conditioned.

[0013] The heat medium circuit is provided with a heat medium passage (20b) of the low-temperature side water-refrigerant heat exchanger, and a heat generator (54) which heats the heat medium flowing into the heat medium passage.

[0014] Furthermore, when the heating capacity (TWH, PR2) of the heating unit is increased by using the heat generated by the heat generating unit, a heating preparation control is executed. In the heating preparation control, the refrigerant discharge capacity of the compressor is kept below a predetermined reference discharge capacity and the blowing capacity of the blower is kept below a predetermined reference blowing capacity until the inlet side heat medium temperature (TWin) of the heat medium flowing into the heat medium passage becomes equal to or higher than the target heat medium temperature (TWinO).

[0015] According to this, in the heating preparation control, the refrigerant discharge capacity of the compressor (11) is kept equal to or lower than the reference discharge capacity until the temperature (TWin) of the heat medium flowing into the heat medium passage (20b) of the low-temperature side water-refrigerant heat exchanger (20) becomes equal to or higher than the target heat medium temperature (TWinO). Therefore, it is possible to suppress an unnecessary increase in the amount of heat absorbed from the heat medium to the low-pressure refrigerant in the low-temperature side water-refrigerant heat exchanger (20).

[0016] In the heating preparation control, the blowing capacity of the blower (32) is set to equal to or lower than the reference blowing capacity until the temperature (TWin) of the heat medium flowing into the heat medium passage (20b) of the low-temperature side water-refrigerant heat exchanger (20) becomes equal to or higher than the target heat medium temperature (TWinO). Thus, an unnecessary increase in the amount of heat dissipated to the blown air in the heating section (12, 40, 121) can be suppressed.

[0017] As a result, by executing the heating preparation control, the temperature (TWin) of the heat medium can be quickly increased by using the heat generated by the heat generator (54). Then, the heat of the heat medium whose temperature has been quickly increased is absorbed by the low-pressure refrigerant in the heat pump cycle (10, 10a) and transferred to the high-pressure refrigerant, thereby quickly increasing the heating capacity of the heating section (12, 40, 121).

[0018] That is, according to the first aspect of the present invention, it is possible to provide an air conditioner that can rapidly increase the heating capacity of the heating section (12, 40, 121) by using the heat generated by the heat generating section (54).

[0019] The reference symbols in parentheses for each means described in this section and in the claims are examples showing the correspondence with the specific means described in the embodiments described later. [Brief description of the drawings]

[0020] [Figure 1] 1 is a schematic overall configuration diagram of an air conditioner according to a first embodiment. [Diagram 2] 2 is a block diagram showing an electrical control unit of the air conditioner of the first embodiment. FIG. [Diagram 3] 4 is a flowchart showing a control flow during heating preparation control of the air conditioner of the first embodiment. [Figure 4] 1 is a schematic overall configuration diagram showing the flow of refrigerant and the like during heating preparation control of an air conditioner according to a first embodiment. FIG. [Diagram 5] 4 is a graph showing changes in the inlet heat medium temperature and the target heat medium temperature under comparative conditions in the air conditioner of the first embodiment. [Figure 6] 4 is a graph showing changes in the inlet heat medium temperature and the target heat medium temperature under a first condition of the air conditioner of the first embodiment. [Figure 7] 6 is a graph showing changes in the inlet heat medium temperature and the target heat medium temperature under a second condition of the air conditioner of the first embodiment. [Figure 8] FIG. 4 is a schematic overall configuration diagram showing the flow of refrigerant and the like in a modified example of heating preparation control of the air conditioner of the first embodiment. [Figure 9] FIG. 4 is a schematic overall configuration diagram showing the flow of refrigerant, etc., in another modified example of the heating preparation control of the air conditioner of the first embodiment. [Figure 10] FIG. 11 is a schematic overall configuration diagram of an air conditioner according to a second embodiment. [Figure 11] FIG. 11 is a schematic overall configuration diagram showing the flow of refrigerant and the like during heating preparation control of an air conditioner of a third embodiment. [Figure 12] FIG. 11 is a schematic overall configuration diagram showing the flow of refrigerant and the like during heating preparation control of an air conditioner of a fourth embodiment. [Figure 13]FIG. 13 is a schematic overall configuration diagram showing the flow of refrigerant and the like during heating preparation control of an air conditioner of a fifth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0021] Hereinafter, a number of embodiments for carrying out the present invention will be described with reference to the drawings. In each embodiment, the same reference numerals may be used to designate parts corresponding to matters described in the preceding embodiment, and duplicated descriptions may be omitted. In each embodiment, when only a part of the configuration is described, other embodiments described previously may be applied to the other parts of the configuration. In addition to combinations of parts that are specifically indicated as being possible in each embodiment, it is also possible to partially combine embodiments even if not indicated, as long as there is no particular problem with the combination.

[0022] (First embodiment) A first embodiment of an air conditioner 1 according to the present invention will be described with reference to Figs. 1 to 9. The air conditioner 1 of this embodiment is applied to an electric vehicle. An electric vehicle is a vehicle that obtains driving force for traveling from an electric motor. The air conditioner 1 performs air conditioning of the vehicle cabin, which is the space to be air-conditioned, and temperature adjustment of the on-board equipment, which is the object to be temperature-adjusted, in the electric vehicle. Therefore, the air conditioner 1 of this embodiment is a vehicle air conditioner with a function of adjusting the temperature of on-board equipment.

[0023] In the air conditioner 1 of this embodiment, the in-vehicle equipment to be temperature-adjusted is a battery 80 and a high-power equipment 81.

[0024] The battery 80 is a secondary battery that stores power to be supplied to electric in-vehicle devices. In this embodiment, a lithium-ion battery is used as the battery 80. The battery 80 is an assembled battery formed by electrically connecting a plurality of stacked battery cells in series or in parallel.

[0025] The battery 80 generates heat during operation (i.e., during charging and discharging). The battery 80 has a characteristic that its output is likely to decrease at low temperatures and its deterioration is likely to progress at high temperatures. For this reason, the temperature of the battery 80 needs to be maintained within an appropriate temperature range (in this embodiment, 15° C. or higher and 55° C. or lower).

[0026] The high-power device 81 is an in-vehicle device that operates when supplied with electric power and generates heat during operation. Specifically, the high-power device 81 in this embodiment is an inverter and a motor generator.

[0027] The inverter is a power conversion device that converts the frequency of the power supplied from the battery 80 to the motor generator, and also converts the AC power generated by the motor generator into DC power and outputs it to the battery 80. When supplied with power, the motor generator serves as an electric motor that outputs driving force for traveling, and serves as a power generation device that generates regenerative power when the vehicle is decelerating or traveling downhill.

[0028] If the high-power equipment 81 becomes hot, the electrical circuits may deteriorate. Therefore, it is necessary to keep the temperature lower than the standard heat-resistant temperature (130° C. in this embodiment) at which the electrical circuits can be protected.

[0029] Therefore, in this embodiment, the appropriate temperature range for properly operating the battery 80 does not completely match the appropriate temperature range for properly operating the high power device 81. In other words, the appropriate temperature range for the battery 80 and the appropriate temperature range for the high power device 81 are different.

[0030] As shown in the overall configuration diagram of FIG. 1, the air conditioner 1 includes a heat pump cycle 10, an indoor air conditioning unit 30, a high-temperature side heat medium circuit 40, a low-temperature side heat medium circuit 50, and the like.

[0031] First, a description will be given of the heat pump cycle 10. The heat pump cycle 10 is a vapor compression type refrigeration cycle device that adjusts the temperatures of the blown air blown into the vehicle cabin, the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40, and the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50 in order to air-condition the vehicle cabin and regulate the temperature of on-board devices.

[0032] The heat pump cycle 10 is configured to be able to switch the refrigerant circuit according to various operation modes, which will be described later, in order to condition the air inside the vehicle cabin and adjust the temperature of on-board devices.

[0033] The heat pump cycle 10 employs an HFO refrigerant (specifically, R1234yf) as a refrigerant. The heat pump cycle 10 constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. The refrigerant is mixed with refrigerant oil for lubricating the compressor 11. The refrigerant oil is a PAG oil that is compatible with liquid-phase refrigerant. A portion of the refrigerant oil circulates through the cycle together with the refrigerant.

[0034] The compressor 11 draws in, compresses, and discharges refrigerant in the heat pump cycle 10. The compressor 11 is disposed in a drive unit compartment at the front side of the vehicle interior. The drive unit compartment forms a space in which at least some of the devices (e.g., a motor generator) used to generate driving force for running the vehicle are disposed.

[0035] The compressor 11 is an electric compressor that uses an electric motor to drive a fixed displacement compression mechanism with a fixed discharge capacity. The rotation speed (i.e., refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 60 for system control, which will be described later.

[0036] The discharge port of the compressor 11 is connected to an inlet side of a refrigerant passage 12a of the water-refrigerant heat exchanger 12. The water-refrigerant heat exchanger 12 has a refrigerant passage 12a through which the high-pressure refrigerant discharged from the compressor 11 flows, and a heat medium passage 12b through which the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40 flows.

[0037] The water-refrigerant heat exchanger 12 is a high-temperature side water-refrigerant heat exchanger 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 of the high-pressure refrigerant is dissipated to the heat medium to heat the high-temperature side heat medium.

[0038] The inlet side of a first refrigerant joint 13a is connected to the outlet of the refrigerant passage 12a of the water-refrigerant heat exchanger 12. The first refrigerant joint 13a is a three-way joint having three inlet and outlet ports that communicate with each other. As the first refrigerant joint 13a, a joint member formed by joining multiple pipes or a joint member formed by providing multiple refrigerant passages in a metal block or a resin block can be used.

[0039] Furthermore, as described below, the heat pump cycle 10 has a second refrigerant joint portion 13b to a sixth refrigerant joint portion 13f. The second refrigerant joint portion 13b to the sixth refrigerant joint portion 13f have the same basic configuration as the first refrigerant joint portion 13a.

[0040] These joints function as a branching section that branches the refrigerant flow when one of the three inlet / outlet ports is used as an inlet and the remaining two are used as outlet ports, and as a merging section that merges the refrigerant flows when two of the three inlet / outlet ports are used as inlet ports and the remaining one is used as an outlet port.

[0041] An inlet side of a heating expansion valve 14a is connected to one outlet side of the first refrigerant joint portion 13a. An inlet side of a second refrigerant joint portion 13b is connected to the other outlet side of the first refrigerant joint portion 13a via a dehumidification passage 22a.

[0042] The dehumidification passage 22a forms a refrigerant flow path through which the refrigerant flows during a parallel dehumidification heating mode, which will be described later. A dehumidification on-off valve 15a is disposed in the dehumidification passage 22a. The dehumidification on-off valve 15a is an electromagnetic valve that opens and closes the dehumidification passage 22a. The operation of the dehumidification on-off valve 15a is controlled by a control voltage output from the control device 60.

[0043] Furthermore, the heat pump cycle 10 has a heating on-off valve 15b, as described below. The basic configuration of the heating on-off valve 15b is similar to 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 units that switch the refrigerant circuit.

[0044] The heating expansion valve 14a is a heating pressure reduction section that reduces the pressure of the high-pressure refrigerant flowing out from the refrigerant passage 12a of the water-refrigerant heat exchanger 12 during a heating mode described later, and adjusts the flow rate (mass flow rate) of the refrigerant flowing out downstream.

[0045] The heating expansion valve 14a is an electric variable throttle mechanism having a valve body portion 141a that changes the opening degree of the throttle passage (i.e., the valve opening degree) and an electric actuator (specifically, a stepping motor) that displaces the valve body portion 141a. The operation of the heating expansion valve 14a is controlled by a control signal (specifically, a control pulse) output from the control device 60.

[0046] The heating expansion valve 14a has a full opening function where the valve body 141a fully opens the valve and functions simply as a refrigerant passage without performing a flow rate adjustment function or a refrigerant pressure reduction function. Also, the heating expansion valve 14a has a full closing function where the valve body 141a fully closes the throttle passage and blocks the refrigerant passage.

[0047] Furthermore, the heat pump cycle 10 includes a cooling expansion valve 14b and a cooling expansion valve 14c, as described below. The cooling expansion valve 14b and the cooling expansion valve 14c have the same basic configuration as the heating expansion valve 14a. Therefore, the cooling expansion valve 14b has a valve body portion 141b and has a fully open function and a fully closed function. The cooling expansion valve 14c has a valve body portion 141c and has a fully open function and a fully closed function.

[0048] The heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c can switch the refrigerant circuit of the heat pump cycle 10 by the above-mentioned fully closing function. More specifically, the valve body portion 141a of the heating expansion valve 14a, the valve body portion 141b of the cooling expansion valve 14b, and the valve body portion 141c of the cooling expansion valve 14c also function as a refrigerant circuit switching unit.

[0049] Of course, the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c may be formed by combining a variable throttle mechanism that does not have a full closing function with an on-off valve. In this case, the on-off valve serves as the refrigerant circuit switching unit.

[0050] The outlet of the heating expansion valve 14a is connected to the refrigerant inlet side of the outdoor heat exchanger 16. Therefore, the valve body portion 141a of the heating expansion valve 14a becomes an outdoor heat exchanger inlet side opening and closing portion that opens and closes the refrigerant inlet side of the outdoor heat exchanger 16. The outdoor heat exchanger 16 is an outdoor heat exchange portion that exchanges heat between the refrigerant flowing out from the heating expansion valve 14a and the outside air blown by a cooling fan (not shown). The outdoor heat exchanger 16 is disposed on the front side of the drive unit room. Therefore, the traveling wind can be applied to the outdoor heat exchanger 16 when the vehicle is traveling.

[0051] An inlet side of a third refrigerant joint 13c is connected to a refrigerant outlet of the exterior heat exchanger 16. One of the outlets of the third refrigerant joint 13c is connected to one of the inlet sides of a fourth refrigerant joint 13d via a heating passage 22b. The heating passage 22b forms a refrigerant flow path through which the refrigerant flows during a heating mode, which will be described later.

[0052] The heating passage 22b is provided with a heating on-off valve 15b and a first check valve 17a. The heating on-off valve 15b is a solenoid valve that opens and closes the heating passage 22b. The first check valve 17a allows the refrigerant to flow from the third refrigerant joint 13c to the fourth refrigerant joint 13d, and prohibits the refrigerant from flowing from the fourth refrigerant joint 13d to the third refrigerant joint 13c. Therefore, the heating on-off valve 15b and the first check valve 17a serve as outdoor unit outlet side opening and closing parts that open and close the refrigerant outlet side of the outdoor heat exchanger 16.

[0053] The other outlet of the third refrigerant joint 13c is connected to the other inlet of the second refrigerant joint 13b. A second check valve 17b is disposed in the refrigerant passage connecting the other outlet of the third refrigerant joint 13c and the other inlet of the second refrigerant joint 13b. The second check valve 17b allows the refrigerant to flow from the third refrigerant joint 13c to the second refrigerant joint 13b, and prohibits the refrigerant from flowing from the second refrigerant joint 13b to the third refrigerant joint 13c. Therefore, the second check valve 17b serves as an outdoor unit outlet side opening and closing part.

[0054] The outlet of the second refrigerant joint 13b is connected to the inlet side of the fifth refrigerant joint 13e. One outlet of the fifth refrigerant joint 13e is connected to the inlet side of the cooling expansion valve 14b. The other outlet of the fifth refrigerant joint 13e is connected to the inlet side of the cooling expansion valve 14c.

[0055] The cooling expansion valve 14b is a cooling pressure reducing section that reduces the pressure of the refrigerant and adjusts the flow rate of the refrigerant flowing downstream during a cooling mode, which will be described later. The outlet of the cooling expansion valve 14b is connected to the refrigerant inlet side of the indoor evaporator 18. Therefore, the valve body 141b of the cooling expansion valve 14b serves as an indoor unit inlet side opening / closing section that opens and closes the refrigerant inlet side of the indoor evaporator 18.

[0056] The interior evaporator 18 is disposed in an air conditioning case 31 of the interior air conditioning unit 30, which will be described later. The interior evaporator 18 is a cooling heat exchanger that exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 14b and the ventilation air to be blown into the vehicle cabin. The interior evaporator 18 cools the ventilation air by evaporating the low-pressure refrigerant and exerting a heat absorption effect.

[0057] One inlet side of the sixth refrigerant joint portion 13f is connected to the refrigerant outlet of the indoor evaporator 18. A third check valve 17c is arranged in the refrigerant flow path connecting the refrigerant outlet of the indoor evaporator 18 and one inlet of the sixth refrigerant joint portion 13f. The third check valve 17c allows the refrigerant to flow from the indoor evaporator 18 side to the sixth refrigerant joint portion 13f side, and prohibits the refrigerant to flow from the sixth refrigerant joint portion 13f side to the indoor evaporator 18 side. Therefore, the third check valve 17c serves as an indoor unit outlet side opening / closing portion that opens and closes the refrigerant outlet side of the indoor evaporator 18.

[0058] The cooling expansion valve 14c is a cooling pressure reducing part that reduces the pressure of the refrigerant and adjusts the flow rate of the refrigerant flowing downstream during a battery cooling mode, which will be described later. The outlet of the cooling expansion valve 14c is connected to the inlet side of the refrigerant passage 20a of the chiller 20.

[0059] The chiller 20 has a refrigerant passage 20a through which the low-pressure refrigerant decompressed by the cooling expansion valve 14c flows, and a heat medium passage 20b through which the low-temperature side 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 exchanges heat 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. The chiller 20 cools the low-temperature side heat medium by evaporating the low-pressure refrigerant to exert a heat absorption effect.

[0060] The other inlet side of the sixth refrigerant joint 13f is connected to the outlet of the refrigerant passage 20a of the chiller 20. Therefore, the indoor evaporator 18 and the chiller 20 are connected in parallel with respect to the flow of refrigerant from the fifth refrigerant joint 13e to the sixth refrigerant joint 13f. The other inlet side of the fourth refrigerant joint 13d is connected to the outlet of the sixth refrigerant joint 13f.

[0061] The outlet of the fourth refrigerant joint 13d is connected to the inlet of the accumulator 21. The accumulator 21 is a low-pressure gas-liquid separator that separates the refrigerant that flows into it into gas and liquid and stores the excess liquid-phase refrigerant in the cycle. The suction port of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 21.

[0062] Next, the high-temperature side heat medium circuit 40 will be described. The high-temperature side heat medium circuit 40 is a circuit that circulates the high-temperature side heat medium. The high-temperature side heat medium circuit 40 uses an ethylene glycol aqueous solution as the high-temperature side heat medium. The high-temperature side heat medium circuit 40 includes the heat medium passage 12b of the water-refrigerant heat exchanger 12, a high-temperature side pump 41, a heater core 42, and the like.

[0063] The high-temperature side pump 41 is a high-temperature side heat medium pumping section that sucks in and pumps the high-temperature side heat medium. The high-temperature side pump 41 pumps 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 rotation speed (i.e., pumping capacity) is controlled by a control voltage output from the control device 60.

[0064] The heat medium inlet side of the heater core 42 is connected to the outlet of the heat medium passage 12b of the water-refrigerant heat exchanger 12. The heater core 42 is disposed in the air conditioning case 31 of the indoor air conditioning unit 30. The heater core 42 is a heating heat exchanger that exchanges heat between the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12 and the blown air. The heater core 42 releases heat from the high-temperature side heat medium to the blown air, thereby heating the blown air. The suction port side of the high-temperature side pump 41 is connected to the heat medium outlet of the heater core 42.

[0065] Therefore, in this embodiment, the water-refrigerant heat exchanger 12 and the various components of the high-temperature side heat medium circuit 40 form a heating section that heats the blown air using the high-pressure refrigerant discharged from the compressor 11 as a heat source.

[0066] Next, the low-temperature side heat medium circuit 50 will be described. The low-temperature side heat medium circuit 50 is a circuit that circulates the low-temperature side heat medium. The low-temperature side heat medium is a heat medium that is heated by a heat generating unit, which will be described later. In the low-temperature side heat medium circuit 50, the same type of fluid 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 be able to switch the heat medium circuit according to various operation modes, which will be described later.

[0067] The low-temperature side heat medium circuit 50 includes 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 of a chiller 20, a cooling water passage 80a of a battery 80, a cooling water passage 81a of a high-power equipment 81, an electric heater 54, a battery bypass passage 55a, a low-temperature side radiator 56, and the like.

[0068] The first low-temperature side pump 51a and the second low-temperature side pump 51b are low-temperature side heat medium pumps that suck in and pump out the low-temperature side heat medium. The basic configuration of the first low-temperature side pump 51a and the second low-temperature side pump 51b is similar to that of the high-temperature side pump 41. The first low-temperature side pump 51a pumps out the low-temperature side heat medium to the inlet side of the cooling water passage 80a of the battery 80.

[0069] The cooling water passage 80a of the battery 80 is a battery-side heat exchanger that exchanges heat between the multiple battery cells and the low-temperature side heat medium. The cooling water passage 80a of the battery 80 is formed in a battery case that houses the multiple battery cells and forms the outer shell of the battery 80.

[0070] The inlet side of the first low-temperature side three-way valve 52a is connected to the outlet of the cooling water passage 80a of the battery 80. The first low-temperature side three-way valve 52a is a three-way flow rate adjustment valve. The first low-temperature side three-way valve 52a allows the low-temperature side heat medium flowing out of the cooling water passage 80a of the battery 80 to flow into the inside thereof and to flow out to at least one of the inlet side of the first heat medium joint portion 53a and the battery bypass passage 55a.

[0071] The first low-temperature side three-way valve 52a can continuously adjust the flow rate ratio between the flow rate of the low-temperature side heat medium flowing out to the first heat medium joint portion 53a side and the flow rate of the low-temperature side heat medium flowing out to the battery bypass passage 55a side. Furthermore, the first low-temperature side three-way valve 52a can adjust the flow rate ratio to cause the total flow rate of the low-temperature side heat medium flowing into it to flow out to either the first heat medium joint portion 53a side or the battery bypass passage 55a side.

[0072] That is, the first low-temperature side three-way valve 52a serves as a heat medium circuit switching unit that switches the circuit configuration of the heat medium circuit. The operation of the first low-temperature side three-way valve 52a is controlled by a control signal output from the controller 60.

[0073] Furthermore, a second low-temperature side three-way valve 52b is disposed in the low-temperature side heat medium circuit 50. The second low-temperature side three-way valve 52b and the three-way valves for the heat medium circuit employed in the embodiments described below have the same basic configuration as the first low-temperature side three-way valve 52a. Therefore, the second low-temperature side three-way valve 52b and the like also function as a heat medium circuit switching unit.

[0074] The first heat medium joint 53a is a three-way joint for the heat medium. Furthermore, the low-temperature side heat medium circuit 50 of this embodiment has a second heat medium joint 53b to a fourth heat medium joint 53d, as described later. The first heat medium joint 53a to the fourth heat medium joint 53d and the heat medium joints employed in the embodiments described later have basic configurations similar to those of the first refrigerant joint 13a of the heat pump cycle 10.

[0075] The outlet of the first heat medium joint portion 53a is connected to the inlet side of the electric heater 54. Therefore, the first low-temperature side three-way valve 52a essentially causes the low-temperature side heat medium that has flowed into it to flow out to at least one of the electric heater 54 side and the battery bypass passage 55a side.

[0076] The battery bypass passage 55a forms a heat medium flow path that guides the low-temperature side heat medium flowing out from the coolant passage 80a of the battery 80 to the suction port side of the first low-temperature side pump 51a, bypassing the electric heater 54 and the heat medium passage 20b of the chiller 20. One of the inlets of the second heat medium joint 53b is connected to the outlet of the battery bypass passage 55a. The suction port side of the first low-temperature side pump 51a is connected to the outlet of the second heat medium joint 53b.

[0077] The second low-temperature side pump 51b pumps the low-temperature side heat medium to the inlet side of the cooling water passage 81a of the high-power system device 81. The cooling water passage 81a of the high-power system device 81 is a high-power system device side heat exchanger that exchanges heat between the high-power system device 81 and the low-temperature side heat medium. The cooling water passage 81a of the high-power system device 81 is formed in a housing portion or a case portion that forms the outer shell of the high-power system device 81.

[0078] The inlet side of the second low-temperature side three-way valve 52b is connected to the outlet of the cooling water passage 81a of the high-power device 81. 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 device 81 to flow into the second low-temperature side three-way valve 52b, and causes the low-temperature side heat medium to flow out to at least one of the other inlet side of the first heat medium joint part 53a and the low-temperature side radiator 56 side.

[0079] Therefore, second low-temperature side three-way valve 52b essentially causes the low-temperature side heat medium that has flowed into it to flow out to at least one of the electric heater 54 side and the low-temperature side radiator 56 side.

[0080] Second low-temperature side three-way valve 52b can continuously adjust the flow rate ratio between the flow rate of the low-temperature side heat medium flowing out to the electric heater 54 side and the flow rate of the low-temperature side heat medium flowing out to the low-temperature side radiator 56 side. Furthermore, second low-temperature side three-way valve 52b can cause the total flow rate of the low-temperature side heat medium flowing therein to flow out to either the electric heater 54 side or the battery bypass passage 55a side by adjusting the flow rate ratio.

[0081] The low-temperature side radiator 56 is an outdoor air heat exchanger on the low-temperature side that exchanges heat between the outdoor air and 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 disposed on the front side of the drive unit room together with the outdoor heat exchanger 16 of the heat pump cycle 10.

[0082] One inlet side of a third heat medium joint part 53c is connected to the heat medium outlet of the low-temperature side radiator 56. The suction port side of the second low-temperature side pump 51b is connected to the outlet of the third heat medium joint part 53c.

[0083] The electric heater 54 is a heat generating unit that generates heat for heating the low-temperature heat medium. In this embodiment, a PTC heater having a PTC element (i.e., a positive temperature coefficient thermistor) that generates heat when supplied with power and heats the low-temperature heat medium flowing through the heating flow path is used as the electric heater 54. The outlet of the heating heat medium flow path of the electric heater 54 is connected to the inlet side of the heat medium passage 20b of the chiller 20.

[0084] The inlet side of the fourth heat medium joint 53d is connected to the outlet of the heat medium passage 20b of the chiller 20. The other inlet side of the second heat medium joint 53b is connected to one outlet of the fourth heat medium joint 53d. The other inlet side of the third heat medium joint 53c is connected to the other outlet of the fourth heat medium joint 53d.

[0085] As is clear 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 do not mix. In addition, the electric heater 54, which is a heat generating section, is only arranged in the low-temperature side heat medium circuit 50. In the high-temperature side heat medium circuit 40, only the water-refrigerant heat exchanger 12 is arranged as a component for heating the high-temperature side heat medium.

[0086] 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 adjusted to an appropriate temperature to an appropriate location in the vehicle cabin for air conditioning. The interior air conditioning unit 30 is disposed inside the instrument panel at the front end of the vehicle cabin.

[0087] 1, the indoor air conditioning unit 30 accommodates an indoor blower 32, an indoor evaporator 18, a heater core 42, etc. in an air conditioning case 31 that forms an air passage for blown air. The air conditioning case 31 is molded from a resin (e.g., polypropylene) that has a certain degree of elasticity and excellent strength.

[0088] An inside / outside air switching device 33 is disposed on the most upstream side of the blown air flow of the air conditioning case 31. The inside / outside air switching device 33 switches between introducing inside air (i.e., air inside the vehicle cabin) and outside air (i.e., air outside the vehicle cabin) into the air conditioning case 31. The operation of the inside / outside air switching device 33 is controlled by a control signal output from the control device 60.

[0089] An interior blower 32 is disposed downstream of the inside / outside air switching device 33 in the flow of blown air. The interior blower 32 blows air drawn in through the inside / outside air switching device 33 toward the vehicle cabin. The interior blower 32 is an electric blower that drives a centrifugal multi-blade fan with an electric motor. The rotation speed (i.e., blowing capacity) of the interior blower 32 is controlled by a control voltage output from the control device 60.

[0090] The indoor evaporator 18 and the heater core 42 are disposed in this order with respect to the flow of the air blown downstream of the indoor blower 32. That is, the indoor evaporator 18 is disposed upstream of the heater core 42 with respect to the flow of the air blown. Also, a cold air bypass passage 35 is formed in the air conditioning case 31, which allows the air blown after passing through the indoor evaporator 18 to flow in a manner that bypasses the heater core 42.

[0091] An air mix door 34 is disposed downstream of the indoor evaporator 18 in the air conditioning case 31 in terms of the blown air flow and upstream of the heater core 42 and the cold air bypass passage 35 in terms of the blown air flow.

[0092] The air mix door 34 is an air volume ratio adjustment unit that adjusts the ratio of the volume of the blown air passing through the heater core 42 side to the volume of the blown air passing through the cold air bypass passage 35, among the blown air after passing through the indoor evaporator 18. The air mix door 34 is driven by an electric actuator for the air mix door. The operation of the electric actuator for the air mix door is controlled by a control signal output from the control device 60.

[0093] A mixing space 36 is disposed downstream of the heater core 42 and the cold air bypass passage 35 in the flow of blown air. The mixing space 36 is a space for mixing the blown air heated by the heater core 42 with the blown air that has passed through the cold air bypass passage 35 and has not been heated. Therefore, in the indoor air conditioning unit 30, the temperature of the blown air (i.e., the conditioned air) mixed in the mixing space 36 can be adjusted by adjusting the opening degree of the air mix door 34.

[0094] At the most downstream portion of the airflow of the air conditioning case 31, a plurality of openings (not shown) are formed for blowing out the blown air mixed in the mixing space 36 into the vehicle cabin. The plurality of openings communicate with a plurality of air outlets formed in the vehicle cabin. The plurality of air outlets include a face air outlet, a foot air outlet, and a defroster air outlet.

[0095] The face air outlet is an outlet that blows air toward the upper body of the occupant, the foot air outlet is an outlet that blows air toward the feet of the occupant, and the defroster air outlet is an outlet that blows air toward the front windshield of the vehicle.

[0096] A blowing mode door (not shown) is disposed in each of the multiple openings. The blowing mode door opens and closes each opening. The blowing mode door is driven by an electric actuator for the blowing mode door. The operation of the electric actuator for the blowing mode door is controlled by a control signal output from the control device 60.

[0097] Therefore, in the interior air conditioning unit 30, the location from which the conditioned air is blown out within the vehicle compartment can be changed by switching the opening hole opened by the blowing mode door.

[0098] Next, an outline of the electric 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 circuits. The control device 60 performs various calculations and processes based on a control program stored in the ROM, and controls the operation of various control target devices 11, 14a to 14c, 15a, 15b, 32 to 34, 41, 51a, 51b, 52a, 52b, 54, etc. connected to its output side.

[0099] 2, an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation sensor 63, a first refrigerant temperature sensor 64a to a third refrigerant temperature sensor 64c, an evaporator temperature sensor 64f, a first refrigerant pressure sensor 65a to a third refrigerant pressure sensor 65c, a high temperature side heat medium temperature sensor 66a, a first low temperature side heat medium temperature sensor 67a to a third low temperature side heat medium temperature sensor 67c, a battery temperature sensor 68, an air conditioning air temperature sensor 69a, an intake air temperature sensor 69b, etc. are connected to the input side of the control device 60. Detection signals of these sensors are input to the control device 60.

[0100] The inside air temperature sensor 61 is an inside air temperature detector that detects the temperature inside the vehicle cabin (inside air temperature) Tr. The outside air temperature sensor 62 is an outside air temperature detector that detects the temperature outside the vehicle cabin (outside air temperature) Tam. The solar radiation sensor 63 is an solar radiation amount detector that detects the amount of solar radiation As irradiated into the vehicle cabin.

[0101] The first refrigerant temperature sensor 64a is a first refrigerant temperature detection unit that detects a first refrigerant temperature TR1, which is the temperature of the refrigerant discharged from the compressor 11. The second refrigerant temperature sensor 64b is a second refrigerant temperature detection unit that detects a second refrigerant temperature TR2, which is the temperature of the refrigerant flowing out from the refrigerant passage 12a of the water-refrigerant heat exchanger 12. The third refrigerant temperature sensor 64c is a third refrigerant temperature detection unit that detects a third refrigerant temperature TR3, which is the temperature of the refrigerant flowing out from the exterior heat exchanger 16.

[0102] 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. Specifically, the evaporator temperature sensor 64f in this embodiment detects the heat exchange fin temperature of the indoor evaporator 18.

[0103] The first refrigerant pressure sensor 65a is a first refrigerant pressure detection unit that detects a first refrigerant pressure PR1 that is the pressure of the refrigerant discharged from the compressor 11. The second refrigerant pressure sensor 65b is a second refrigerant pressure detection unit that detects a second refrigerant pressure PR2 that is the pressure of the refrigerant flowing out from the refrigerant passage 12a of the water-refrigerant heat exchanger 12. The third refrigerant pressure sensor 65c is a third refrigerant pressure detection unit that detects a third refrigerant pressure PR3 that is the pressure of the refrigerant flowing out from the exterior heat exchanger 16.

[0104] The high-temperature side heat medium temperature sensor 66a is a high-temperature side heat medium temperature detection unit that detects a high-temperature side heat medium temperature TWH, which is the temperature of the high-temperature side heat medium flowing into the heater core .

[0105] The first low-temperature side heat medium temperature sensor 67a is a first low-temperature side heat medium temperature detection unit that detects a first low-temperature side heat medium temperature TWL1, which is the temperature of the low-temperature side heat medium pumped from the first low-temperature side pump 51a and flowing into the coolant passage 80a of the battery 80.

[0106] The second low-temperature side heat medium temperature sensor 67b is a second low-temperature side heat medium temperature detection unit that detects a second low-temperature side heat medium temperature TWL2, which is the temperature of the low-temperature side heat medium pumped from the second low-temperature side pump 51b and flowing into the cooling water passage 81a of the high-power equipment 81.

[0107] The third low-temperature side heat medium temperature sensor 67c is a chiller inlet side heat medium temperature detection unit that detects the inlet side heat medium temperature TWin, which is the temperature of the low-temperature side heat medium flowing into the heat medium passage 20b of the chiller 20.

[0108] 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). The battery temperature sensor 68 of this embodiment has multiple temperature sensors and detects the temperatures of multiple locations of the battery 80. Therefore, the control device 60 can detect the temperature difference between the battery cells that form the battery 80. Furthermore, the average value of the detection values ​​of the multiple temperature sensors is used as the battery temperature TB.

[0109] The conditioned air temperature sensor 69a is an air conditioning air temperature detection unit that detects the blown air temperature TAV, which is the temperature of the blown air blown into the vehicle cabin from the mixing space 36. The intake air temperature sensor 69b is an intake air temperature detection unit that detects the intake air temperature TAin, which is the temperature of the blown air flowing into the heater core 42.

[0110] 2, an air conditioning operation panel 70 is connected to the input side of the control device 60. The air conditioning operation panel 70 is disposed near the instrument panel at the front of the vehicle interior. Operation signals are input to the control device 60 from various operation switches provided on the air conditioning operation panel 70.

[0111] The various operation switches provided on the air conditioning operation panel 70 specifically include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, and the like.

[0112] The auto switch is an operation unit that allows the user to set or cancel automatic control operation of the vehicle interior air conditioning. The air conditioner switch is an operation unit that allows the user to request cooling of the blown air by the interior evaporator 18. The air volume setting switch is an operation unit that allows the user to manually set the air volume of the interior blower 32. The temperature setting switch is an operation unit that allows the user to set the set temperature Tset in the vehicle interior.

[0113] The control device 60 of this embodiment is an integrated device that controls various control target devices connected to its output side. The components (hardware and software) of the control device 60 that control the operation of each control target device constitute the control unit that controls the operation of each control target device.

[0114] For example, in the control device 60, a configuration for controlling the refrigerant discharge capacity of the compressor 11 (specifically, the rotation speed of the compressor 11) constitutes a discharge capacity control unit 60a. Also, a configuration for controlling the air blowing capacity of the indoor blower 32 (specifically, the rotation speed of the indoor blower 32) constitutes an air blowing capacity control unit 60b. Also, a configuration for controlling the heating capacity of the electric heater 54 constitutes a heat generation capacity control unit 60c.

[0115] Next, the operation of the air conditioner 1 having the above configuration will be described. As described above, the air conditioner 1 can perform air conditioning in the vehicle cabin and temperature adjustment of the in-vehicle devices. To achieve this, the air conditioner 1 switches the circuit configuration of the heat pump cycle 10 and the circuit configuration of the low-temperature side heat medium circuit 50 to execute various operation modes.

[0116] The operation modes of the air conditioner 1 include an operation mode for air conditioning the vehicle cabin and an operation mode for adjusting the temperature of in-vehicle devices. The air conditioner 1 can execute an appropriate combination of the operation modes for air conditioning and the operation modes for temperature adjustment.

[0117] Therefore, the air conditioner 1 can only condition the air inside the vehicle cabin without adjusting the temperature of the in-vehicle devices. Also, it is possible to adjust the temperature of the in-vehicle devices without conditioning the air inside the vehicle cabin. Also, it is possible to adjust the temperature of the in-vehicle devices while conditioning the air inside the vehicle cabin.

[0118] First, the air conditioning operation modes will be described. The air conditioning operation modes in this embodiment include (A1) a cooling mode, (A2) a series dehumidification and heating mode, (A3) a parallel dehumidification and heating mode, and (A4) a heating mode.

[0119] (A1) The cooling mode is an operation mode in which the ventilation air is cooled and then blown into the passenger compartment, thereby cooling the passenger compartment.

[0120] (A2) The series dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blown air is reheated and blown into the passenger compartment, thereby performing dehumidifying and heating for the passenger compartment.

[0121] (A3) The parallel dehumidifying heating mode is an operating mode in which the cooled and dehumidified blown air is reheated with a heating capacity higher than that in the series dehumidifying heating mode and blown into the passenger compartment, thereby dehumidifying and heating the passenger compartment.

[0122] (A4) The heating mode is an operation mode in which the ventilation air is heated and blown into the passenger compartment, thereby heating the passenger compartment.

[0123] The air conditioning operation mode is switched by executing an air conditioning control program stored in the control device 60. The air conditioning control program is executed when the auto switch on the operation panel 70 is turned on and automatic control operation of the vehicle interior air conditioning is set.

[0124] In the main routine of the air conditioning control program, the detection signals of the above-mentioned sensors and the operation signals of the operation switches of the operation panel 70 are read at predetermined intervals. Then, based on the values ​​of the read detection signals and operation signals, a target blown-out temperature TAO, which is a target temperature of the air blown into the vehicle cabin, is calculated.

[0125] More specifically, the target air outlet temperature TAO is calculated using the following formula F1. TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×As+C…(F1) Here, Tset is the set temperature in the vehicle cabin set by the temperature setting switch on the operation panel 70. Tr is the inside air temperature detected by the inside air temperature sensor 61. Tam is the outside air temperature detected by the outside air temperature sensor 62. As is the amount of solar radiation detected by the solar radiation sensor 63. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

[0126] When the air conditioner switch on the operation panel 70 is turned on and the target blown air temperature TAO is lower than a predetermined cooling target heat medium temperature KTAO1, the air conditioning operation mode is switched to the cooling mode.

[0127] In addition, when the air conditioner switch is turned on, if the target blowing temperature TAO is equal to or higher than the cooling target heat medium temperature KTAO1, and the outside air temperature Tam is higher than a predetermined dehumidification and heating target heat medium temperature KTAO2, the air conditioning operation mode is switched to the series dehumidification and heating mode.

[0128] In addition, when the air conditioner switch is turned on, if the target blowing temperature TAO is equal to or higher than the cooling target heat medium temperature KTAO1 and the outside air temperature Tam is equal to or lower than the dehumidification and heating target heat medium temperature KTAO2, the air conditioning operation mode is switched to the parallel dehumidification and heating mode.

[0129] Furthermore, when the cooling switch of the air conditioner switch is not turned on, the air conditioning operation mode is switched to the heating mode.

[0130] For this reason, the cooling mode is mainly executed when the outside temperature is relatively high, such as in summer. The series dehumidifying and heating mode is mainly executed in spring or autumn. The parallel dehumidifying and heating mode is mainly executed when it is necessary to heat the blown air with a higher heating capacity than the series dehumidifying and heating mode, such as in early spring or late autumn. The heating mode is mainly executed when the outside temperature is low in winter. The detailed operation of each operating mode for air conditioning is explained below.

[0131] (A1) Cooling mode In the cooling mode, the control device 60 fully opens the heating expansion valve 14a and throttles the cooling expansion valve 14b to reduce the pressure of the refrigerant. The cooling expansion valve 14c is controlled according to the temperature adjustment operation mode. This is the same for other air conditioning operation modes. The control device 60 also closes the dehumidification opening / closing valve 15a and the heating opening / closing valve 15b.

[0132] Therefore, in the heat pump cycle 10 in the cooling mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the water-refrigerant heat exchanger 12, the heating expansion valve 14a which is fully open, the outdoor heat exchanger 16, the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 21, and the suction port of the compressor 11.

[0133] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotation speed of the compressor 11 so that the evaporator temperature Tefin detected by the evaporator temperature sensor 64f approaches a target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target air outlet temperature TAO by referring to a control map stored in advance in the control device 60.

[0134] Furthermore, the control device 60 controls the throttle opening degree of the cooling expansion valve 14b so that the degree of supercooling SC3 of the refrigerant flowing into the cooling expansion valve 14b approaches the target degree of supercooling SCO3.

[0135] The degree of subcooling SC3 of the refrigerant flowing into the cooling expansion valve 14b is calculated using a third refrigerant temperature TR3 detected by a third refrigerant temperature sensor 64c and a third refrigerant pressure PR3 detected by a third refrigerant pressure sensor 65c. The target degree of subcooling SCO3 is determined based on the outside air temperature Tam and with reference to a control map previously stored in the control device 60 so that the coefficient of performance (COP) of the cycle approaches a maximum value.

[0136] Furthermore, the control device 60 controls the high temperature side pump 41 so as to exert a predetermined pumping capacity.

[0137] Therefore, in the high-temperature side heat medium circuit 40 in the cooling mode, the high-temperature side heat medium pumped from the high-temperature side pump 41 circulates through the heat medium passage 12b of the water-refrigerant heat exchanger 12, the heater core 42, and the suction port of the high-temperature side pump 41, in that order.

[0138] Furthermore, the control device 60 determines the rotation speed of the indoor blower 32 so as to approach the target blowing capacity determined by the blowing capacity control unit 60b. Therefore, the blowing capacity control unit 60b is a target blowing capacity determination unit. More specifically, the blowing capacity control unit 60b determines the target blowing capacity by referring to a control map stored in advance in the control device 60 based on the target blowing temperature TAO.

[0139] In the control map for the indoor blower 32, when the target blowing temperature TAO is in the extremely low temperature range (i.e., during maximum cooling) or the extremely high temperature range (i.e., during maximum heating), the blowing capacity is determined to be maximum. Furthermore, as the target blowing temperature TAO moves from the extremely low temperature range or the extremely high temperature range toward the intermediate temperature range, the blowing capacity is determined to be reduced. Then, when the target blowing temperature TAO is in the intermediate temperature range, the blowing capacity is determined to be minimum.

[0140] The control device 60 controls the opening degree of the air mix door 34 so that the blowing air temperature TAV detected by the air conditioning air temperature sensor 69a approaches the target blowing temperature TAO. The control device 60 determines the opening and closing operation of the blowing mode door by referring to a control map stored in advance in the control device 60 based on the target blowing temperature TAO.

[0141] Therefore, in the heat pump cycle 10 in the cooling mode, the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as condensers (in other words, heat radiators) that condense the refrigerant by dissipating heat, and the indoor evaporator 18 functions as an evaporator that evaporates the refrigerant, forming a vapor compression refrigeration cycle.

[0142] As a result, in the heat pump cycle 10 in the cooling mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12. Furthermore, the blown air is cooled in the indoor evaporator 18.

[0143] In addition, in the high temperature side heat medium circuit 40 in the cooling mode, the heat medium heated in the water-refrigerant heat exchanger 12 is supplied to the heater core 42.

[0144] In addition, in the interior air conditioning unit 30 in the cooling mode, the blown air blown from the interior blower 32 is cooled by the interior evaporator 18. The blown air cooled by the interior evaporator 18 is temperature-adjusted to approach the target blown temperature TAO by adjusting the opening degree of the air mix door 34. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby cooling the vehicle cabin.

[0145] (A2) Series dehumidification and heating mode In the serial dehumidification heating mode, the controller 60 throttles the heating expansion valve 14a and the cooling expansion valve 14b. The controller 60 also closes the dehumidification opening / closing valve 15a and the heating opening / closing valve 15b.

[0146] Therefore, in the heat pump cycle 10 in the serial dehumidification heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: 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 accumulator 21, and the suction port of the compressor 11.

[0147] Furthermore, the control device 60 appropriately controls the operation of other control target devices. For example, the control device 60 controls the compressor 11 in the same manner as in the cooling mode.

[0148] Furthermore, the control device 60 determines the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14b based on the target blowing temperature TAO, with reference to a control map previously stored in the control device 60, so that the COP approaches the maximum value. In the control map for the serial dehumidification heating mode, it is determined that the throttle opening of the heating expansion valve 14a is decreased and the throttle opening of the cooling expansion valve 14b is increased as the target blowing temperature TAO increases.

[0149] Similarly to the cooling mode, the control device 60 controls the operation of the high-temperature side pump 41 of the high-temperature side heat medium circuit 40, etc. Similarly to the cooling mode, the control device 60 controls the operation of the indoor blower 32 of the indoor air conditioning unit 30, etc.

[0150] Therefore, in the heat pump cycle 10 in the serial dehumidifying 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 outdoor air temperature Tam, the outdoor heat exchanger 16 functions as a condenser. Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outdoor air temperature Tam, the outdoor heat exchanger 16 functions as an evaporator.

[0151] As a result, in the heat pump cycle 10 in the serial dehumidification heating mode, the high temperature side heat medium is heated in the water-refrigerant heat exchanger 12. Furthermore, the blown air is cooled in the indoor evaporator 18.

[0152] In the high temperature side heat medium circuit 40 in the serial dehumidification heating mode, the heat medium heated in the water-refrigerant heat exchanger 12 is supplied to the heater core 42.

[0153] In the interior air conditioning unit 30 in the serial dehumidifying and heating mode, the air blown from the interior blower 32 is cooled and dehumidified in the interior evaporator 18. The temperature of the air cooled and dehumidified in the interior evaporator 18 is adjusted to approach the target blowing temperature TAO by adjusting the opening degree of the air mix door 34. The temperature-adjusted air is then blown into the vehicle cabin, thereby achieving dehumidifying and heating the vehicle cabin.

[0154] Furthermore, in the heat pump cycle 10 in the serial dehumidification heating mode, the throttle opening of the heating expansion valve 14a is decreased and the throttle opening of the cooling expansion valve 14b is increased as the target blowing temperature TAO increases. This makes it possible to improve the heating capacity of the heater core 42 for heating the blown air as the target blowing temperature TAO increases.

[0155] More specifically, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outdoor air temperature Tam, the temperature difference between the saturation temperature of the refrigerant in the outdoor heat exchanger 16 and the outdoor air temperature Tam can be reduced as the target blowing temperature TAO increases. Therefore, as the target blowing temperature TAO increases, the amount of heat dissipated from the refrigerant in the outdoor heat exchanger 16 to the outdoor air can be reduced, and the amount of heat dissipated from the refrigerant to the heat medium in the water-refrigerant heat exchanger 12 can be increased.

[0156] Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, an increase in the target blowing temperature TAO can increase the temperature difference between the outside air temperature Tam and the refrigerant in the outdoor heat exchanger 16. Therefore, an increase in the target blowing temperature TAO can increase the amount of heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 16, thereby increasing the amount of heat released from the refrigerant to the heat medium in the water-refrigerant heat exchanger 12.

[0157] As a result, in the serial dehumidification heating mode, the heating capacity of the heater core 42 for heating the blown air can be improved as the target outlet temperature TAO increases.

[0158] (A3) Parallel dehumidification and heating mode In the parallel dehumidification heating mode, the controller 60 throttles the heating expansion valve 14a and throttles the cooling expansion valve 14b. The controller 60 also opens the dehumidification opening / closing valve 15a and the heating opening / closing valve 15b.

[0159] Therefore, in the heat pump cycle 10 in the parallel dehumidification heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the dehumidification passage 22a, the cooling expansion valve 14b, the indoor evaporator 18, the accumulator 21, and the suction port of the compressor 11. In other words, the outdoor heat exchanger 16 and the indoor evaporator 18 are switched to a refrigerant circuit in which the refrigerant flows in parallel to each other.

[0160] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotation 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.

[0161] The target condensation pressure PDO is determined so that the high-temperature side heat medium temperature TWH detected by the high-temperature side heat medium temperature sensor 66a approaches a predetermined target high-temperature side heat medium temperature TWHO (about 50° C. in this embodiment). The target high-temperature side heat medium temperature TWHO is set so that the heater core 42 constituting the heating section can increase the temperature of the blown air to a temperature that can realize sufficient heating of the vehicle interior.

[0162] Furthermore, the control device 60 determines the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14b based on the target blowing temperature TAO, with reference to a control map previously stored in the control device 60, so that the COP approaches the maximum value. In the control map for the parallel dehumidification heating mode, it is determined that the throttle opening of the heating expansion valve 14a is decreased and the throttle opening of the cooling expansion valve 14b is increased as the target blowing temperature TAO increases.

[0163] Similarly to the cooling mode, the control device 60 controls the operation of the high-temperature side pump 41 of the high-temperature side heat medium circuit 40, etc. Similarly to the cooling mode, the control device 60 controls the operation of the indoor blower 32 of the indoor air conditioning unit 30, etc.

[0164] Therefore, in the heat pump cycle 10 in the parallel dehumidifying 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 in the parallel dehumidifying and heating mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12. Furthermore, the blown air is cooled in the indoor evaporator 18.

[0165] In the high temperature side heat medium circuit 40 in the parallel dehumidification heating mode, the heat medium heated in the water-refrigerant heat exchanger 12 is supplied to the heater core 42.

[0166] In the interior air conditioning unit 30 in the parallel dehumidifying heating mode, the air blown from the interior blower 32 is cooled and dehumidified by the interior evaporator 18. The temperature of the air cooled and dehumidified by the interior evaporator 18 is adjusted to approach the target blowing temperature TAO by adjusting the opening degree of the air mix door 34. The temperature-adjusted air is then blown into the vehicle cabin, thereby achieving dehumidification and heating of the vehicle cabin.

[0167] Furthermore, in the heat pump cycle 10 in the parallel dehumidification heating mode, the throttle opening of the heating expansion valve 14a can be made smaller than the throttle opening of the cooling expansion valve 14b. This allows the refrigerant evaporation temperature in the outdoor heat exchanger 16 to be lowered to a temperature lower than the refrigerant evaporation temperature in the indoor evaporator 18.

[0168] Therefore, in the parallel dehumidifying heating mode, the amount of heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 16 can be increased more than in the series dehumidifying heating mode, and the amount of heat released from the refrigerant to the heat medium in the water-refrigerant heat exchanger 12 can be increased. As a result, in the parallel dehumidifying heating mode, the heating capacity of the heater core 42 for the blown air can be improved more than in the series dehumidifying heating mode.

[0169] (A4) Heating mode In the heating mode, the controller 60 throttles the heating expansion valve 14a and fully closes the cooling expansion valve 14b. The controller 60 also closes the dehumidification opening / closing valve 15a and opens the heating opening / closing valve 15b.

[0170] Therefore, in the heat pump cycle 10 in the heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the suction port of the compressor 11.

[0171] Furthermore, the control device 60 appropriately controls the operation of other devices to be controlled. For example, the control device 60 controls the compressor 11 in the same manner as in the parallel dehumidifying and heating mode.

[0172] Furthermore, the control device 60 controls the throttle opening degree of the heating expansion valve 14a so that the degree of supercooling SC2 of the refrigerant flowing into the heating expansion valve 14a approaches the target degree of supercooling SCO2.

[0173] The degree of subcooling 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. The target degree of subcooling SCO2 is determined based on the second refrigerant temperature TR2, with reference to a control map previously stored in the control device 60, so that the COP approaches the maximum value.

[0174] Similarly to the cooling mode, the control device 60 controls the operation of the high-temperature side pump 41 of the high-temperature side heat medium circuit 40, etc. Similarly to the cooling mode, the control device 60 controls the operation of the indoor blower 32 of the indoor air conditioning unit 30, etc.

[0175] Therefore, in the heat pump cycle 10 in 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 in the heating mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12.

[0176] In the high temperature side heat medium circuit 40 in the heating mode, the heat medium heated in the water-refrigerant heat exchanger 12 is supplied to the heater core 42.

[0177] In the interior air conditioning unit 30 in the heating mode, the air blown from the interior blower 32 passes through the interior evaporator 18. The temperature of the air that has passed through the interior evaporator 18 is adjusted to approach the target blowing temperature TAO by adjusting the opening degree of the air mix door 34. The temperature-adjusted air is then blown into the vehicle interior, thereby heating the vehicle interior.

[0178] Next, the operation mode for temperature adjustment will be described. In the operation mode for temperature adjustment, the temperature of the battery 80 and the high-power equipment 81, which are objects to be adjusted in temperature, is adjusted.

[0179] As described above, in this embodiment, the appropriate temperature zone for the battery 80 is different from the appropriate temperature zone for the high-power equipment 81. For this reason, in the temperature adjustment operation mode, a battery operation mode for adjusting the temperature of the battery 80 and a high-power equipment operation mode for adjusting the temperature of the high-power equipment 81 are combined and executed.

[0180] The operating modes for the battery include (B1) a battery warm-up mode, (B2) a battery equalizing temperature mode, and (B3) a battery cooling mode.

[0181] (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.

[0182] (B2) The battery temperature equalization mode is an operation mode in which the temperatures of the battery cells constituting the battery 80 are equalized.

[0183] (B3) The battery cooling mode is an operation mode in which the battery 80 is cooled by the heat medium cooled by the chiller 20.

[0184] In addition, the operation modes for the high-power equipment include (C1) a high-power equipment warm-up mode, (C2) a high-power equipment waste heat recovery mode, and (C3) a high-power equipment cooling mode.

[0185] (C1) The heavy electric equipment warm-up mode is an operation mode in which the heavy electric equipment 81 is warmed up by the low-temperature side heat medium heated by the electric heater 54.

[0186] (C2) The high-power equipment waste heat recovery mode is an operation mode in which heat generated by the high-power equipment 81 is absorbed by the low-pressure refrigerant in the chiller 20.

[0187] (C3) The high-power equipment cooling mode is an operation mode in which the high-power equipment 81 is cooled by the heat medium cooled by the low-temperature side radiator 56.

[0188] The operation mode for temperature adjustment is switched by executing a control program for temperature adjustment stored in the control device 60. The control program for temperature adjustment is executed when the vehicle system is running, when the battery 80 is being charged from an external power source, etc., regardless of whether the user has requested air conditioning in the vehicle cabin or not.

[0189] The control program for temperature adjustment reads in the detection signals of the above-mentioned sensors at predetermined intervals, and switches the operation mode for temperature adjustment based on the read detection signals.

[0190] More specifically, the temperature adjustment control program switches the battery operation mode by referring to a control map stored in advance in the control device 60 based on the battery temperature TB detected by the battery temperature sensor 68. In the control map, as the battery temperature TB rises, the operation mode is switched in the order of (B1) battery warm-up mode, (B2) battery equalizing temperature mode, and (B3) battery cooling mode.

[0191] Furthermore, the temperature adjustment control program switches the operation mode for the high power system equipment by referring to a control map stored in advance in the control device 60 based on the second low temperature side heat medium temperature TWL2 detected by the second low temperature side heat medium temperature sensor 67b. In the control map, as the second low temperature side heat medium temperature TWL2 rises, the operation mode is switched in the order of (C1) high power system equipment warm-up mode, (C2) high power system equipment waste heat recovery mode, and (C3) high power system equipment cooling mode.

[0192] However, if the battery operation mode and the high-power equipment operation mode cannot be executed simultaneously due to the circuit configuration of the low-temperature side heat medium circuit 50, the battery operation mode is prioritized. For example, if the (B3) battery cooling mode and the (C1) high-power equipment warm-up mode are selected simultaneously, the (C1) high-power equipment warm-up mode is not executed, and the (B3) battery cooling mode is executed. The detailed operation of each operation mode for temperature adjustment is described below.

[0193] (B1) Battery warm-up mode In the battery warm-up mode, the control device 60 fully closes the cooling expansion valve 14c. Therefore, no refrigerant flows into the chiller 20 in the battery warm-up mode.

[0194] The control device 60 also controls the operation of the first low-temperature side three-way valve 52a so as to cause the low-temperature side heat medium flowing out from the coolant passage 80a of the battery 80 to flow to the electric heater 54 side. The control device 60 also controls the operation of the electric heater 54 so as to exert a predetermined heating capacity. The control device 60 also controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity.

[0195] For this reason, in the low-temperature side heat medium circuit 50 in the battery warm-up mode, the low-temperature side heat medium pumped by the first low-temperature side pump 51a is switched to a circuit in which it circulates through the cooling water passage 80a of the battery 80, the electric heater 54, the heat medium passage 20b of the chiller 20, and the suction port of the first low-temperature side pump 51a, in that order.

[0196] Therefore, in the low-temperature side heat medium circuit 50 in the battery warm-up mode, the low-temperature side heat medium heated by the electric heater 54 is drawn into the first low-temperature side pump 51a. The low-temperature side heat medium pumped by the first low-temperature side pump 51a flows into the coolant passage 80a of the battery 80 and dissipates heat to each battery cell of the battery 80. In this way, the battery 80 is warmed up.

[0197] (B2) Battery temperature equalization mode In the battery equalizing temperature mode, the control device 60 controls the operation of the first low-temperature side three-way valve 52a so as to cause the low-temperature side heat medium flowing out from the cooling water passage 80a of the battery 80 to flow to the battery bypass passage 55a side. In addition, the control device 60 controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity.

[0198] Therefore, in the low-temperature side heat medium circuit 50 in the battery equalization mode, the low-temperature side heat medium pumped by the first low-temperature side pump 51a is switched to a circuit in which it circulates through 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 in that order.

[0199] Therefore, in the low-temperature side heat medium circuit 50 in the battery equalization mode, the temperature of each battery cell that constitutes the battery 80 is equalized when the low-temperature side heat medium pumped from the first low-temperature side pump 51a flows through the coolant passage 80a of the battery 80.

[0200] Here, the battery equalization mode is an operation mode aimed at equalizing the temperature of each battery cell of the battery 80. Therefore, even if the battery equalization mode is selected based on the battery temperature TB, the battery equalization mode may be stopped when equalization of the temperature of the battery 80 is not required. An example of a case where equalization of the temperature of the battery 80 is when the temperature difference ΔTB between the battery cells is smaller than a predetermined target cell temperature difference ΔKTB.

[0201] (B3) Battery Cooling Mode The battery cooling mode is an operation mode in which the battery 80 is cooled by the heat medium cooled by the chiller 20. Therefore, when the compressor 11 of the heat pump cycle 10 is operating, such as during air conditioning, the control device 60 throttles the cooling expansion valve 14c of the heat pump cycle 10. Furthermore, when the air conditioning operation mode is the (A4) heating mode, the control device 60 opens the dehumidification opening / closing valve 15a and the heating opening / closing valve 15b.

[0202] Therefore, in the heat pump cycle 10 in the battery cooling mode, the low-pressure refrigerant decompressed 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 accumulator 21 via the sixth refrigerant joint 13f and the fourth refrigerant joint 13d.

[0203] Furthermore, when the battery cooling mode is executed during the execution of the (A4) heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the dehumidification passage 22a, the cooling expansion valve 14c, the chiller 20, the accumulator 21, and the suction port of the compressor 11. In other words, the outdoor heat exchanger 16 and the chiller 20 are switched to a refrigerant circuit in which the refrigerant circulates in parallel with respect to the flow of the refrigerant.

[0204] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the throttle 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 approaches the battery target temperature TWLO1. The battery target temperature TWLO1 is set so that the battery 80 can be operated appropriately.

[0205] The control device 60 also controls the operation of the first low-temperature side three-way valve 52a so as to cause the low-temperature side heat medium flowing out from the cooling water passage 80a of the battery 80 to flow to the electric heater 54. The control device 60 also stops the supply of power to the electric heater 54. The control device 60 also controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity.

[0206] For this reason, in the low-temperature side heat medium circuit 50 in the battery cooling mode, the low-temperature side heat medium pumped by the first low-temperature side pump 51a is switched to a circuit in which it circulates through the cooling water passage 80a of the battery 80, the electric heater 54, the heat medium passage 20b of the chiller 20, and the suction port of the first low-temperature side pump 51a in that order.

[0207] Therefore, in the heat pump cycle 10 in the battery cooling mode during air conditioning, 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, forming a vapor compression refrigeration cycle. As a result, in the heat pump cycle 10 in the battery cooling mode during air conditioning, the low-temperature side heat medium is cooled by the chiller 20.

[0208] In addition, in the low-temperature side heat medium circuit 50, the low-temperature side heat medium cooled by the chiller 20 is sucked into the first low-temperature side pump 51a. The low-temperature side heat medium pumped from the first low-temperature side pump 51a flows into the cooling water passage 80a of the battery 80 and absorbs heat from each battery cell of the battery 80. This cools the battery 80.

[0209] Next, the battery cooling mode during non-air conditioning will be described. In the battery cooling mode during non-air conditioning, the control device 60 fully opens the heating expansion valve 14a, fully closes the cooling expansion valve 14b, and throttles the cooling expansion valve 14c. The control device 60 also closes the dehumidification opening / closing valve 15a and the heating opening / closing valve 15b.

[0210] Therefore, in the heat pump cycle 10 in the battery cooling mode during non-air conditioning, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates in the following order: the water-refrigerant heat exchanger 12, the heating expansion valve 14a which is fully open, the outdoor heat exchanger 16, the cooling expansion valve 14c, the chiller 20, the accumulator 21, and the suction port of the compressor 11.

[0211] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotation speed of the compressor 11 so as to exert a predetermined discharge capacity for the battery cooling mode. The control device 60 also controls the throttle opening of the cooling expansion valve 14c so that the first low-temperature side heat medium temperature TWL1 approaches the battery target temperature TWLO1.

[0212] Furthermore, the control device 60 controls the operation of the first low-temperature side three-way valve 52a, etc., in the same manner as in the battery cooling mode during air conditioning. Therefore, in the low-temperature side heat medium circuit 50 in the battery cooling mode during non-air conditioning, the low-temperature side heat medium is switched to a circuit in which the low-temperature side heat medium circulates in the same order as in the battery cooling mode during air conditioning.

[0213] Therefore, in the heat pump cycle 10 in the battery cooling mode during non-air conditioning, 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 heat pump cycle 10 in the battery cooling mode during non-air conditioning, the low-temperature side heat medium is cooled by the chiller 20.

[0214] Furthermore, in the low-temperature side heat medium circuit 50, the battery 80 is cooled in the same manner as in the battery cooling mode during air conditioning.

[0215] (C1) High-power equipment warm-up mode In the high-power device warm-up mode, the control device 60 fully closes the cooling expansion valve 14c. Therefore, no refrigerant flows into the chiller 20 in the battery warm-up mode.

[0216] The controller 60 also controls the operation of the second low-temperature side three-way valve 52b so as to cause the low-temperature side heat medium flowing out from the cooling water passage 81a of the high-power equipment 81 to flow to the electric heater 54 side. The controller 60 also controls the operation of the electric heater 54 so as to exert a predetermined heating capacity. The controller 60 also controls the operation of the second low-temperature side pump 51b so as to exert a predetermined pumping capacity.

[0217] For this reason, in the low-temperature side heat medium circuit 50 in the battery warm-up mode, the low-temperature side heat medium pumped by the second low-temperature side pump 51b is switched to a circuit in which it circulates in the following order: the cooling water passage 81a of the high-power equipment 81, the electric heater 54, the heat medium passage 20b of the chiller 20, and the suction port of the second low-temperature side pump 51b.

[0218] Therefore, in the low-temperature side heat medium circuit 50 in the high-power equipment warm-up mode, the low-temperature side heat medium heated by the electric heater 54 is sucked into the second low-temperature side pump 51b. The low-temperature side heat medium pumped from the second low-temperature side pump 51b flows into the cooling water passage 81a of the high-power equipment 81 and dissipates heat to the high-power equipment 81. This causes the high-power equipment 81 to be warmed up.

[0219] (C2) High-power equipment waste heat recovery mode The high power appliance waste heat recovery mode is an operation mode in which the waste heat of the high power appliances 81 is used as a heating source for the blown air. Therefore, the high power appliance waste heat recovery mode is executed during air conditioning.

[0220] In the high power equipment waste heat recovery mode, the cooling expansion valve 14c of the heat pump cycle 10 is throttled. Furthermore, when the air conditioning operation mode is the (A4) heating mode, the control device 60 opens the dehumidification opening / closing valve 15a and the heating opening / closing valve 15b.

[0221] Therefore, in the heat pump cycle 10 in the high electric equipment waste heat recovery mode, the low-pressure refrigerant decompressed 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 accumulator 21 via the sixth refrigerant joint 13f and the fourth refrigerant joint 13d.

[0222] Furthermore, when the high-power equipment waste heat recovery mode is executed during the execution of the (A4) heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the dehumidification passage 22a, the cooling expansion valve 14c, the chiller 20, the accumulator 21, and the suction port of the compressor 11. In other words, the outdoor heat exchanger 16 and the chiller 20 are switched to a refrigerant circuit in which the refrigerant circulates in parallel with respect to the flow of the refrigerant.

[0223] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the throttle opening of the cooling expansion valve 14c so that the second low-temperature side heat medium temperature TWL2 approaches the high-power equipment target temperature TWLO2. The high-power equipment target temperature TWLO2 is set so that the high-power equipment 81 can be operated appropriately.

[0224] The control device 60 also controls the operation of the second low-temperature side three-way valve 52b so as to cause the low-temperature side heat medium flowing out from the cooling water passage 81a of the high-power equipment 81 to flow to the electric heater 54. The control device 60 also stops the supply of power to the electric heater 54. The control device 60 also controls the operation of the second low-temperature side pump 51b so as to exert a predetermined pumping capacity.

[0225] For this reason, in the low-temperature side heat medium circuit 50 in the high-power equipment waste heat recovery mode, the low-temperature side heat medium pumped by the second low-temperature side pump 51b is switched to a circuit in which it circulates through the cooling water passage 81a of the high-power equipment 81, the electric heater 54, the heat medium passage 20b of the chiller 20, and the suction port of the second low-temperature side pump 51b in that order.

[0226] Therefore, in the heat pump cycle 10 in the high-power equipment waste heat recovery mode during air conditioning, 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, forming a vapor compression refrigeration cycle. As a result, in the heat pump cycle 10 in the high-power equipment waste heat recovery mode during air conditioning, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12. Furthermore, in the chiller 20, the heat of the low-temperature side heat medium (i.e., the waste heat of the high-power equipment 81) is absorbed by the low-pressure refrigerant.

[0227] In the low-temperature side heat medium circuit 50, the low-temperature side heat medium cooled by the chiller 20 is sucked into the second low-temperature side pump 51b. The low-temperature side heat medium pumped from the second low-temperature side pump 51b flows into the cooling water passage 81a of the high-power equipment 81 and absorbs waste heat from the high-power equipment 81.

[0228] Here, the high power appliance waste heat recovery mode is an operation mode aimed at effectively utilizing the waste heat of the high power appliances 81 as a heat source for heating, etc. Therefore, even if the high power appliance waste heat recovery mode is selected based on the second low temperature side heat medium temperature TWL2, the high power appliance waste heat recovery mode may be stopped when waste heat recovery is not required.

[0229] Examples of cases in which waste heat recovery is not required include cases in which 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 the reference high-temperature side temperature difference KΔTWH2 for recovery.

[0230] (C3) High-power equipment cooling mode In the high power equipment cooling mode, the control device 60 controls the operation of the second low temperature side three-way valve 52b so as to cause 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. In addition, the control device 60 controls the operation of the second low temperature side pump 51b so as to exert a predetermined pumping capacity.

[0231] Therefore, in the low-temperature side heat medium circuit 50 in the high-power equipment cooling mode, the low-temperature side heat medium pumped from the second low-temperature side pump 51b is switched to a circuit in which it circulates through the cooling water passage 81a of the high-power equipment 81, the low-temperature side radiator 56, and the suction port of the second low-temperature side pump 51b in that order.

[0232] Therefore, in the low-temperature side heat medium circuit 50 in the high-power equipment cooling mode, the low-temperature side heat medium cooled by heat exchange with the outside air in the low-temperature side radiator 56 is drawn into the second low-temperature side pump 51b. The low-temperature side heat medium pumped from the second low-temperature side pump 51b flows into the cooling water passage 81a of the high-power equipment 81. As a result, the high-power equipment 81 is cooled.

[0233] As described above, in the air conditioner 1 of this embodiment, by appropriately combining and executing an operating mode for air conditioning and an operating mode for temperature adjustment, it is possible to perform comfortable air conditioning in the vehicle cabin and appropriate temperature adjustment of multiple on-board devices.

[0234] In the air conditioner 1 of this embodiment, when conditioning the vehicle interior, the temperature of the blown air is adjusted by heating the blown air with the heating unit. Therefore, in order to achieve quick-acting and highly responsive air conditioning in the air conditioner 1, it is desirable that the heating unit be in a state where it can exert sufficient heating capacity when air conditioning of the vehicle interior is started.

[0235] The heating section of the present embodiment is formed by the water-refrigerant heat exchanger 12 of the heat pump cycle 10 and each component of the high-temperature side heat medium circuit 40. Therefore, the heating capacity of the heating section can be defined by the high-temperature side heat medium temperature TWH, which is the temperature of the high-temperature side heat medium flowing into the heater core 42.

[0236] Therefore, in the heating section of this embodiment, when starting air conditioning of the vehicle cabin, it is desirable that the high-temperature side heat medium temperature TWH, which corresponds to the actual heating capacity of the heating section, be equal to or higher than the target high-temperature side heat medium temperature TWHO, which corresponds to the reference heating capacity of the heating section.

[0237] In this embodiment, the control flow shown in Fig. 3 is executed to perform heating preparation control for improving the heating capacity of the heating unit when air conditioning in the vehicle cabin is started by utilizing heat generated by the electric heater 54, which is a heat generating unit. The control flow shown in Fig. 3 is executed at predetermined intervals as a subroutine of the main routine of the air conditioning control program. Each control step shown in the flowchart in Fig. 3 is a function realization unit possessed by the control device 60.

[0238] First, in step S1, it is determined whether 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 equal to or greater than a predetermined reference high temperature side temperature difference KΔTWH (15°C in this embodiment).

[0239] As described above, the heating capacity of the heating section in this embodiment can be defined by the high-temperature side heat medium temperature TWH. Therefore, if it is determined in step S1 that the high-temperature side temperature difference ΔTWH is equal to or greater than the reference high-temperature side temperature difference KΔTWH, it is determined that the heating section is not in a state where it can exert sufficient heating capacity to condition the air inside the vehicle, and the process proceeds to step S2. In steps S2 to S7, heating preparation control is executed.

[0240] On the other hand, if it is determined in step S1 that the high temperature side temperature difference ΔTWH is smaller than the reference high temperature side temperature difference KΔTWH, 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 routine.

[0241] In step S2, in order to execute the heating preparation control, the circuit configuration of the heat pump cycle 10 is switched, the circuit configuration of the low-temperature side heat medium circuit is switched, and the operation of various component devices is controlled.

[0242] Specifically, in the heating preparation control, the control device 60 fully closes the heating expansion valve 14a, fully closes the cooling expansion valve 14b, and throttles the cooling expansion valve 14c. The control device 60 also opens the dehumidification opening / closing valve 15a and closes the heating opening / closing valve 15b.

[0243] For this reason, in the heat pump cycle 10 under heating preparation control, as shown by the dashed arrow in FIG. 4, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: the water-refrigerant heat exchanger 12, the dehumidification passage 22a, the cooling expansion valve 14c, the chiller 20, the accumulator 21, and the suction port of the compressor 11.

[0244] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotation speed of the compressor 11 so that the discharge capacity of the compressor 11 is equal to or lower than 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 exhibited in a normal air conditioning operation mode. In this embodiment, specifically, the rotation speed of the compressor 11 is set to 0 rpm. That is, in step S2 of this embodiment, the compressor 11 is stopped.

[0245] Furthermore, the control device 60 controls the throttle opening of the cooling expansion valve 14c so as to achieve a predetermined reference opening for heating preparation control.

[0246] Furthermore, the control device 60 controls the operation of the high temperature side pump 41 so as to exert a predetermined pumping capacity.

[0247] Therefore, in the high-temperature side heat medium circuit 40 during heating preparation control, as shown by the solid arrows in FIG. 4, the high-temperature side heat medium pumped by the high-temperature side pump 41 circulates through the heat medium passage 12b of the water-refrigerant heat exchanger 12, the heater core 42, and the suction port of the high-temperature side pump 41 in that order.

[0248] The controller 60 also controls the operation of the second low-temperature side three-way valve 52b so as to cause the low-temperature side heat medium flowing out from the cooling water passage 81a of the high-power equipment 81 to flow to the electric heater 54 side. The controller 60 also controls the operation of the electric heater 54 so as to exert a predetermined heating capacity. The controller 60 also controls the operation of the second low-temperature side pump 51b so as to exert a predetermined pumping capacity.

[0249] For this reason, in the low-temperature side heat medium circuit 50 in heating preparation control, the low-temperature side heat medium pumped from the second low-temperature side pump 51b circulates through the cooling water passage 81a of the high-power device 81, the electric heater 54, the heat medium passage 20b of the chiller 20, and the suction port of the second low-temperature side pump 51b in this order, as shown by the solid arrows in Fig. 4. In other words, in the low-temperature side heat medium circuit 50 in heating preparation control, the low-temperature side heat medium heated by the electric heater 54 is switched to a circuit that bypasses the cooling water passage 80a of the battery 80.

[0250] Therefore, in the low-temperature side heat medium circuit 50 during heating preparation control, the low-temperature side heat medium pumped by the second low-temperature side pump 51b is heated when passing through the electric heater 54.

[0251] Furthermore, the control device 60 controls the rotation speed of the indoor blower 32 so that the blowing capacity of the indoor blower 32 is equal to or lower than a predetermined reference blowing capacity for heating preparation control. The reference blowing capacity for heating preparation control is set to a value lower than the blowing capacity exhibited in the normal air conditioning operation mode. In this embodiment, specifically, the rotation speed of the indoor blower 32 is set to 0 rpm. That is, in step S2, the indoor blower 32 is stopped.

[0252] Next, in step S3, a target heat medium temperature TWinO is determined. Step S3 is therefore a target heat medium temperature determination unit. The target heat medium temperature TWinO is determined to a value that prevents the inlet side heat medium temperature TWin from dropping below the lower limit heat medium temperature TWmin (15°C in this embodiment) even if the low-pressure refrigerant absorbs heat from the low-temperature side heat medium in the chiller 20. The lower limit heat medium temperature TWmin is set to the lowest temperature of the low-pressure side heat medium that can be used as a heat source for air conditioning.

[0253] More specifically, in step S3, the target heat medium temperature TWinO is determined by referring to a control map stored in advance in the control device 60 based on the intake air temperature TAin detected by the intake air temperature sensor 69b and the target air blowing capacity determined by the air blowing capacity control unit 60b. In the control map for heating preparation control, the target heat medium temperature TWinO is determined to be increased as the intake air temperature TAin decreases. Also, the target heat medium temperature TWinO is determined to be increased as the target air blowing capacity increases.

[0254] 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 equal to or higher than the target heat medium temperature TWinO.

[0255] If it is determined in step S4 that the inlet heat medium temperature TWin is equal to or higher than the target heat medium temperature TWinO, it is determined that the inlet heat medium temperature TWin will not fall below the lower limit heat medium temperature TWmin even if the rotation speed of the compressor 11 is increased, and the process proceeds to step S5.

[0256] On the other hand, if it is determined in step S4 that the inlet side heat medium temperature TWin is not equal to or higher than the target heat medium temperature TWinO, it is determined that increasing the rotation speed of the compressor 11 may cause the inlet side heat medium temperature TWin to fall below the lower limit heat medium temperature TWmin, and the process returns to step S2.

[0257] In step S5, the rotation speed of the compressor 11 is increased. More specifically, in this embodiment, the compressor 11 is operated and controlled in the same manner as in the (A4) heating mode, etc. Therefore, in the heating preparation control of this embodiment, when the inlet heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO, the refrigerant discharge capacity of the compressor 11 is increased.

[0258] As a result, in the heat pump cycle 10, the refrigerant circulates as shown by the dashed arrows in Fig. 4. 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.

[0259] Therefore, in the heat pump cycle 10 during the heating preparation control, heat possessed by the low-temperature side heat medium is absorbed by the low-pressure refrigerant in the chiller 20. Also, in the water-refrigerant heat exchanger 12, the high-temperature side heat medium is heated.

[0260] Next, in step S6, it is determined whether the high temperature side heat medium temperature TWH is equal to or higher than the target high temperature side heat medium temperature TWHO.

[0261] If it is determined in step S6 that the high-temperature side heat medium temperature TWH is equal to or higher than the target high-temperature side heat medium temperature TWHO, it is determined that the heating capacity of the heating unit is equal to or higher than 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, it is determined that the heating capacity of the heating unit is not equal to or higher than the reference heating capacity, and the process returns to step S5.

[0262] In step S7, the rotation speed of the indoor blower 32 is increased. More specifically, in this embodiment, the indoor blower 32 is operated and controlled in the same manner as in the cooling mode, etc. Therefore, in the heating preparation control of this embodiment, when the inlet heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO and the heating capacity of the heating unit becomes equal to or higher than the reference heating capacity, the indoor blower 32 is operated to increase the blowing capacity of the indoor blower 32.

[0263] As a result, in the interior air conditioning unit 30, a part or all of the air blown from the interior blower 32 is heated when passing through the heater core 42. As a result, the temperature-adjusted air is blown into the vehicle cabin, making it possible to air-condition the vehicle cabin.

[0264] As described above, in the air conditioner 1 of this embodiment, the heating preparation control is executed, and therefore the heating capacity of the heating section (high temperature side heat medium temperature TWH in this embodiment) can be quickly increased by using the heat generated by the electric heater 54. As a result, the air conditioner 1 can realize air conditioning with high immediate effect and responsiveness.

[0265] More specifically, in the heating preparation control of this embodiment, as described in step S5, the compressor 11 is stopped until the inlet heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO. Then, when the inlet heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO, the compressor 11 is operated to increase the refrigerant discharge capacity of the compressor 11.

[0266] This makes it possible to suppress an unnecessary increase in the amount of heat absorbed from the low-temperature side heat medium to the low-pressure refrigerant in the chiller 20 until the inlet-side heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO. Therefore, the inlet-side heat medium temperature TWin, which is the temperature of the low-temperature side heat medium, can be quickly increased by the heat generated by the electric heater 54.

[0267] As a result, as shown in Figs. 5 and 6, it is possible to shorten the warm-up time TW required to increase the high-temperature side heat medium temperature TWH to the target high-temperature side heat medium temperature TWHO.

[0268] Here, Fig. 5 is a graph showing changes in the high temperature side heat medium temperature TWH and the inlet side heat medium temperature TWin under comparative conditions in which both the compressor 11 and the indoor blower 32 are operated immediately after energizing the electric heater 54. Note that in Figs. 5 to 7, electricity is energized to the electric heater 54 at an elapsed time of 0 second.

[0269] 6 is a graph showing changes in the high temperature side heat medium temperature TWH and the inlet side heat medium temperature TWin under a first condition in which the compressor 11 and the indoor blower 32 are operated when the inlet side heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO after energization of the electric heater 54. In addition, in FIG. 6, the target heat medium temperature TWinO is determined to be approximately the lower limit heat medium temperature TWmin+20°C.

[0270] Furthermore, in the heating preparation control of this embodiment, as described in step S7, the indoor blower 32 is stopped until the inlet heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO and the high-temperature side heat medium temperature TWH becomes equal to or higher than the target high-temperature side heat medium temperature TWHO. Then, when the inlet heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO and the high-temperature side heat medium temperature TWH becomes equal to or higher than the target high-temperature side heat medium temperature TWHO, the indoor blower 32 is operated.

[0271] This makes it possible to prevent the amount of heat dissipated from the high-temperature side heat medium to the blown air in the heater core 42 constituting the heating section from increasing unnecessarily until the inlet-side heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO and the high-temperature side heat medium temperature TWH becomes equal to or higher than the target high-temperature side heat medium temperature TWHO. Therefore, the inlet-side heat medium temperature TWin can be quickly increased by the heat generated by the electric heater 54.

[0272] As a result, as shown in FIG. 7, the warm-up time TW can be further shortened.

[0273] 7 is a graph showing changes in the high-temperature side heat medium temperature TWH and the inlet-side heat medium temperature TWin under a first condition in which the compressor 11 is operated when the inlet-side heat medium temperature TWin becomes equal to or higher than the target heat medium temperature TWinO after the electric heater 54 is energized, and then the indoor blower 32 is operated when the high-temperature side heat medium temperature TWH becomes equal to or higher than the target high-temperature side heat medium temperature TWHO. In addition, in FIG. 7, the target heat medium temperature TWinO is determined to be about the lower-limit heat medium temperature TWmin+10°C.

[0274] As described in step S1, the heating preparation control of this embodiment is executed when the high temperature side temperature difference ΔTWH is equal to or greater than the reference high temperature side temperature difference KΔTWH. Therefore, the heating preparation control of this embodiment is executed when the heating capacity of the heating unit is insufficient. This makes it possible to prevent the interior blower 32 from frequently stopping due to unnecessary execution of the heating preparation control, i.e., to prevent the air conditioning in the vehicle cabin from stopping.

[0275] Furthermore, in the heating preparation control of this embodiment, as described in step S2, the second low-temperature side three-way valve 52b, which is the heat medium circuit switching unit, switches the circuit configuration 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 bypassing the coolant passage 80a of the battery 80.

[0276] This makes it possible to prevent the heat of the low-temperature side heat medium heated by the electric heater 54 from being absorbed by the battery 80, which has a relatively large heat capacity, and to quickly increase the inlet side heat medium temperature TWin. As a result, the warm-up time TW can be further shortened.

[0277] In the heating preparation control of this embodiment, as described in step S2, the cooling expansion valve 14b is fully closed. Furthermore, a third check valve 17c configured to be able to close the refrigerant outlet side is disposed on the refrigerant outlet side of the indoor evaporator 18.

[0278] With this, even if the low-temperature side heat medium heated by the electric heater 54 flows into the heat medium passage 20b of the chiller 20 and the refrigerant pressure in the refrigerant passage 20a rises, it is possible to prevent the refrigerant from flowing back from the chiller 20 side into the indoor evaporator 18. As a result, it is possible to prevent the refrigerant from accumulating in the indoor evaporator 18, that is, the so-called refrigerant stagnation phenomenon.

[0279] Similarly, in the heating preparation control of this embodiment, as described in step S2, the heating expansion valve 14a is fully closed and the heating on-off valve 15b is closed. Furthermore, a first check valve 17a and a second check valve 17b configured to be able to close the refrigerant outlet side are arranged on the refrigerant outlet side of the outdoor heat exchanger 16.

[0280] With this, even if the low-temperature side heat medium heated by the electric heater 54 flows into the heat medium passage 20b of the chiller 20 and the refrigerant pressure in the refrigerant passage 20a increases, it is possible to prevent the refrigerant from flowing back from the chiller 20 side into the outdoor heat exchanger 16. As a result, it is possible to prevent the refrigerant from stagnation in the outdoor heat exchanger 16.

[0281] In step S3, which is the target heat medium temperature determination section of this embodiment, the target heat medium temperature TWinO is determined to be increased as the intake air temperature TAin decreases and as the target blowing capacity increases.

[0282] According to this, when the indoor blower 32 is operated, the target heat medium temperature TWinO can be increased with an increase in the amount of heat dissipated from the high-temperature side heat medium to the blown air in the heater core 42. Therefore, as shown in Fig. 7, it is possible to suppress an increase in the temperature drop ΔTL of the high-temperature side heat medium temperature TWH immediately after the indoor blower 32 is operated.

[0283] In the heating preparation control of this embodiment, as described in step S2, an example has been described in which the refrigerant circuit of the heat pump cycle 10 is switched to a refrigerant circuit that circulates the refrigerant as shown by the dashed arrow in Figure 4, but this is not limited to the example.

[0284] For example, as a modification of the heating preparation control, in step S2, the control device 60 sets the heating expansion valve 14a in a throttled state, the cooling expansion valve 14b in a fully closed state, and the cooling expansion valve 14c in a throttled state. Furthermore, the control device 60 opens the dehumidification opening / closing valve 15a and the heating opening / closing valve 15b.

[0285] Therefore, in the heat pump cycle 10 of the modified example, as shown by the dashed arrow in Fig. 8, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, the accumulator 21, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the first refrigerant joint 13a, the dehumidification passage 22a, the cooling expansion valve 14c, the chiller 20, the accumulator 21, and the suction port of the compressor 11. In other words, the refrigerant circuit is switched to one in which the outdoor heat exchanger 16 and the chiller 20 are connected in parallel with respect to the refrigerant flow.

[0286] Furthermore, the control device 60 appropriately controls the operation of other control target devices of the heat pump cycle 10. For example, the control device 60 controls the throttle opening of the heating expansion valve 14a so that the refrigerant evaporation temperature in the outdoor heat exchanger 16 becomes lower than the outdoor air temperature Tam. The other operations are the same as the heating preparation control of the first embodiment described above.

[0287] Therefore, in the modified heating preparation control, not only is heat generated by the electric heater 54 in the chiller 20 absorbed, but the high temperature side heat medium can be heated by utilizing heat absorbed from the outside air in the exterior heat exchanger 16. As a result, the heating capacity of the heating section can be increased even more quickly. The modified heating preparation control is effective when executed in cases such as when the outside air temperature Tam is higher than the refrigerant evaporation temperature in the chiller 20.

[0288] As shown in the overall configuration diagram of Fig. 9, when the outdoor heat exchanger 16 is equipped with the shutter device 16a, in another modified example of the heating preparation control, in step S2, the control device 60 fully opens the heating expansion valve 14a, fully closes the cooling expansion valve 14b, and throttles the cooling expansion valve 14c. Furthermore, the control device 60 closes the dehumidification opening / closing valve 15a and closes the heating opening / closing valve 15b. The control device 60 also fully closes the shutter device 16a.

[0289] The shutter device 16a adjusts the flow rate of outdoor air flowing into the outdoor air passage of the outdoor heat exchanger 16, thereby continuously adjusting the amount of heat exchanged between the refrigerant and the outdoor air in the outdoor heat exchanger 16. The shutter device 16a can also stop heat exchange between the refrigerant and the outdoor air in the outdoor heat exchanger 16 by bringing the shutter device 16a into a fully closed state that blocks the outdoor air passage of the outdoor heat exchanger 16. The operation of the shutter device 16a is controlled by a control signal output from the control device 60.

[0290] 9, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the order of the water-refrigerant heat exchanger 12, the heating expansion valve 14a which is fully open, the outdoor heat exchanger 16, the cooling expansion valve 14c, the chiller 20, the accumulator 21, and the suction port of the compressor 11. The other operations are the same as those of the above-mentioned embodiment.

[0291] In the other modified example, the shutter device 16a is fully closed, so that heat exchange between the refrigerant and the outside air is not performed in the outdoor heat exchanger 16. Therefore, the heat pump cycle 10 in the heating preparation control of the other modified example operates in the same manner as in the first embodiment. Therefore, according to the heating preparation control of the other modified example, it is possible to obtain the same effect as the heating preparation control of the first embodiment.

[0292] Second embodiment In this embodiment, an example will be described in which the configuration of the heating section of the heat pump cycle 10 is changed from that of the air conditioner 1 of the first embodiment. Specifically, in the heat pump cycle 10 of this embodiment, as shown in the overall configuration diagram of Fig. 10, the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 are eliminated, and an indoor condenser 121 is used as the heating section.

[0293] The indoor condenser 121 is a heating heat exchanger that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air to heat the blown air. The indoor condenser 121 is disposed in the air conditioning case 1 of the indoor air conditioning unit 30, similar to the heater core 42.

[0294] Further, the second refrigerant temperature sensor 64b of this embodiment detects the temperature of the refrigerant flowing out from the indoor condenser 121 as a second refrigerant temperature TR2. The second refrigerant pressure sensor 65b of this embodiment detects the pressure of the refrigerant flowing out from the indoor condenser 121 as a second refrigerant pressure PR2. The other configurations of the air conditioner 1 are similar to those of the first embodiment.

[0295] In addition, in this embodiment, the target condensation pressure PDO used in the parallel heating mode, etc., is a value determined so that the refrigerant condensation temperature in the indoor condenser 121 approaches the target condensation temperature TDO (approximately 50°C in this embodiment).

[0296] Here, the heating section in this embodiment is formed by the indoor condenser 121. Therefore, the heating capacity of the heating section 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.

[0297] Therefore, in the heating section of this embodiment, when starting air conditioning of the vehicle cabin, it is desirable that the second refrigerant temperature TR2 corresponding to the actual heating capacity of the heating section is equal to or higher than the target condensing temperature TDO corresponding to the reference heating capacity of the heating section, or that the second refrigerant pressure PR2 corresponding to the actual heating capacity of the heating section is equal to or higher than the target condensing pressure PDO corresponding to the reference heating capacity of the heating section.

[0298] In this embodiment, in step S1 of the heating preparation control, it is determined whether the pressure difference ΔPH obtained by subtracting the second refrigerant pressure PR2 from the target condensation pressure PDO is equal to or greater than a predetermined reference pressure difference KΔPH. Here, in this embodiment, the refrigerant is set so that the temperature at the pressure obtained by subtracting the reference pressure difference KΔPH from the target condensation pressure PDO is about 15° C. lower than the target condensation temperature TDO.

[0299] If it is determined in step S1 that the pressure difference ΔPH is equal to or greater than the reference pressure difference KΔPH, it is determined that the heating unit is not in a state where it can exert a sufficient heating capacity, and the process proceeds to step S2. On the other hand, if it is determined in step S1 that the pressure difference ΔPH is smaller than the reference pressure difference KΔPH, it is determined that the heating unit is in a state where it can exert a sufficient heating capacity, and the process returns to the main routine.

[0300] Similarly, in step S6 of the heating preparation control in this embodiment, it is determined whether the second refrigerant pressure PR2 is equal to or higher than the target condensation pressure PDO.

[0301] If it is determined in step S6 that the second refrigerant pressure PR2 is equal to or higher than the target condensation pressure PDO, it is determined that the heating capacity of the heating unit is equal to or higher than 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 lower than the target condensation pressure PDO, it is determined that the heating capacity of the heating unit is not equal to or higher than the reference heating capacity, and the process returns to step S5. Other operations of the air conditioner 1 are the same as those in the first embodiment.

[0302] Therefore, according to the air conditioner 1 of this embodiment, the same effects as those of the first embodiment can be obtained. That is, the air conditioner 1 of this embodiment can also perform comfortable air conditioning in the vehicle cabin and appropriate temperature adjustment of a plurality of in-vehicle devices. Furthermore, the heat generated by the electric heater 54 can be used to quickly increase the heating capacity of the heating section (in this embodiment, the target condensation pressure PDO). As a result, air conditioning with immediate effect and high responsiveness can be realized.

[0303] Third embodiment In this embodiment, an example will be described in which an inlet side connecting passage 91, an outlet side connecting passage 92, etc. are added to the air conditioner 1 of the first embodiment, as shown in the overall configuration diagram of Fig. 11. The inlet side connecting passage 91 and the outlet side connecting 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.

[0304] Furthermore, a high-temperature side three-way valve 43 is disposed in a heat medium flow path extending from the outlet of the heat medium passage 12b of the water-refrigerant heat exchanger 12 of the high-temperature side heat medium circuit 40 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 therein and then out to at least one of the heater core 42 side and the inlet side connecting passage 91 side.

[0305] The high-temperature side three-way valve 43 can continuously adjust the flow rate ratio between the flow rate of the high-temperature side heat medium flowing out to the heater core 42 side and the flow rate of the high-temperature side heat medium flowing out to the inlet side connecting passage 91 side. Furthermore, the high-temperature side three-way valve 43 can cause the total flow rate of the high-temperature side heat medium flowing inside to flow out to either the heater core 42 side or the inlet side connecting passage 91 side by adjusting the flow rate ratio.

[0306] An inlet portion of the inlet side connecting passage 91 is connected to one of the outlets of the high temperature side three-way valve 43. In addition, an outlet portion of the inlet side connecting passage 91 is connected to one of the inlets of a fifth heat medium joint portion 53e that is disposed in a heat medium flow path leading from the discharge port of the first low temperature side pump 51a of the low temperature side heat medium circuit 50 to the inlet of the coolant passage 80a of the battery 80.

[0307] An inlet portion of the outlet side connecting passage 92 is connected to one outlet of a sixth heat medium joint portion 53f arranged in a heat medium flow path leading from the outlet of the coolant 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. In addition, an outlet portion of the outlet side connecting passage 92 is connected to one inlet of a seventh heat medium joint portion 53g arranged in a heat medium flow path leading from the other 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 rest of the configuration of the air conditioner 1 is similar to that of the first embodiment.

[0308] Next, the operation of the air conditioner 1 of this embodiment with the above configuration will be described. In the air conditioner 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 to the heater core 42 side.

[0309] Therefore, when the air conditioning operation mode and the temperature adjustment operation mode are executed, the circuit configurations of the heat pump cycle 10, the high-temperature side heat medium circuit 40, and the low-temperature side heat medium circuit 50 are the same as those in the first embodiment. Therefore, in the air conditioner 1 of this embodiment, by executing an appropriate combination of the air conditioning operation mode and the temperature adjustment operation mode, it is possible to perform comfortable air conditioning in the vehicle cabin and appropriate temperature adjustment of multiple on-board devices.

[0310] Furthermore, in the air conditioner 1 of this embodiment, similarly to the first embodiment, heating preparation control can be performed. Therefore, the heating capacity of the heating unit can be quickly increased by using the heat generated by the electric heater 54. As a result, air conditioning with immediate effect and high responsiveness can be realized.

[0311] The heating preparation control is executed for the purpose of quickly improving the heating capacity of the heater when air conditioning in the vehicle cabin is started. For this reason, the heating preparation control is often executed before air conditioning is started when the outside air temperature is relatively low. When the outside air temperature is low, it may be necessary to warm up the battery 80.

[0312] On the other hand, in the low-temperature side heat medium circuit 50 during the heating preparation control, the low-temperature side heat medium heated by the electric heater 54 is switched to a circuit that bypasses the coolant passage 80a of the battery 80. For this reason, the low-temperature side heat medium heated by the electric heater 54 cannot be caused to flow into the coolant passage 80a of the battery 80 to warm up the battery 80.

[0313] Therefore, in this embodiment, when the heating preparation control is being executed and the battery temperature TB is equal to or lower than a predetermined reference warm-up temperature KTBL, the control device 60 controls the operation of the high temperature side three-way valve 43 so as to cause the high temperature side heat medium flowing out of the heat medium passage 12b of the water-refrigerant heat exchanger 12 to flow to the inlet side connecting passage 91. The reference warm-up temperature KTBL is set to a temperature at which it is determined that the battery 80 needs to be warmed up.

[0314] For this reason, in the air conditioner 1 of this embodiment, when warming up of the battery 80 is required during execution of the heating preparation control, the high-temperature side heat medium pumped by the high-temperature side pump 41 circulates in this order through the heat medium passage 12b of the water-refrigerant heat exchanger 12, the high-temperature side three-way valve 43, the inlet side connecting passage 91, the coolant passage 80a of the battery 80, the outlet side connecting passage 92, the heater core 42, and the suction port of the high-temperature side pump 41, as shown by the solid arrows in FIG. 11 .

[0315] According to this, when the compressor 11 is operated in step S5 of the heating preparation control described in the first embodiment, the high-temperature side heat medium can be heated in the water-refrigerant heat exchanger 12. Then, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12 can be caused to flow into the cooling water passage 80a of the battery 80 via the high-temperature side three-way valve 43 and the inlet side connecting passage 91. This allows the battery 80 to be warmed up.

[0316] The high-temperature side heat medium flowing out from the coolant passage 80a of the battery 80 flows into the heater core 42 via the outlet-side connecting passage 92. In the heating preparation control, the indoor blower 32 is stopped until the high-temperature side heat medium temperature TWH becomes equal to or higher than the target high-temperature side heat medium temperature TWHO. Therefore, the high-temperature side heat medium that has flowed into the heater core 42 flows out of the heater core 42 without exchanging heat with the blown air, and is sucked into the high-temperature side pump 41.

[0317] Other operations are the same as those in the first embodiment. Therefore, according to the air conditioner 1 of this embodiment, the battery 80 can be warmed up during the execution of the heating preparation control.

[0318] (Fourth embodiment) In this embodiment, an air conditioner 1a shown in the overall configuration diagram of Fig. 12 will be described. The air conditioner 1a of this embodiment is used as a vehicle air conditioner with an in-vehicle equipment temperature adjustment function, similar to the first embodiment. The air conditioner 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.

[0319] Here, the configuration of the indoor air conditioning unit 30 of the air conditioner 1a is the same as that of the first embodiment. Therefore, in Fig. 12, for clarity of illustration, 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 40 are disposed in the air conditioning case 1 of the indoor air conditioning unit 30, as in the first embodiment.

[0320] In the heat pump cycle 10a of the present embodiment, the first refrigerant joint portion 13a, the heating expansion valve 14a, the outdoor heat exchanger 16, the accumulator 21, and the like are eliminated from the heat pump cycle 10 described in the first embodiment.

[0321] In the heat pump cycle 10a, an inlet side of a receiver 23 is connected to an outlet of a refrigerant passage 12a of the water-refrigerant heat exchanger 12. The receiver 23 is a high-pressure side gas-liquid separator that separates the high-pressure refrigerant flowing out from the refrigerant passage 12a of the water-refrigerant heat exchanger 12 into gas and liquid and stores the excess liquid-phase refrigerant in the cycle. The refrigerant outlet of the receiver 23 is connected to an inlet side of a fifth refrigerant joint 13e.

[0322] Other configurations of the heat pump cycle 10a are similar to those of the heat pump cycle 10 described in the first embodiment.

[0323] In the present embodiment, the high temperature side heat medium circuit 40a includes the heat medium passage 12b of the 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, and the like.

[0324] The high-temperature side three-way valve 43 of the present embodiment allows the high-temperature side heat medium flowing out from the heat medium passage 12b of the water-refrigerant heat exchanger 12 to flow therein and then out to at least one of the heater core 42 side and the high-temperature side radiator 44 side.

[0325] High-temperature side three-way valve 43 can continuously adjust the flow rate ratio between the flow rate of the high-temperature side heat medium flowing out to the heater core 42 side and the flow rate of the high-temperature side heat medium flowing out to the high-temperature side radiator 44 side. Furthermore, high-temperature side three-way valve 43 can cause the total flow rate of the high-temperature side heat medium flowing into it to flow out to either the heater core 42 side or the high-temperature side radiator 44 side by adjusting the flow rate ratio.

[0326] The high-temperature side radiator 44 is an outside air heat exchanger on the high-temperature side that exchanges heat between the outside air and the high-temperature side heat medium flowing out from the high-temperature side three-way valve 43 .

[0327] One inlet side of the eighth heat medium joint portion 53h is connected to the heat medium outlet of the high temperature side radiator 44. The other inlet side of the eighth heat medium joint portion 53h is connected to the heat medium outlet of the heater core 42 of this embodiment. The suction port side of the high temperature side pump 41 is connected to the outlet of the eighth heat medium joint portion 53h.

[0328] The rest of the configuration of the high temperature side heat medium circuit 40a is similar to that of the high temperature side heat medium circuit 40 described in the first embodiment.

[0329] In addition, the low-temperature side heat medium circuit 50a of this embodiment is provided 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 of the chiller 20, a cooling water passage 80a of the battery 80, a cooling water passage 81a of the high-power system equipment 81, an electric heater 54, a high-power system equipment bypass passage 55b, a low-temperature side radiator 56, and the like.

[0330] In the low-temperature side heat medium circuit 50a, the discharge port 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.

[0331] In this embodiment, the first low-temperature side three-way valve 52a allows the low-temperature side heat medium flowing out from the heat medium passage 20b of the chiller 20 to flow into its interior and 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.

[0332] The first low-temperature side three-way valve 52a can continuously adjust the flow rate ratio between the flow rate of the low-temperature side heat medium flowing out to the electric heater 54 side and the flow rate of the low-temperature side heat medium flowing out to the third low-temperature side three-way valve 52c side. Furthermore, the first low-temperature side three-way valve 52a can cause the total flow rate of the low-temperature side heat medium flowing therein to flow out to either the electric heater 54 side or the third low-temperature side three-way valve 52c side by adjusting the flow rate ratio.

[0333] One inlet side of a ninth heat medium joint portion 53i is connected to the outlet of the heating flow path of the electric heater 54. The suction port side of the first low-temperature side pump 51a is connected to the outlet of the ninth heat medium joint portion 53i.

[0334] The third low-temperature side three-way valve 52c allows the low-temperature side heat medium flowing out from the first low-temperature side three-way valve 52a to flow into its interior and out to at least one of the cooling water passage 80a side of the battery 80 and one of the inlet sides of the tenth heat medium joint portion 53j.

[0335] The third low-temperature side three-way valve 52c can continuously adjust the flow rate ratio between the flow rate of the low-temperature side heat medium flowing out to the cooling water passage 80a side of the battery 80 and the flow rate of the low-temperature side heat medium flowing out to the tenth heat medium joint portion 53j side. Furthermore, the third low-temperature side three-way valve 52c can cause the total flow rate of the low-temperature side heat medium flowing inside to flow out to either the cooling water passage 80a side of the battery 80 or the tenth heat medium joint portion 53j side by adjusting the flow rate ratio.

[0336] One inlet side of an eleventh heat medium joint portion 53k is connected to the outlet of the coolant passage 80a of the battery 80. The other inlet side of the ninth heat medium joint portion 53i is connected to the outlet of the eleventh heat medium joint portion 53k.

[0337] In the low-temperature side heat medium circuit 50a, the discharge port of the second low-temperature side pump 51b is connected to the inlet side of a cooling water passage 81a of the high-power device 81. The outlet of the cooling water passage 81a of the high-power device 81 is connected to the inlet side of the second low-temperature side three-way valve 52b.

[0338] The second low-temperature side three-way valve 52b in this embodiment allows the low-temperature side heat medium flowing out from the cooling water passage 81a of the high-power system equipment 81 to flow into its interior and out to at least one of the other inlet side of the tenth heat medium joint portion 53j and the high-power system equipment bypass passage 55b side.

[0339] The second low-temperature side three-way valve 52b can continuously adjust the flow rate ratio between the flow rate to be flowed out to the tenth heat medium joint portion 53j side and the flow rate of the low-temperature side heat medium to be flowed out to the high electric equipment bypass passage 55b side. Furthermore, the second low-temperature side three-way valve 52b can adjust the flow rate ratio to cause the total flow rate of the low-temperature side heat medium flowing therein to flow out to either the tenth heat medium joint portion 53j side or the high electric equipment bypass passage 55b side.

[0340] The high-power system device bypass passage 55b is a heat medium passage that guides the low-temperature side heat medium flowing out from the cooling water passage 81a of the high-power system device 81 to the suction port side of the second low-temperature side pump 51b, bypassing the low-temperature side radiator 56, etc. One inlet of the twelfth heat medium joint 53m is connected to the outlet of the high-power system device bypass passage 55b. The suction port side of the second low-temperature side pump 51b is connected to the outlet of the twelfth heat medium joint 53m.

[0341] The heat medium inlet side of the low-temperature side radiator 56 is connected to the outlet of the tenth heat medium joint 53j. The heat medium outlet of the low-temperature side radiator 56 is connected to the inlet side of the thirteenth heat medium joint 53n. The other inlet side of the twelfth heat medium joint 53m is connected to one outlet of the thirteenth heat medium joint 53n. The other inlet side of the eleventh heat medium joint 53k is connected to the other outlet of the thirteenth heat medium joint 53n.

[0342] The rest of the configuration of the low-temperature side heat medium circuit 50a is similar to that of the low-temperature side heat medium circuit 50 described in the first embodiment.

[0343] Next, the operation of the air conditioner 1a of this embodiment in the above configuration will be described. In the air conditioner 1a of this embodiment, there are (A1) cooling mode, (A2) dehumidification heating mode, and (A3) heating mode as air conditioning operation modes. As in the first embodiment, the air conditioning operation modes are switched by executing the air conditioning control program stored in the control device 60. The detailed operation of each air conditioning operation mode will be described below.

[0344] (A1) Cooling mode In the cooling mode, the control device 60 throttles the cooling expansion valve 14b. The cooling expansion valve 14c is controlled in accordance with the operation mode for temperature adjustment, similarly to the first embodiment.

[0345] Therefore, in the heat pump cycle 10a in cooling mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the water-refrigerant heat exchanger 12, the receiver 23, the cooling expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11 in that order.

[0346] 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 manner as in the cooling mode of the first embodiment. The control device 60 controls the throttle opening of the cooling expansion valve 14c so that the superheat degree SH of the refrigerant on the outlet side of the indoor evaporator 18 approaches a predetermined reference superheat degree KSH.

[0347] The controller 60 also controls the operation of the high-temperature side pump 41 so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium temperature TWH approaches the target high-temperature side heat medium temperature TWHO.

[0348] For this reason, in the high-temperature side heat medium circuit 40 in the cooling mode, the high-temperature side heat medium pumped by the high-temperature side pump 41 is switched to a refrigerant circuit in which it circulates through the water-refrigerant heat exchanger 12, the heater core 42, and the suction port of the high-temperature side pump 41 in that order. At the same time, the high-temperature side heat medium pumped by the high-temperature side pump 41 is switched to a refrigerant circuit in which it circulates through the water-refrigerant heat exchanger 12, the high-temperature side radiator 44, and the suction port of the high-temperature side pump 41 in that order. In other words, the heater core 42 and the high-temperature side radiator 44 are switched to a circuit in which they are connected in parallel with respect to the flow of the high-temperature side heat medium.

[0349] Here, in the cooling mode, the amount of heat exchanged between the high-temperature side heat medium and the blown air in the heater core 42 is small. Therefore, in the cooling mode, the high-temperature side three-way valve 43 allows almost the entire flow rate of the high-temperature side heat medium flowing out from the heat medium passage 12b of the water-refrigerant heat exchanger 12 to flow to the high-temperature side radiator 44. The other operations are the same as those in the cooling mode described in the first embodiment.

[0350] Therefore, in the heat pump cycle 10a in the 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 the cooling mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12. Furthermore, the blown air is cooled in the indoor evaporator 18.

[0351] In the high-temperature side heat medium circuit 40a in the cooling mode, the heat medium heated in the water-refrigerant heat exchanger 12 is supplied to the heater core 42 in accordance with the flow rate ratio control of the high-temperature side three-way valve 43.

[0352] In addition, in the interior air conditioning unit 30 in the cooling mode, the blown air blown from the interior blower 32 is cooled by the interior evaporator 18. The blown air cooled by the interior evaporator 18 is temperature-adjusted to approach the target blown temperature TAO by adjusting the opening degree of the air mix door 34. Then, the temperature-adjusted blown air is blown into the vehicle cabin, thereby cooling the vehicle cabin.

[0353] (A2) Dehumidification heating mode In the dehumidifying and heating mode, the control device 60 puts the cooling expansion valve 14b in a throttled state and the cooling expansion valve 14c in a throttled state.

[0354] Therefore, in the heat pump cycle 10a in the dehumidifying and heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 12, the receiver 23, the cooling expansion valve 14b, the indoor evaporator 18, and the suction port of the compressor 11. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant discharged from the compressor 11 circulates in the order of the water-refrigerant heat exchanger 12, the receiver 23, the cooling expansion valve 14c, the chiller 20, and the suction port of the compressor 11. In other words, the refrigerant circuit is switched to one in which the indoor evaporator 18 and the chiller 20 are connected in parallel with respect to the flow of the refrigerant.

[0355] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the compressor 11 is controlled in the same manner as in the parallel dehumidification heating mode of the first embodiment. The control device 60 also controls the throttle 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.

[0356] The controller 60 also controls the operation of the high-temperature side pump 41 so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium temperature TWH approaches the target high-temperature side heat medium temperature TWHO.

[0357] Therefore, in the dehumidifying and heating mode, the high temperature side heat medium circuit 40a is switched to a circuit in which the high temperature side heat medium circulates in the same order as in the cooling mode.

[0358] Furthermore, the control device 60 controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity.

[0359] The controller 60 also controls the operation of the first low-temperature side three-way valve 52a so as to cause the low-temperature side heat medium flowing out of the heat medium passage 20b of the chiller 20 to flow to the third low-temperature side three-way valve 52c. The controller 60 also controls the operation of the third low-temperature side three-way valve 52c so as to cause the low-temperature side heat medium flowing out of the first low-temperature side three-way valve 52a to flow to the tenth heat medium joint portion 53j. The controller 60 also controls the operation of the second low-temperature side three-way valve 52b so as to cause the low-temperature side heat medium flowing out of the third low-temperature side three-way valve 52c to flow to the low-temperature side radiator 56.

[0360] For this reason, in the dehumidifying and heating mode, the low-temperature side heat medium circuit 50a is switched to a circuit in which the low-temperature side heat medium pumped 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, in that order. Other operations are the same as in the cooling mode.

[0361] Therefore, in the heat pump cycle 10a in the dehumidifying 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 and the chiller 20 function as evaporators.

[0362] As a result, in the heat pump cycle 10a in the dehumidifying heating mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12. The blown air is cooled in the indoor evaporator 18. Furthermore, in the chiller 20, the low-pressure refrigerant absorbs heat from the low-temperature side heat medium, and the temperature of the low-temperature side heat medium becomes lower than the outside air temperature.

[0363] In the high-temperature side heat medium circuit 40a in the dehumidification heating mode, the heat medium heated in the water-refrigerant heat exchanger 12 is supplied to the heater core 42 in accordance with the flow rate ratio control of the high-temperature side three-way valve 43.

[0364] In the low-temperature side heat medium circuit 50a in the dehumidifying heating mode, the low-temperature side heat medium cooled in 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 that flows into the low-temperature side radiator 56 absorbs heat from the outside air. The low-temperature side heat medium that has absorbed heat from the outside air in the low-temperature side radiator 56 and has increased in temperature is sucked into the first low-temperature side pump 51a and pumped to the heat medium passage 20b of the chiller 20.

[0365] In the interior air conditioning unit 30 in the dehumidifying heating mode, the air blown from the interior blower 32 is cooled and dehumidified by the interior evaporator 18. The temperature of the air cooled and dehumidified by the interior evaporator 18 is adjusted to approach the target blowing temperature TAO by adjusting the opening degree of the air mix door 34. The temperature-adjusted air is then blown into the vehicle cabin, thereby achieving dehumidifying and heating the vehicle cabin.

[0366] (A3) Heating mode In the heating mode, the control device 60 fully closes the cooling expansion valve 14b and throttles the cooling expansion valve 14c.

[0367] Therefore, in the heat pump cycle 10a in the heating mode, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the water-refrigerant heat exchanger 12, the receiver 23, the cooling expansion valve 14c, the chiller 20, and the suction port of the compressor 11 in that order.

[0368] 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 manner as in the heating mode of the first embodiment. Furthermore, the control device 60 controls the throttle opening of the cooling expansion valve 14c so that the superheat degree SH of the outlet side refrigerant of the chiller 20 approaches a predetermined reference superheat degree KSH.

[0369] The controller 60 also controls the operation of the high-temperature side pump 41 so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium temperature TWH approaches the target high-temperature side heat medium temperature TWHO.

[0370] Therefore, in the dehumidifying and heating mode, the high temperature side heat medium circuit 40a is switched to a circuit in which the high temperature side heat medium circulates in the same order as in the cooling mode.

[0371] Here, in the heating mode, the amount of heat exchange between the high-temperature side heat medium and the blown air increases in the heater core 42. Therefore, in the heating mode, the high-temperature side three-way valve 43 allows almost the entire flow rate of the high-temperature side heat medium flowing out from the heat medium passage 12b of the water-refrigerant heat exchanger 12 to flow to the heater core 42 side.

[0372] Moreover, the controller 60 controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity. Similarly to the dehumidifying and heating mode, the controller 60 controls the operation of the first low-temperature side three-way valve 52a to the third low-temperature side three-way valve 52c.

[0373] Therefore, in the heating mode, the low-temperature side heat medium circuit 50a is switched to a circuit in which the low-temperature side heat medium circulates in the same order as in the dehumidification heating mode. The other operations are the same as in the heating mode described in the first embodiment.

[0374] Therefore, in the heat pump cycle 10a in the 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 the heating mode, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12. Furthermore, in the chiller 20, the low-pressure refrigerant absorbs heat from the low-temperature side heat medium, and the temperature of the low-temperature side heat medium becomes lower than the outside air temperature.

[0375] In the high-temperature side heat medium circuit 40a in the heating mode, the heat medium heated in the water-refrigerant heat exchanger 12 is supplied to the heater core 42 in accordance with the flow rate ratio control of the high-temperature side three-way valve 43.

[0376] In the low-temperature side heat medium circuit 50a in the heating mode, the low-temperature side heat medium cooled in 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 that flows into the low-temperature side radiator 56 absorbs heat from the outside air. The low-temperature side heat medium that flows out of the low-temperature side radiator 56 is sucked into the first low-temperature side pump 51a and pumped to the heat medium passage 20b of the chiller 20.

[0377] In the interior air conditioning unit 30 in the heating mode, the air blown from the interior blower 32 passes through the interior evaporator 18. The temperature of the air that has passed through the interior evaporator 18 is adjusted to approach the target blowing temperature TAO by adjusting the opening degree of the air mix door 34. The temperature-adjusted air is then blown into the vehicle interior, thereby heating the vehicle interior.

[0378] Next, the operation modes for temperature adjustment will be described. In this embodiment, the operation modes for the battery include (B1) a battery equalizing temperature mode and (B2) a battery cooling mode. In addition, the operation mode for the high-power equipment includes (C1) a high-power equipment cooling mode. The detailed operation of each operation mode for temperature adjustment will be described below.

[0379] (B1) Battery temperature equalization mode The battery cooling mode is executed when the temperature difference ΔTB between each battery cell is equal to or greater than the target cell temperature difference ΔKTB.

[0380] In the battery equalizing temperature mode, the control device 60 controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity. The control device 60 controls the operation of the first low-temperature side three-way valve 52a so as to cause the low-temperature side heat medium flowing out from the heat medium passage 20b of the chiller 20 to flow to the third low-temperature side three-way valve 52c side. The control device 60 also controls the operation of the third low-temperature side three-way valve 52c so as to cause the low-temperature side heat medium flowing out from the first low-temperature side three-way valve 52a to flow to the cooling water passage 80a side of the battery 80.

[0381] For this reason, in the low-temperature side heat medium circuit 50a in the battery equalization mode, the low-temperature side heat medium pumped by the first low-temperature side pump 51a is switched to a circuit in which it circulates, in the order of heat medium passage 20b of the chiller 20, first low-temperature side three-way valve 52a, third low-temperature side three-way valve 52c, cooling water passage 80a of the battery 80, and the suction port of the first low-temperature side pump 51a.

[0382] Therefore, in the low-temperature side heat medium circuit 50a in the battery equalization mode, the temperature of each battery cell that constitutes the battery 80 is equalized when the low-temperature side heat medium pumped by the first low-temperature side pump 51a flows through the coolant passage 80a of the battery 80.

[0383] (B2) Battery Cooling Mode The battery cooling mode is executed when the battery temperature TB becomes equal to or higher than a predetermined reference cooling temperature KTBH. The battery cooling mode is an operation mode in which the battery 80 is cooled by the low-temperature side heat medium cooled by the chiller 20. Therefore, when the compressor 11 of the heat pump cycle 10 is operating, such as during air conditioning, the control device 60 throttles the cooling expansion valve 14c of the heat pump cycle 10 even in the cooling mode.

[0384] Therefore, in the heat pump cycle 10a in the battery cooling mode, the low-pressure refrigerant decompressed 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 sucked into the compressor 11 via the sixth refrigerant joint portion 13f.

[0385] Furthermore, the control device 60 appropriately controls the operation of other devices to be controlled. For example, the control device 60 controls the cooling expansion valve 14c in the same manner as in the dehumidifying and heating mode.

[0386] The controller 60 also controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the first low-temperature side three-way valve 52a so as to cause the low-temperature side heat medium flowing out of the heat medium passage 20b of the chiller 20 to flow to the third low-temperature side three-way valve 52c. The controller 60 also controls the operation of the third low-temperature side three-way valve 52c so that the first low-temperature side heat medium temperature TWL1 approaches the battery target temperature TWLO1.

[0387] Therefore, in the low-temperature side heat medium circuit 50a in the dehumidifying heating mode, the low-temperature side heat medium pumped by the first low-temperature side pump 51a is switched to a circuit in which the low-temperature side heat medium pumped 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 in this order. At the same time, the low-temperature side heat medium pumped by the first low-temperature side pump 51a is switched to a circuit in which the low-temperature side heat medium pumped 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 in this order. In other words, the circuit is switched to one in which the cooling water passage 80a of the battery 80 and the low-temperature side radiator 56 are connected in parallel with respect to the flow of the low-temperature side heat medium.

[0388] Therefore, in the heat pump cycle 10a in the battery cooling mode during 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.

[0389] In the low-temperature side heat medium circuit 50a, the low-temperature side heat medium cooled by the chiller 20 flows into both the coolant passage 80a of the battery 80 and the low-temperature side radiator 56 in accordance with the flow rate ratio control of the first low-temperature side three-way valve 52a. The low-temperature side heat medium that flows into the coolant passage 80a of the battery 80 absorbs heat from the battery 80. As a result, the battery 80 is cooled.

[0390] Next, the battery cooling mode during non-air conditioning will be described. In the battery cooling mode during non-air conditioning, the control device 60 fully closes the cooling expansion valve 14b and throttles the cooling expansion valve 14c.

[0391] Therefore, in the heat pump cycle 10a in the battery cooling mode during non-air conditioning, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which it circulates through the water-refrigerant heat exchanger 12, the receiver 23, the cooling expansion valve 14c, the chiller 20, and the suction port of the compressor 11 in that order.

[0392] Furthermore, the control device 60 appropriately controls the operation of other controlled devices. For example, the control device 60 controls the rotation speed of the compressor 11 so as to achieve a predetermined discharge capacity. The control device 60 also controls the throttle opening of the cooling expansion valve 14c so that the first low-temperature side heat medium temperature TWL1 approaches the battery target temperature TWLO1.

[0393] The controller 60 also controls the operation of the high-temperature side pump 41 so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the high-temperature side three-way valve 43 so as to cause the high-temperature side heat medium that has flowed in from the heat medium passage 12b of the water-refrigerant heat exchanger 12 to flow out to the high-temperature side radiator 44 side.

[0394] For this reason, in the high-temperature side heat medium circuit 40a in the battery cooling mode during non-air conditioning, the high-temperature side heat medium pumped from the high-temperature side pump 41 is switched to a circuit in which it circulates 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, in that order.

[0395] The controller 60 also controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the first low-temperature side three-way valve 52a and the third low-temperature side three-way valve 52c in the same manner as in the battery cooling mode during air conditioning.

[0396] Therefore, in the low-temperature side heat medium circuit 50a in the battery cooling mode during non-air conditioning, the low-temperature side heat medium pumped by the first low-temperature side pump 51a is switched to a circuit in which it circulates in the same way as in the battery cooling mode during air conditioning.

[0397] Therefore, in the heat pump cycle 10a in the battery cooling mode during non-air conditioning, 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 the battery cooling mode during non-air conditioning, the high-temperature side heat medium is heated in the water-refrigerant heat exchanger 12. Furthermore, the low-pressure side heat medium is cooled in the chiller 20.

[0398] In addition, in the high-temperature side heat medium circuit 40a, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12 is pressure-fed to the high-temperature side radiator 44 via the high-temperature side three-way valve 43. The high-temperature side heat medium that has flowed into the high-temperature side radiator 44 dissipates heat to the outside air and is cooled.

[0399] In the low-temperature side heat medium circuit 50a, similarly to the battery cooling mode during air conditioning, the low-temperature side heat medium cooled by the chiller 20 flows into the coolant passage 80a of the battery 80. The low-temperature side heat medium that has flowed into the coolant passage 80a of the battery 80 absorbs heat from the battery 80. As a result, the battery 80 is cooled.

[0400] (C1) High-power equipment cooling mode The high power equipment cooling mode is executed when the second low-temperature side heat medium temperature TWL2 becomes equal to or higher than a predetermined reference high power equipment cooling temperature KTWL2. The high power equipment cooling mode is an operation 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.

[0401] In the high power equipment cooling mode, the control device 60 controls the operation of the second low-temperature side pump 51b so as to exert a predetermined pumping capacity. The control device 60 also controls the operation of the second low-temperature side three-way valve 52b so that the second low-temperature side heat medium temperature TWL2 approaches the high power equipment target temperature TWLO2.

[0402] Therefore, in the low-temperature side heat medium circuit 50a in the high-power device cooling mode, the low-temperature side heat medium pumped by the second low-temperature side pump 51b is switched to a circuit in which it circulates through the cooling water passage 81a of the high-power device 81, the second low-temperature side three-way valve 52b, the high-power device bypass passage 55b, and the suction port of the second low-temperature side pump 51b in this order. At the same time, the low-temperature side heat medium pumped by the second low-temperature side pump 51b is switched to a circuit in which it circulates through the cooling water passage 81a of the high-power device 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 in this order. In other words, the high-power device bypass passage 55b and the low-temperature side radiator 56 are switched to a circuit in which they are connected in parallel with respect to the flow of the low-temperature side heat medium.

[0403] Therefore, in the low-temperature side heat medium circuit 50a in the high electric equipment cooling mode, at least a portion of the low-temperature side heat medium pumped from the second low-temperature side pump 51b flows into the low-temperature side radiator 56. The low-temperature side heat medium that flows into the low-temperature side radiator 56 is cooled by heat exchange with the outside air. The low-temperature side heat medium that flows out of the low-temperature side radiator 56 joins and is mixed with the low-temperature side heat medium that has flowed through the high electric equipment bypass passage 55b at the twelfth heat medium joint portion 53m.

[0404] At this time, the temperature of the low-temperature side heat medium mixed at the twelfth heat medium joint 53m approaches the target temperature TWLO2 for the high-power equipment by controlling the flow rate ratio of the second low-temperature side three-way valve 52b. The low-temperature side heat medium mixed at the twelfth heat medium joint 53m is sucked into the second low-temperature side pump 51b. The low-temperature side heat medium pumped from the second low-temperature side pump 51b flows into the cooling water passage 81a of the high-power equipment 81. As a result, the high-power equipment 81 is cooled.

[0405] As described above, according to the air conditioning device 1a of this embodiment, by appropriately combining and executing the air conditioning operation mode and the temperature adjustment operation mode, it is possible to perform comfortable air conditioning in the vehicle cabin and appropriate temperature adjustment of multiple on-board devices.

[0406] Furthermore, in the air conditioner 1a of this embodiment, like the first embodiment, heating preparation control can be executed.

[0407] Specifically, in step S2 of the heating preparation control in this embodiment, in order to execute the heating preparation control, the controller 60 puts the cooling expansion valve 14b in a fully closed state and the cooling expansion valve 14c in a throttled state.

[0408] Therefore, in the heat pump cycle 10a under heating preparation control, as shown by the dashed arrow in Figure 12, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in the following order: water-refrigerant heat exchanger 12, receiver 23, cooling expansion valve 14c, chiller 20, and the suction port of the compressor 11.

[0409] The controller 60 also controls the operation of the high-temperature side pump 41 so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the high-temperature side three-way valve 43 so as to cause the high-temperature side heat medium flowing out of the heat medium passage 12b of the water-refrigerant heat exchanger 12 to flow to the heater core 42 side.

[0410] Therefore, in the high-temperature side heat medium circuit 40a during heating preparation control, as shown by the solid arrows in FIG. 12, the high-temperature side heat medium pumped by the high-temperature side pump 41 circulates through the heat medium passage 12b of the water-refrigerant heat exchanger 12, the heater core 42, and the suction port of the high-temperature side pump 41 in that order.

[0411] The controller 60 also controls the operation of the first low-temperature side pump 51a so as to exert a predetermined pumping capacity. The controller 60 also controls the operation of the first low-temperature side three-way valve 52a so as to cause the low-temperature side heat medium flowing out of the heat medium passage 20b of the chiller 20 to flow into the cooling water passage 80a of the battery 80.

[0412] For this reason, in the low-temperature side heat medium circuit 50a in heating preparation control, the low-temperature side heat medium pumped by the first low-temperature side pump 51a circulates through the heat medium passage 20b of the chiller 20, the electric heater 54, and the suction port of the first low-temperature side pump 51a in that order, as shown by the solid arrows in Fig. 12. In other words, in the low-temperature side heat medium circuit 50a in heating preparation control, the low-temperature side heat medium heated by the electric heater 54 is switched to a circuit that bypasses the coolant passage 80a of the battery 80.

[0413] Other operations of the heating preparation control are the same as those of the first embodiment. Therefore, the heating preparation control of the air conditioner 1a of this embodiment can also provide the same effects as those of the first embodiment. That is, the heat generated by the electric heater 54 can be used to quickly increase the heating capacity of the heating unit. As a result, air conditioning with immediate effect and high responsiveness can be achieved.

[0414] Fifth embodiment In this embodiment, an example will be described in which an inlet side connecting passage 91a, an outlet side connecting passage 92a, etc. are added to the air conditioner 1a of the fourth embodiment, as shown in the overall configuration diagram of Fig. 13. The inlet side connecting passage 91a and the outlet side connecting 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.

[0415] Furthermore, in the high-temperature side heat medium circuit 40a of the present embodiment, a high-temperature side four-way valve 43a is arranged instead of the 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 thereinto 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.

[0416] The high-temperature side four-way valve 43a can adjust the flow rate ratio of the high-temperature side heat medium flowing out to the heater core 42 side, the high-temperature side heat medium flowing out to the high-temperature side radiator 44 side, and the high-temperature side heat medium flowing out to the inlet side connecting passage 91a side. Furthermore, by adjusting the flow rate ratio, the high-temperature side four-way valve 43a can cause the total flow rate of the high-temperature side heat medium flowing inside to flow out to one of the heater core 42 side, the high-temperature side radiator 44 side, and the inlet side connecting passage 91a side.

[0417] That is, the high-temperature side four-way valve 43a serves as a heat medium circuit switching unit. The operation of the high-temperature side four-way valve 43a is controlled by a control signal output from the control device 60.

[0418] Furthermore, in the high temperature side heat medium circuit 40a, a first four-way joint 53q is arranged in place of the eighth heat medium joint 53h. The first four-way joint 53q is a four-way joint having four inlet and outlet ports that communicate with each other. As the first four-way joint 53q, a joint member formed in the same manner as the first refrigerant joint 13a, etc. can be used.

[0419] The low-temperature side heat medium circuit 50a of the present embodiment is further provided with a fourteenth heat medium joint 53p. The fourteenth heat medium joint 53p is disposed in a heat medium flow path extending from the outlet of the third low-temperature side three-way valve 52c to the inlet of the coolant passage 80a of the battery 80.

[0420] Furthermore, in the low-temperature side heat medium circuit 50a, a second four-way joint 53r is arranged in place of the eleventh heat medium joint 53k. The basic configuration of the second four-way joint 53r is similar to that of the first four-way joint 53q.

[0421] An inlet portion of the inlet side connection passage 91a is connected to one outlet of the high temperature side four-way valve 43a. An outlet portion of the inlet side connection passage 91a is connected to one inlet of the fourteenth heat medium joint portion 53p. An inlet portion of the outlet side connection passage 92a is connected to one outlet of the second four-way joint portion 53r. An outlet portion of the outlet side connection passage 92a is connected to one inlet of the first four-way joint portion 53q. The rest of the configuration of the air conditioner 1a is the same as that of the fourth embodiment.

[0422] Next, the operation of the air conditioner 1a of this embodiment in the above configuration will be described. In the air conditioner 1a of this embodiment, during normal operation, the control device 60 controls the operation of the high-temperature side four-way valve 43a so that the high-temperature side heat medium circuit 40a becomes the same circuit as in the fourth embodiment. Therefore, during normal operation, the high-temperature side heat medium does not flow out from the high-temperature side four-way valve 43a to the inlet side connection passage 91a.

[0423] Therefore, in the air conditioner 1a of this embodiment, the air conditioning operation mode and the temperature adjustment operation mode are appropriately combined and executed, thereby making it possible to perform comfortable air conditioning in the vehicle cabin and appropriate temperature adjustment of a plurality of in-vehicle devices. Furthermore, as in the fourth embodiment, the heating capacity of the heating unit can be quickly increased by performing the heating preparation control. As a result, it is possible to realize air conditioning with immediate effect and high responsiveness.

[0424] In addition, in this embodiment, when the heating preparation control is being executed and the battery temperature TB is equal to or lower than a 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 of the heat medium passage 12b of the water-refrigerant heat exchanger 12 flows to both the heater core 42 side and the inlet side connecting passage 91a side.

[0425] For this reason, in the air conditioner 1 of this embodiment, when the battery 80 needs to be warmed up during the execution of the heating preparation control, as shown by the solid arrow in Fig. 13, the high-temperature side heat medium pumped from the high-temperature side pump 41 is switched to a circuit in which it circulates 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 in that order. At the same time, the high-temperature side heat medium pumped from the high-temperature side pump 41 is switched to a circuit in which it circulates through the heat medium passage 12b of the water-refrigerant heat exchanger 12, the high-temperature side four-way valve 43a, the inlet side connecting passage 91a, the cooling water passage 80a of the battery 80, the outlet side connecting passage 92a, and the suction port of the high-temperature side pump 41 in that order. In other words, the heater core 42 and the cooling water passage 80a of the battery 80 are switched to a circuit in which they are connected in parallel with respect to the flow of the high-temperature side heat medium.

[0426] According to this, when the compressor 11 is operated in step S5 of the heating preparation control described in the first embodiment, the high-temperature side heat medium can be heated in the water-refrigerant heat exchanger 12. Then, at least a part of the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12 can be caused to flow into the cooling water passage 80a of the battery 80 via the high-temperature side four-way valve 43a and the inlet side connecting passage 91a. This allows the battery 80 to be warmed up.

[0427] The high-temperature side heat medium flowing out from the coolant passage 80a of the battery 80 is sucked into the high-temperature side pump 41 via the outlet side connecting passage 92a.

[0428] Other operations are the same as those in the first embodiment. Therefore, according to the air conditioner 1a of the present embodiment, the battery 80 can be warmed up during the execution of the heating preparation control.

[0429] (Other embodiments) The present invention is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit of the present invention.

[0430] (1) In the above-described embodiment, an example was described in which the air conditioner 1, 1a according to the present invention was applied to an electric vehicle, but the application of the air conditioner 1 is not limited to this. For example, the air conditioner 1 may be applied to a hybrid vehicle that obtains driving force for traveling from an electric motor and an internal combustion engine (i.e., an engine), or further to a plug-in hybrid vehicle that can charge a battery with electric power supplied from an external power source when the vehicle is stopped.

[0431] The present invention may also be applied to a stationary air conditioner with a temperature adjustment function that adjusts the temperature of an object to be adjusted (for example, a computer, a computer server device, or other electrical equipment) while performing indoor air conditioning.

[0432] In the above embodiment, an example has been described in which an inverter and a motor generator are adopted as the strong electric device 81, but the strong electric device 81 is not limited to this. For example, a charging device, a power control unit (a so-called PCU), a transaxle, a control device for ADAS, or the like may be adopted as the strong electric device 81.

[0433] The charging device is an on-board charger that charges the battery 80 with regenerative power, etc. The power control unit is a power control device that performs power transformation and power distribution. The transaxle is a power transmission mechanism that integrates the transmission, differential gear, etc. The control device for ADAS is a control device for advanced driver assistance systems. When applied to a stationary air conditioner, it may be configured to cool other heat-generating equipment.

[0434] (2) The configurations of the heat pump cycles 10, 10a are not limited to those disclosed in the above-described embodiments.

[0435] For example, in the above-described embodiment, an example was described in which the third check valve 17c, which has a relatively small refrigerant passage cross-sectional area, is used as the indoor unit outlet side opening and closing portion, but the indoor unit outlet side opening and closing portion may also be formed by combining an evaporation pressure regulating valve and a normal check valve.

[0436] The evaporation pressure regulating valve is a variable throttle mechanism that changes the valve opening so as to maintain the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined set pressure in order to suppress frost formation on the indoor evaporator 18. As the evaporation pressure regulating valve, a mechanical mechanism that increases the valve opening as the flow rate of the refrigerant circulating inside increases can be used.

[0437] In the second embodiment, the water-refrigerant heat exchanger 12 and the receiver 23 are used, but the present invention is not limited to this. For example, a so-called subcooling type heat exchanger may be used, which has a condensing section that condenses the refrigerant, a liquid receiving section that separates the refrigerant condensed in the condensing section into gas and liquid and stores the liquid-phase refrigerant, and a supercooling section that supercools the liquid-phase refrigerant flowing out from the liquid receiving section.

[0438] Furthermore, within the scope in which the above-mentioned effects can be obtained, a plurality of components may be integrated or separated. For example, the fourth refrigerant joint portion 13d and the sixth refrigerant joint portion 13f may be integrated in the same manner as the first four-way joint portion 53q.

[0439] In the above embodiment, the refrigerant is R1234yf, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be used. Alternatively, a mixed refrigerant made by mixing a plurality of these refrigerants may be used. Furthermore, carbon dioxide may be used as the refrigerant to configure a supercritical refrigeration cycle in which the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant.

[0440] (3) The configurations of the high-temperature side heat medium circuits 40, 40a and the low-temperature side heat medium circuits 50, 50a are not limited to those disclosed in the above-described embodiment.

[0441] For example, in the above embodiment, a PTC heater is used as the electric heater 54, which is the heat generating unit, but the present invention is not limited to this. For example, a nichrome wire or a carbon fiber heater may be used. Furthermore, a high-power electric device may be used as the heat generating unit. For example, a control device for ADAS may be used as the heat generating unit, and the amount of heat generated may be adjusted by performing an inefficient operation.

[0442] Furthermore, within the scope in which the above-mentioned effects can be obtained, a plurality of components may 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 heat medium joint section 53a of the first to third embodiments may be integrated into a five-way valve having five heat medium inlet / outlets. Furthermore, the first four-way joint section 53q and the second four-way joint section 53r may be formed by combining two three-way joints.

[0443] In the above embodiment, an example in which an ethylene glycol aqueous solution is used as the high-temperature side heat medium and the low-temperature side heat medium is described, but the present invention is not limited to this. For the high-temperature side heat medium circuit 40, 40a, a solution containing dimethylpolysiloxane or nanofluid, an antifreeze, an aqueous liquid refrigerant containing alcohol, a liquid medium containing oil, etc. may be used.

[0444] (4) The operation of the air conditioners 1, 1a is not limited to the above-mentioned operation modes. The air conditioners 1, 1a may be configured to be able to execute other operation modes. If the air conditioners 1, 1a have at least an operation mode in which the blown air is heated by the heating unit, the effect of quickly increasing the heating capacity of the heating unit by the heating preparation control described above can be obtained.

[0445] In addition, in step S2 of the heating preparation control described above, an example in which the compressor 11 is stopped has been described, but the present invention is not limited to this. For example, the reference discharge capacity for the heating preparation control may be the lower limit of the range in which the rotation speed (refrigerant discharge capacity) of the compressor 11 expected during normal operation can take, or a value lower than the lower limit.

[0446] In addition, in step S2 of the heating preparation control described above, an example in which the indoor blower 32 is stopped has been described, but the present invention is not limited to this. For example, the reference blowing capacity for the heating preparation control may be the lower limit of the range of the rotation speed (blowing capacity) of the indoor blower 32 expected during normal operation, or a value lower than the lower limit. [Explanation of symbols]

[0447] 10, 10a Heat pump cycle 11 Compressor 12 Water-refrigerant heat exchanger (heating section) 121 Indoor condenser (heating section) 20 Chiller (low temperature water-refrigerant heat exchanger) 20b Heat medium passage 32 Indoor fan (fan) 40, 40a High temperature side heat medium circuit (heating section) 50, 50a Low temperature side heat medium circuit (heat medium circuit) 54 Electric heater (heat generating part)

Claims

1. a heat pump cycle (10, 10a) including a compressor (11) that compresses and discharges a refrigerant, a heating section (12, 40, 121) that uses the high-pressure refrigerant discharged from the compressor as a heat source to heat air to be blown to a space to be air-conditioned, and a low-temperature side water-refrigerant heat exchanger (20) that causes a low-pressure refrigerant to absorb heat possessed by a heat medium; A heat medium circuit (50, 50a) for circulating the heat medium; A blower (32) that blows the blown air toward the air-conditioned space, a heat medium passage (20b) of the low-temperature side water-refrigerant heat exchanger and a heat generating section (54) that heats the heat medium flowing into the heat medium passage are arranged in the heat medium circuit; When the heating capacity (TWH, PR2) of the heating unit is improved by using heat generated by the heat generation unit, heating preparation control is performed to keep the refrigerant discharge capacity of the compressor at or below a predetermined reference discharge capacity and to keep the air blowing capacity of the blower at or below a predetermined reference air blowing capacity until an inlet heat medium temperature (TWin) of the heat medium flowing into the heat medium passage becomes equal to or higher than a target heat medium temperature (TWinO).

2. 2. The air conditioner according to claim 1, wherein in the heating preparation control, when the inlet side heat medium temperature becomes equal to or higher than the target heat medium temperature, the refrigerant discharge capacity of the compressor is increased.

3. 3. The air conditioning device according to claim 2, wherein, in the heating preparation control, when the inlet heat medium temperature becomes equal to or higher than the target heat medium temperature and the heating capacity of the blown air in the heating section becomes equal to or higher than a predetermined reference heating capacity (TWHO, PDO), the blowing capacity of the blower is increased.

4. 4. The air conditioner according to claim 1, wherein the heating preparation control is executed when a value obtained by subtracting an actual heating capacity of the heating unit from a reference heating capacity of the heating unit is equal to or greater than a predetermined reference value.

5. The heat pump cycle includes an indoor evaporator (18) for exchanging heat between the low-pressure refrigerant and the blown air, an indoor unit inlet side opening / closing unit (141b) for opening and closing a refrigerant inlet side of the indoor evaporator, and an indoor unit outlet side opening / closing unit (17c) for opening and closing a 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, 5. The air conditioning apparatus according to claim 1, wherein the indoor unit inlet side opening / closing unit and the indoor unit outlet side opening / closing unit are configured to be capable of closing the refrigerant inlet side and the refrigerant outlet side of the indoor evaporator when the heating preparation control is executed.

6. In the heat medium circuit, a cooling water passage (80a) for a battery (80) and a heat medium circuit switching unit (52a to 52c) for switching a circuit configuration are arranged, 6. The air conditioner according to claim 1, wherein the heat medium circuit switching unit switches the heat medium to a circuit that bypasses the coolant passage when the heating preparation control is executed.

7. A target heat medium temperature determination unit (S3) for determining the target heat medium temperature, 7. The air conditioner according to claim 1, wherein the target heat medium temperature determination unit determines the target heat medium temperature to be increased as the temperature of the blown air flowing into the heating unit decreases.

8. A target heat medium temperature determination unit (S3) for determining the target heat medium temperature; A target blowing capacity determination unit (60b) that determines a target blowing capacity of the blower, 8. The air conditioner according to claim 1, wherein the target heat medium temperature determination unit determines the target heat medium temperature to be increased as the target air blowing capacity increases.

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