air conditioning unit

Abstract

The air conditioning unit (1) includes a heat pump cycle (10), a heating unit (20), a low-temperature side heat medium circuit (30), and a heat dissipation regulation and control unit (50a). The heat pump cycle includes a compressor (11), a condenser (12), a pressure reducing unit (14b), and an evaporator (16). The heating unit includes a heating heat exchanger (13, 23), an outdoor air radiator (22), and a heat dissipation regulation unit (25). The low-temperature side heat medium circuit includes a heating device (31). The heat dissipation regulation and control unit regulates the heat dissipation in the outdoor air radiator so that the temperature of the supply air heated by the heating heat exchanger is close to the predetermined target temperature (TAO).

Description

[0001] This application is a divisional application of the following application:

[0002] The original application was filed on March 12, 2020.

[0003] The original application number was 202080025226.0

[0004] Original invention title: Air conditioning device

[0005] Cross-reference of related applications

[0006] This application is based on Japanese Patent Application No. 2019-67628, filed on March 29, 2019, and Japanese Patent Application No. 2020-32898, filed on February 28, 2020, the contents of which are incorporated herein by reference. Technical Field

[0007] This invention relates to air conditioning devices. Background Technology

[0008] Previously, the technology described in Patent Document 1 was known as a technology related to air conditioning devices. The vehicle air conditioning device described in Patent Document 1 is configured to have a cooling circuit, a low-temperature circuit, and a high-temperature circuit, and is capable of performing cooling and heating of the vehicle interior. In the low-temperature circuit of Patent Document 1, a drive unit (motor, inverter) and a battery are configured, and the drive unit and battery are cooled using the cooling water of the low-temperature circuit.

[0009] Furthermore, the vehicle air conditioning unit of Patent Document 1 utilizes a refrigeration circuit to extract waste heat absorbed during the cooling of drive equipment and the like in a low-temperature circuit, and then uses this heat, via a heater core in a high-temperature circuit, to heat the vehicle interior, which is the target space for air conditioning. In other words, the vehicle air conditioning unit of Patent Document 1 achieves energy saving when heating the target space for air conditioning by utilizing waste heat from drive equipment and the like.

[0010] Existing technical documents

[0011] Patent documents

[0012] Patent Document 1: Japanese Patent Application Publication No. 2015-186989

[0013] However, in the structure of Patent Document 1, the drive unit and battery are incidentally heat-generating components, so the amount of waste heat from the equipment fluctuates constantly depending on the equipment's operating status. Furthermore, in the structure of Patent Document 1, the waste heat is drawn from the low-temperature water circuit via the refrigeration circuit and then used to heat the supply air in the heater core of the high-temperature water circuit. In other words, it is conceivable that fluctuations in the amount of waste heat would become a major cause of temperature fluctuations in the supply air during heating, reducing the comfort of the conditioned space. Summary of the Invention

[0014] The present invention was made in view of these problems, and its object is to provide an air conditioning device that, when using waste heat from equipment for heating, can suppress the influence of the heat generated by the heat-generating equipment and ensure the comfort of the air-conditioned space.

[0015] The air conditioning device according to the first aspect of the present invention includes a heat pump cycle, a heating unit, a low-temperature side heat medium circuit, and a heat dissipation regulation and control unit. The heat pump cycle includes a compressor, a condenser, a pressure reducing unit, and an evaporator.

[0016] The compressor compresses and discharges the refrigerant. The condenser condenses the high-pressure refrigerant compressed by the compressor through heat exchange. The pressure reducing section reduces the pressure of the refrigerant flowing out of the condenser. The evaporator allows the low-pressure refrigerant, after being reduced in pressure by the pressure reducing section, to exchange heat with the low-temperature heat medium on the low-temperature side, causing the refrigerant to evaporate.

[0017] The heating unit includes a heat exchanger for heating, an outdoor air radiator, and a heat dissipation regulating unit. The heat exchanger uses the heat from the high-pressure refrigerant as a heat source to heat the supplied air blown into the air-conditioned space. The outdoor air radiator dissipates the heat from the high-pressure refrigerant to the outdoor air. The heat dissipation regulating unit adjusts the amount of heat dissipated from the high-pressure refrigerant to the outdoor air by the outdoor air radiator.

[0018] The low-temperature side heat medium circuit is configured to circulate a low-temperature side heat medium that absorbs heat through heat exchange in the evaporator. Furthermore, the low-temperature side heat medium circuit includes a heating device configured to cool through heat exchange with the low-temperature side heat medium. Additionally, a heat dissipation regulation and control unit controls the operation of the heat dissipation regulation unit.

[0019] Furthermore, the heat dissipation regulation and control unit uses the heat dissipation regulation unit to adjust the heat dissipation in the outdoor air radiator so that the temperature of the supply air heated by the heating heat exchanger is close to the predetermined target temperature.

[0020] Therefore, by coordinating the operation of the heat pump cycle, the heating unit, and the low-temperature side heat medium circuit, the heat-generating equipment can be cooled via the low-temperature side heat medium, and the waste heat from the heat-generating equipment can be extracted through the heat pump cycle and used to heat the supply air in the heating unit. In other words, the air conditioning unit can simultaneously cool the heat-generating equipment and regulate the air in the air-conditioned space by utilizing the waste heat from the heat-generating equipment.

[0021] Furthermore, by adjusting the heat dissipation in the outdoor air radiator using the heat dissipation regulating unit, the heat possessed by the high-pressure refrigerant dissipating heat to the supply air in the heating heat exchanger can be adjusted. Therefore, by adjusting the heat dissipation in the outdoor air radiator using the heat dissipation regulating unit, the influence of the heat generated by the heating equipment on the temperature of the supply air supplied to the air-conditioned space can be adjusted, so that the supply air temperature is close to a predetermined target temperature. In other words, when the air conditioning unit is used to condition the air in an air-conditioned space that utilizes the waste heat of the heating equipment, the comfort of the air-conditioned space can be improved regardless of the heat generated by the heating equipment.

[0022] Furthermore, the air conditioning device according to the second aspect of the present invention includes a heat pump cycle, a heating unit, a low-temperature side heat medium circuit, and a heat exchange rate regulation and control unit. The heat pump cycle includes a compressor, a condenser, a pressure reducing unit, and an evaporator.

[0023] The compressor compresses and discharges the refrigerant. The condenser condenses the high-pressure refrigerant compressed by the compressor through heat exchange. The pressure reducing section reduces the pressure of the refrigerant flowing from the condenser. The evaporator evaporates the low-pressure refrigerant after pressure reduction by exchanging heat with a low-temperature heat medium. The heating section has a heating heat exchanger that uses the heat of the high-pressure refrigerant as a heat source to heat the supply air blown into the air-conditioned space.

[0024] The low-temperature side heat medium circuit is configured to circulate a low-temperature side heat medium that absorbs heat through heat exchange in the evaporator. Furthermore, the low-temperature side heat medium circuit includes a heating device, an outside air heat exchanger, and a heat exchange rate regulating unit. The heating device is configured to be cooled through heat exchange with the low-temperature side heat medium. The outside air heat exchanger allows heat exchange between the low-temperature side heat medium and the outside air. The heat exchange rate regulating unit regulates the heat exchange rate in the heating device and the outside air heat exchanger. Moreover, the heat exchange rate regulating control unit controls the operation of the heat exchange rate regulating unit.

[0025] Furthermore, the heat exchange quantity regulation and control unit regulates the heat exchange quantity in the outside air heat exchanger while maintaining the cooling capacity generated by the heat exchange between the heating device and the low-temperature side heat medium, so that the temperature of the supply air heated by the heating heat exchanger is close to the predetermined target temperature.

[0026] Therefore, by coordinating the operation of the heat pump cycle, the heating unit, and the low-temperature side heat medium circuit, the heat-generating equipment can be cooled via the low-temperature side heat medium, and the waste heat from the heat-generating equipment can be extracted through the heat pump cycle and used to heat the supply air in the heating unit. In other words, the air conditioning unit can simultaneously cool the heat-generating equipment and regulate the air in the air-conditioned space by utilizing the waste heat from the heat-generating equipment.

[0027] Furthermore, by using a heat exchange rate regulating unit to adjust the heat exchange rate in the outdoor air heat exchanger, the total amount of heat absorbed from the low-temperature side heat medium circuit can be regulated. Thus, the air conditioning unit can regulate the amount of heat possessed by the high-pressure refrigerant dissipating heat to the supply air in the heating heat exchanger.

[0028] Furthermore, while maintaining the cooling capacity generated by heat exchange between the heating device and the low-temperature heat medium, the heat exchange rate in the outdoor air heat exchanger is adjusted to bring the supply air temperature close to a predetermined target temperature. This allows for appropriate cooling of the heating device while simultaneously regulating the impact of the heating device's heat output on the temperature of the supply air supplied to the air-conditioned space. In other words, when the air conditioning unit conditions the air in an air-conditioned space utilizing the waste heat of the heating device, it can improve the comfort of the air-conditioned space regardless of the heating device's heat output.

[0029] Furthermore, the air conditioning device according to the third aspect of the present invention includes a heat pump cycle, a low-temperature side heat medium circuit, and an equipment cooling control unit. The heat pump cycle includes a compressor, a condenser, a pressure reducing unit, and an evaporator.

[0030] The compressor compresses and discharges the refrigerant. The condenser condenses the high-pressure refrigerant compressed by the compressor through heat exchange. The pressure reducing section reduces the pressure of the refrigerant flowing out of the condenser. The evaporator causes the low-pressure refrigerant, after being reduced in pressure by the pressure reducing section, to evaporate by exchanging heat with the low-temperature heat medium.

[0031] The low-temperature side heat medium circuit is configured to circulate a low-temperature side heat medium that absorbs heat through heat exchange in the evaporator. Furthermore, the low-temperature side heat medium circuit includes a heating device configured to be cooled through heat exchange with the low-temperature side heat medium.

[0032] The equipment cooling control unit performs controls related to the cooling of the heat-generating equipment. When cooling of the heat-generating equipment is initiated, the equipment cooling control unit starts the circulation of the low-temperature side heat medium through the evaporator in the low-temperature side heat medium circuit, and then starts the flow of refrigerant relative to the evaporator.

[0033] Therefore, in environments with extremely low ambient temperatures, when the heating element is cooled by the low-temperature side heat medium, causing the low-temperature side heat medium to absorb the waste heat from the heating element, the waste heat from the heating element can be used to heat the temperature of the low-temperature side heat medium. Furthermore, by starting the refrigeration cycle with the low-temperature side heat medium preheated, the refrigerant pressure on the low-pressure side of the refrigeration cycle can be increased to a certain extent beforehand. Thus, the use of an evaporator to cool the heating element in extremely low-temperature environments improves performance in the initial stages. Attached Figure Description

[0034] The above and other objects, features, and advantages of the present invention will become more apparent from the following detailed description with reference to the accompanying drawings. In the drawings,

[0035] Figure 1 This is an overall structural diagram of the air conditioning device according to the first embodiment.

[0036] Figure 2 This is an overall structural diagram of the indoor air conditioning unit involved in the first embodiment.

[0037] Figure 3 This is a block diagram illustrating the control system of the air conditioning device according to the first embodiment.

[0038] Figure 4 This is a flowchart of the control process related to heat dissipation adjustment and heating start-up in the first embodiment.

[0039] Figure 5 This is a flowchart of the control process related to the adjustment of heat dissipation in an air conditioning unit.

[0040] Figure 6 This is a flowchart of the control process related to the adjustment of the heating output of the electric heater in an air conditioning unit.

[0041] Figure 7 This is a flowchart of the control process related to the adjustment of heat dissipation in the low-temperature side heat medium circuit in the air conditioning device 1 of the second embodiment.

[0042] Figure 8 This is a flowchart of the control process related to the adjustment of heat exchange when the outside air temperature is lower than the battery temperature in the second embodiment.

[0043] Figure 9 This is a flowchart of the control process related to the adjustment of heat exchange volume when the outside air temperature is higher than the battery temperature in the second embodiment.

[0044] Figure 10 This is a flowchart of the control process related to the start of heat dissipation adjustment in the air conditioning device according to the third embodiment.

[0045] Figure 11 This is a flowchart of the control process related to the start of heating of the electric heater in the air conditioning device according to the third embodiment.

[0046] Figure 12 This is an overall structural diagram of the air conditioning device according to the fourth embodiment.

[0047] Figure 13 This is an overall structural diagram of the air conditioning device according to the fifth embodiment.

[0048] Figure 14 This is an overall structural diagram of the air conditioning device according to the sixth embodiment.

[0049] Figure 15 This is an overall structural diagram of the air conditioning device according to the seventh embodiment.

[0050] Figure 16 This is an overall structural diagram of the air conditioning device according to the eighth embodiment.

[0051] Figure 17 This is an overall structural diagram of the air conditioning device according to the ninth embodiment.

[0052] Figure 18 This is a flowchart of the control process related to the setting of the target temperature in the cooling and heating mode of the air conditioning device according to the tenth embodiment.

[0053] Figure 19 This is a flowchart of the control process related to the setting of the target temperature in the cooling and heating mode of the air conditioning device according to the eleventh embodiment.

[0054] Figure 20 This is an explanatory diagram showing an example of the internal volume of the cryogenic sensor side and the internal volume of the cryogenic device in the twelfth embodiment.

[0055] Figure 21 This is a perspective view showing the battery and battery heat exchanger in the twelfth embodiment.

[0056] Figure 22 This is an explanatory diagram showing an example of the internal volume of the cryogenic side device in the twelfth embodiment.

[0057] Figure 23 This is a flowchart of the control process for starting the cooling of the battery in the air conditioning device according to the thirteenth embodiment.

[0058] Figure 24 This is an explanatory diagram relating to the changes in the temperature of the low-temperature side heat medium and the refrigerant suction pressure at the start of battery cooling in the thirteenth embodiment.

[0059] Figure 25 This is an overall structural diagram of the air conditioning unit according to the fourteenth embodiment. Detailed Implementation

[0060] Hereinafter, various embodiments for carrying out the present invention will be described with reference to the accompanying drawings. In each embodiment, the same reference numerals are sometimes used to denote parts corresponding to matters described in previous embodiments, and repeated descriptions are omitted. Where only a part of the structure is described in each embodiment, other previously described embodiments can be applied to the other parts of the structure. Not only are the combinations of combinable parts specifically shown in each embodiment, but embodiments can also be partially combined with each other even if not explicitly shown, provided that the combination does not particularly hinder it.

[0061] (First Implementation)

[0062] First, refer to Figures 1 to 3 The first embodiment of the present invention will be described below. In the first embodiment, the air conditioning device 1 according to the present invention is applied to an electric vehicle air conditioning device that obtains driving force for vehicle driving from a driving motor. The air conditioning device 1 performs air conditioning in the vehicle interior, which is the space to be conditioned, and temperature regulation of the battery 31, which is a heat-generating device, in the electric vehicle.

[0063] Furthermore, the air conditioning unit 1 can switch between cooling mode, heating mode, and dehumidification / heating mode as the air conditioning operation modes for regulating the air inside the vehicle. Cooling mode is an operation mode that cools the air supplied to the vehicle interior before blowing it out. Heating mode is an operation mode that heats the air supplied to the vehicle interior before blowing it out. Dehumidification / heating mode is an operation mode that dehumidifies and heats the vehicle interior by reheating the cooled and dehumidified air supplied to the vehicle interior before blowing it out.

[0064] Furthermore, the air conditioning unit 1 can switch between providing cooling to the battery 31 regardless of the air conditioning operating mode. Therefore, the operating mode of the air conditioning unit 1 can be defined by a combination of the air conditioning operating mode and the presence or absence of cooling to the battery 31. Thus, the operating modes of the air conditioning unit 1 include seven modes: cooling mode, heating mode, dehumidifying heating mode, stand-alone cooling mode, cooling cooling mode, cooling heating mode, and cooling dehumidifying heating mode.

[0065] The standalone cooling mode is an operating mode that cools the battery 31 without adjusting the air conditioning inside the vehicle. The cooling and refrigeration mode is an operating mode that cools both the vehicle interior and the battery 31. The cooling and heating mode is an operating mode that heats both the vehicle interior and the battery 31. The cooling, dehumidifying, and heating mode is an operating mode that dehumidifies and heats both the vehicle interior and the battery 31.

[0066] Furthermore, in the heat pump cycle 10 of the air conditioning unit 1, an HFC refrigerant (specifically R134a) is used as the refrigerant, forming a subcritical refrigeration cycle where the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. Refrigeration oil for lubricating the compressor 11 is mixed into the refrigerant. PAG oil (polyalkylene glycol oil), which is miscible with the liquid refrigerant, is used as the refrigeration oil. A portion of the refrigeration oil circulates in the cycle along with the refrigerant.

[0067] Next, while referring to Figures 1-3 The specific structure of the air conditioning device 1 according to the first embodiment will be described. The air conditioning device 1 according to the first embodiment includes a heat pump cycle 10, a heating unit 20, a low-temperature side heat medium circuit 30, an indoor air conditioning unit 40, and a control device 50.

[0068] First, the components of the heat pump cycle 10 constituting the air conditioning unit 1 will be described. The heat pump cycle 10 is a vapor compression type refrigeration cycle device.

[0069] First, compressor 11 draws in refrigerant in heat pump cycle 10, compresses it, and then discharges it. Compressor 11 is located inside the vehicle's engine hood. Compressor 11 is an electric compressor that uses an electric motor to drive a fixed-capacity compression mechanism with a fixed discharge capacity. The speed (i.e., refrigerant discharge capacity) of compressor 11 is controlled according to a control signal output from control device 50 (described later).

[0070] Furthermore, the outlet of the compressor 11 is connected to the inlet side of the refrigerant passage 12a in the heat medium refrigerant heat exchanger 12. The heat medium refrigerant heat exchanger 12 is a heat exchanger that heats the high-pressure refrigerant discharged from the compressor 11 by dissipating heat from it to the high-temperature heat medium circulating in the high-temperature heat medium circuit 21 of the heating section 20.

[0071] The heat exchanger 12 has a refrigerant passage 12a through which the refrigerant of the heat pump cycle 10 flows and a heat medium passage 12b through which the high-temperature side heat medium of the high-temperature side heat medium circuit 21 flows. The heat exchanger 12 is formed of a homogeneous metal with excellent heat transfer properties (aluminum alloy in the first embodiment), and the constituent parts are integrated by brazing.

[0072] Therefore, the high-pressure refrigerant flowing in the refrigerant passage 12a and the high-temperature heat medium flowing in the heat medium passage 12b can exchange heat with each other. The heat medium refrigerant heat exchanger 12 is an example of a condenser that dissipates heat from the high-pressure refrigerant and constitutes part of the heating section 20 described later. Furthermore, the high-temperature heat medium flowing in the heat medium passage 12b can be a solution containing ethylene glycol, antifreeze, etc.

[0073] A refrigerant branch with a three-way connector is connected to the outlet of the refrigerant passage 12a of the heat medium refrigerant heat exchanger 12. The refrigerant branch branches the flow of liquid refrigerant flowing out of the heat medium refrigerant heat exchanger 12. In the refrigerant branch, one of the three inflow outlets is used as a refrigerant inlet, and the remaining two are used as refrigerant outlets.

[0074] The refrigerant outlet on one side of the refrigerant branch is connected to the refrigerant inlet side of the indoor evaporator 15 via a first expansion valve 14a. The refrigerant outlet on the other side of the refrigerant branch is connected to the refrigerant inlet side of the chiller 16 via a second expansion valve 14b.

[0075] The first expansion valve 14a is a pressure-reducing section that, at least in cooling mode, reduces the pressure of the refrigerant flowing out of the refrigerant outlet from one side of the refrigerant branch. The first expansion valve 14a is an electrically operated variable throttling mechanism, having a valve core and an electric actuator. That is, the first expansion valve 14a is constituted by a so-called electrically operated expansion valve.

[0076] The valve core of the first expansion valve 14a is configured to change the opening degree of the refrigerant passage (in other words, the throttling opening degree). The electric actuator has a stepper motor that changes the throttling opening degree of the valve core. The first expansion valve 14a is controlled to operate according to a control signal output from the control device 50.

[0077] Furthermore, the first expansion valve 14a is composed of a variable throttling mechanism, which has a fully open function that fully opens the refrigerant passage when the throttling opening is fully open, and a fully closed function that closes the refrigerant passage when the throttling opening is fully closed. In other words, the first expansion valve 14a can prevent the pressure reduction effect on the refrigerant from being exerted by fully opening the refrigerant passage.

[0078] Furthermore, the first expansion valve 14a can cut off the flow of refrigerant to the indoor evaporator 15 by closing the refrigerant passage. That is, the first expansion valve 14a functions as both a pressure-reducing section for reducing refrigerant pressure and a refrigerant circuit switching section for switching the refrigerant circuit.

[0079] The outlet of the first expansion valve 14a is connected to the refrigerant inlet side of the indoor evaporator 15. The indoor evaporator 15 is an evaporator that, at least in cooling mode, causes the low-pressure refrigerant, after being depressurized by the first expansion valve 14a, to exchange heat with the supply air, thereby evaporating the low-pressure refrigerant and cooling the supply air W.

[0080] like Figure 2 As shown, the indoor evaporator 15 is disposed within the housing 41 of the indoor air conditioning unit 40. That is, the indoor evaporator 15 is equivalent to an example of a refrigeration evaporator, and the first expansion valve 14a is equivalent to an example of a refrigeration pressure reducing unit.

[0081] like Figure 1 As shown, a second expansion valve 14b is connected to the refrigerant outlet on the other side of the refrigerant branch. The second expansion valve 14b is a pressure-reducing section that reduces the pressure of the refrigerant flowing out of the refrigerant outlet on the other side of the refrigerant branch, at least in heating mode.

[0082] The second expansion valve 14b, like the first expansion valve 14a, is an electrically operated variable throttling mechanism, having a valve core and an electric actuator. That is, the second expansion valve 14b is a so-called electrically operated expansion valve, having both fully open and fully closed functions.

[0083] In other words, the second expansion valve 14b can prevent the refrigerant from being depressurized by fully opening the refrigerant passage. Additionally, the second expansion valve 14b can cut off the flow of refrigerant to the chiller 16 by closing the refrigerant passage. That is, the second expansion valve 14b functions both as a pressure-reducing section for depressurizing the refrigerant and as a refrigerant circuit switching section for switching the refrigerant circuit.

[0084] The outlet of the second expansion valve 14b is connected to the refrigerant inlet side of the chiller 16. The chiller 16 is a heat exchanger that allows the low-pressure refrigerant, after being depressurized by the second expansion valve 14b, to exchange heat with the low-temperature heat medium circulating in the low-temperature heat medium circuit 30.

[0085] The chiller 16 has a refrigerant passage 16a and a heat medium passage 16b. The refrigerant passage 16a allows low-pressure refrigerant, after being depressurized by the second expansion valve 14b, to flow through it. The heat medium passage 16b allows low-temperature heat medium circulating in the low-temperature heat medium circuit 30 to flow through it. Therefore, the chiller 16 is an evaporator that absorbs heat from the low-pressure refrigerant by evaporating it through heat exchange between the low-pressure refrigerant flowing in the refrigerant passage 16a and the low-temperature heat medium flowing in the heat medium passage 16b. That is, the chiller 16 is equivalent to an example of an evaporator, and the second expansion valve 14b is equivalent to an example of a pressure-reducing unit.

[0086] like Figure 1As shown, an evaporation pressure regulating valve 17 is connected to the inlet side of the refrigerant outlet of the indoor evaporator 15. The evaporation pressure regulating valve 17 is an evaporation pressure regulating unit that maintains the refrigerant evaporation pressure in the indoor evaporator 15 above a predetermined reference pressure. The evaporation pressure regulating valve 17 is composed of a mechanical variable throttling mechanism that increases the valve opening degree as the refrigerant pressure at the outlet side of the indoor evaporator 15 increases.

[0087] Furthermore, the evaporation pressure regulating valve 17 is configured to maintain the refrigerant evaporation temperature in the indoor evaporator 15 at a reference temperature (1°C in this embodiment) or higher that can suppress frost formation on the indoor evaporator 15.

[0088] Furthermore, the outlet of the evaporating pressure regulating valve 17 is connected to the refrigerant inlet side of one of the refrigerant confluence sections. Additionally, the refrigerant outlet side of the chiller 16 is connected to the refrigerant inlet side of the other refrigerant confluence section. Here, the refrigerant confluence section has the same three-way connector structure as the refrigerant branch section, with two of the three inflow outlets serving as refrigerant inlets and the remaining one as a refrigerant outlet.

[0089] The refrigerant confluence section merges the flow of refrigerant from the evaporating pressure regulating valve 17 with the flow of refrigerant from the chiller 16. Furthermore, the refrigerant outlet of the refrigerant confluence section is connected to the suction port side of the compressor 11.

[0090] Next, the heating unit 20 in the air conditioning unit 1 will be described. The heating unit 20 is a structure used to heat the supply air W supplied to the air-conditioned space by using the high-pressure refrigerant in the heat pump cycle 10 as a heat source.

[0091] The heating unit 20 according to the first embodiment is composed of a high-temperature side heat medium circuit 21. The high-temperature side heat medium circuit 21 is a heat medium circuit that circulates the high-temperature side heat medium. As the high-temperature side heat medium, a solution containing ethylene glycol, antifreeze, etc. can be used.

[0092] The high-temperature side heat medium circuit 21 of the heating section 20 is equipped with a heat medium passage 12b of a heat medium refrigerant heat exchanger 12, a radiator 22, a heater core 23, an electric heater 24, a high-temperature side flow regulating valve 25, a high-temperature side pump 26, etc.

[0093] As described above, in the heat medium passage 12b of the heat medium refrigerant heat exchanger 12, the high-temperature side heat medium is heated by heat exchange with the high-pressure refrigerant flowing in the refrigerant passage 12a. That is, the high-temperature side heat medium is heated using the heat extracted by the heat pump cycle 10.

[0094] Radiator 22 is a heat exchanger that allows the high-temperature side heat medium, heated by the heat medium / refrigerant heat exchanger 12, to exchange heat with the outside air OA blown by the outside air fan (not shown), thereby dissipating the heat of the high-temperature side heat medium to the outside air OA. Radiator 22 is an example of an outside air radiator.

[0095] Furthermore, the radiator 22 is located on the front side inside the vehicle's engine hood. With the operation of the aforementioned external air fan, external air OA flows from the front side of the vehicle to the rear, passing through the heat exchange section of the radiator 22. Additionally, when the vehicle is in motion, the airflow can be directed from the front side of the vehicle to the rear, contacting the radiator 22.

[0096] The heater core 23 is a heat exchanger that heats the supply air W by exchanging heat between a high-temperature side heat medium heated by the heat medium / refrigerant heat exchanger 12 and the supply air W passing through the indoor evaporator 15. Therefore, the heater core 23 is an example of a heat exchanger for heating. Figure 1 , Figure 2 As shown, the heater core 23 is disposed inside the housing 41 of the indoor air conditioning unit 40.

[0097] An electric heater 24 is connected to the inlet and outlet of one side of the heat medium passage 12b in the heat medium heat exchanger 12. The electric heater 24 is a heating device that heats the high-temperature side heat medium flowing in the heat medium passage of the electric heater 24 by being supplied with electricity.

[0098] As the electric heater 24, a PTC heater with a PTC element (i.e., a positive characteristic thermistor) can be used, for example. The electric heater 24 can arbitrarily adjust the heat used to heat the high-temperature side heat medium by means of the control voltage output from the control device 50.

[0099] One of the inlet / outlet ports of a high-temperature side flow regulating valve 25 is connected to the outlet side of the heat medium passage in the electric heater 24. The high-temperature side flow regulating valve 25 is an electrically operated three-way flow regulating valve with three inlet / outlet ports. Another inlet / outlet port of the high-temperature side flow regulating valve 25 is connected to the inlet port of the heater core 23. The remaining inlet / outlet ports of the high-temperature side flow regulating valve 25 are connected to the inlet port of the radiator 22.

[0100] Therefore, in the high-temperature side heat medium circuit 21, the radiator 22 and the heater core 23 are connected in parallel with respect to the flow of the high-temperature side heat medium through the heat medium passage 12b of the heat medium refrigerant heat exchanger 12. Furthermore, the high-temperature side flow regulating valve 25 can continuously adjust the flow ratio of the high-temperature side heat medium flowing into the heater core 23 to the high-temperature side heat medium flowing into the radiator 22 in the high-temperature side heat medium circuit 21.

[0101] Furthermore, a merging section with a three-way connector is connected to the outlet of the radiator 22 and the outlet of the heater core 23. The merging section uses one of the three inlet outlets in the three-way connector as the outlet and the remaining two as inlet outlets. Therefore, the merging section allows the flow of the high-temperature side heat medium after passing through the radiator 22 and the flow of the high-temperature side heat medium after passing through the heater core 23 to merge.

[0102] Furthermore, the outlet of the confluence section is connected to the suction port of the high-temperature side pump 26. The high-temperature side pump 26 is a heat medium pump that pressurizes the high-temperature side heat medium in the high-temperature side heat medium circuit 21 to circulate it. The high-temperature side pump 26 is an electric pump whose speed (i.e., pressurization capacity) is controlled by a control voltage output from the control device 50. The discharge port of the high-temperature side pump 26 is connected to the inlet outlet on the other side of the heat medium passage 12b of the heat medium refrigerant heat exchanger 12.

[0103] like Figure 1 As shown, the high-temperature side heat medium circuit 21 can continuously adjust the flow rate of the high-temperature side heat medium flowing to the radiator 22 side and the flow rate of the high-temperature side heat medium flowing to the heater core 23 side by means of the high-temperature side flow regulating valve 25 configured in the branch.

[0104] In other words, by controlling the operation of the high-temperature side flow regulating valve 25, the heat of the high-temperature side heat medium dissipating heat from the radiator 22 to the outside air OA and the heat of the high-temperature side heat medium dissipating heat from the heater core 23 to the supply air W can be regulated. That is, the high-temperature side flow regulating valve 25 is equivalent to an example of a heat dissipation regulating unit.

[0105] Next, the low-temperature side heat medium circuit 30 in the air conditioning unit 1 will be described. The low-temperature side heat medium circuit 30 is a heat medium circuit that circulates the low-temperature side heat medium. As the low-temperature side heat medium, the same fluid as the high-temperature side heat medium in the high-temperature side heat medium circuit 21 can be used.

[0106] The low-temperature side heat medium circuit 30 is equipped with a heat medium passage 16b of the chiller 16, a battery 31, an external air heat exchanger 32, a low-temperature side flow regulating valve 33, a low-temperature side pump 34, etc. The outlet of the heat medium passage 16b in the chiller 16 is connected to the suction side of the low-temperature side pump 34.

[0107] The cryogenic side pump 34 is a heat medium pump that pressurizes and delivers the cryogenic side heat medium in the heat medium passage 16b after passing through the chiller 16 in the cryogenic side heat medium circuit 30. The basic structure of the cryogenic side pump 34 is the same as that of the high-temperature side pump 26.

[0108] Furthermore, a branch with a tee fitting structure is connected to the outlet side of the cryogenic pump 34. The branch uses one of the three inflow outlets in the tee fitting structure as an inlet and the remaining two as outlets. Therefore, the branch can split the flow of the cryogenic hot medium pressurized from the cryogenic pump 34 into two flows.

[0109] One of the outlets of the branch of the low-temperature side heat medium circuit 30 is connected to the inlet side of the heat medium passage in the battery 31. The battery 31 supplies power to various electrical devices of the vehicle, for example, using a rechargeable secondary battery (in this embodiment, a lithium-ion battery). The battery 31 generates heat during charging and discharging, and is therefore an example of a heat-generating device.

[0110] The battery 31 is a so-called battery pack formed by stacking multiple battery cells and connecting these battery cells in series or parallel. The output of this battery 31 tends to decrease when its temperature is low, and degradation tends to progress when its temperature is high. Therefore, the temperature of the battery 31 needs to be maintained within an appropriate temperature range (e.g., above 15°C and below 55°C) that allows for full utilization of the battery 31's charge and discharge capacity.

[0111] Here, in the air conditioning unit 1, a low-temperature heat medium passes through the heat medium passage of the battery 31 to exchange heat, thereby enabling the heat generated in the battery 31 to be absorbed by the low-temperature heat medium and thus regulating the temperature of the battery 31. That is, the battery 31 is connected in the low-temperature heat medium circuit 30 so that it can be cooled by the low-temperature heat medium, and the temperature of the battery 31 can be maintained within a predetermined temperature range.

[0112] Furthermore, the outlet of the branch of the low-temperature side heat medium circuit 30 is connected to the inlet side of the outside air heat exchanger 32. The outside air heat exchanger 32 is a heat exchanger that allows the low-temperature side heat medium discharged from the low-temperature side pump 34 to exchange heat with the outside air OA blown by the outside air fan (not shown).

[0113] The external air heat exchanger 32 is located at the front of the drive unit compartment. Therefore, when the vehicle is in motion, the airflow can come into contact with the external air heat exchanger 32. Therefore, the external air heat exchanger 32 can also be integrally formed with the radiator 22, etc.

[0114] like Figure 1 As shown, a low-temperature flow regulating valve 33 is connected to the outlet side of the heat medium passage of battery 31 and the outlet side of the external air heat exchanger 32. The low-temperature flow regulating valve 33 is a electrically operated three-way flow regulating valve with three inflow and outflow outlets.

[0115] That is, one inlet and outlet of the low-temperature flow regulating valve 33 is connected to the outlet side of the heat medium passage of the battery 31, and another inlet and outlet of the low-temperature flow regulating valve 33 is connected to the outlet side of the external air heat exchanger 32. Yet another inlet and outlet of the low-temperature flow regulating valve 33 is connected to the inlet side of the heat medium passage 16b in the chiller 16.

[0116] Therefore, the flow of the low-temperature side heat medium circuit 30 can be switched by controlling the operation of the low-temperature side flow regulating valve 33. For example, regarding the flow of the low-temperature side heat medium through the heat medium passage 16b of the chiller 16, the low-temperature side flow regulating valve 33 can continuously adjust the flow ratio of the low-temperature side heat medium through the external air heat exchanger 32 to the low-temperature side heat medium through the heat medium passage of the battery 31. That is, the low-temperature side pump 34 is equivalent to an example of a heat exchange quantity regulating unit.

[0117] For example, in the low-temperature side heat medium circuit 30, the low-temperature side flow regulating valve 33 can be controlled to connect the inflow and outlet of the chiller 16 side with the inflow and outlet of the battery 31 side, while closing the inflow and outlet of the outside air heat exchanger 32 side. In this case, the flow of the low-temperature side heat medium is switched so that the entire amount of the low-temperature side heat medium after passing through the chiller 16 passes through the heat medium passage of the battery 31.

[0118] According to this method, the low-temperature heat medium cooled by the chiller 16 can be supplied to the battery 31, thereby cooling the battery 31. In other words, the waste heat of the battery 31 absorbed as it cools can be absorbed by the low-pressure refrigerant of the heat pump cycle 10 through heat exchange in the chiller 16.

[0119] For example, in the low-temperature side heat medium circuit 30, the low-temperature side flow regulating valve 33 can be controlled to connect the inflow and outlet of the chiller 16 side with the inflow and outlet of the outside air heat exchanger 32 side, while closing the inflow and outlet of the battery 31 side. In this case, the flow of the low-temperature side heat medium is switched so that the entire amount of the low-temperature side heat medium after passing through the chiller 16 passes through the outside air heat exchanger 32.

[0120] According to this method, the low-temperature side heat medium cooled by the chiller 16 can be supplied to the outside air heat exchanger 32. Therefore, if the temperature of the low-temperature side heat medium is lower than the outside air temperature, the low-temperature side heat medium can absorb heat from the outside air OA. Thus, the outside air OA can be used as a heat source.

[0121] That is, the air conditioning unit 1 can cool and regulate the temperature of the battery 31 by utilizing the low-temperature side heat medium circuit 30. In addition, the air conditioning unit 1 can use the outside air OA as a heat source by utilizing the outside air heat exchanger 32.

[0122] Next, while referring to Figure 2 The interior air conditioning unit 40 constituting the air conditioning system 1 will be described below. The interior air conditioning unit 40 is a unit in the air conditioning system 1 used to blow the supply air W, which has been regulated by the heat pump cycle 10, to appropriate parts of the vehicle interior. The interior air conditioning unit 40 is located inside the instrument panel (i.e., dashboard) at the front of the vehicle interior.

[0123] The indoor air conditioning unit 40 is constructed by housing a blower 42, an indoor evaporator 15, a heater core 23, etc., within an air passage formed inside a housing 41, wherein the housing 41 forms the outer shell of the indoor air conditioning unit 40. The housing 41 forms an air passage for supply air W blown into the vehicle interior. The housing 41 is molded from a resin (specifically polypropylene) that has a certain degree of elasticity and excellent strength.

[0124] like Figure 2 As shown, an internal / external air switching device 43 is arranged on the upstream side of the air supply airflow in the housing 41. The internal / external air switching device 43 switches between internal air (indoor air) and external air (outdoor air) and introduces them into the housing 41.

[0125] The internal / external air switching device 43 continuously adjusts the opening areas of the internal air inlet and the external air inlet within the housing 41 via an internal / external air switching gate, thereby changing the ratio of the internal air volume to the external air volume. The internal / external air switching gate is driven by an electric actuator. This electric actuator controls its operation based on a control signal output from the control device 50.

[0126] A blower 42 is disposed downstream of the airflow from the air exchange device 43. The blower 42 is an electric blower mechanism that uses an electric motor to drive a centrifugal multi-blade fan. The blower 42 blows the air drawn in through the air exchange device 43 toward the vehicle interior. The speed (i.e., airflow capacity) of the blower 42 is controlled by a control voltage output from the control device 50.

[0127] Downstream of the supply airflow from the blower 42, an indoor evaporator 15 and a heater core 23 are arranged sequentially relative to the flow of the supply air. That is, the indoor evaporator 15 is positioned upstream of the supply airflow compared to the heater core 23.

[0128] Additionally, a cold air bypass passage 45 is formed within the housing 41. The cold air bypass passage 45 is an air passage that allows the supply air W after passing through the indoor evaporator 15 to bypass the heater core 23 and flow downstream.

[0129] An air mixing gate 44 is provided downstream of the supply airflow of the indoor evaporator 15 and upstream of the supply airflow of the heater core 23. The air mixing gate 44 adjusts the ratio of the airflow through the heater core 23 to the airflow through the cold air bypass passage 45 in the supply air W after passing through the indoor evaporator 15.

[0130] The air mixing door 44 is driven by an electric actuator for air mixing door operation. The electric actuator controls its operation according to the control signal output from the control device 50.

[0131] A mixing space 46 is provided downstream of the supply air flow of the heater core 23. In the mixing space 46, the supply air W heated by the heater core 23 is mixed with the supply air W that has not been heated by the heater core 23 but has passed through the cold air bypass passage 45.

[0132] Furthermore, an opening is provided at the lowest point of the airflow in the housing 41 to blow the airflow (air conditioning air) mixed in the mixing space 46 into the vehicle interior. This opening includes a face opening, a foot opening, and a defrost opening (none shown).

[0133] The face opening is for blowing air conditioning air towards the upper body of the occupants inside the vehicle. The foot opening is for blowing air conditioning air towards the feet of the occupants. The defrost opening is for blowing air conditioning air towards the inner side of the windshield at the front of the vehicle.

[0134] These face openings, foot openings, and defrost openings are connected to face air vents, foot air vents, and defrost air vents (not shown) located inside the vehicle interior via ducts that form air passages.

[0135] Therefore, the air mixing door 44 adjusts the airflow ratio between the airflow through the heater core 23 and the airflow through the cold air bypass passage 45, thereby regulating the temperature of the air conditioning air mixed in the mixing space 46. As a result, the temperature of the supply air (air conditioning air) blown into the vehicle interior from each outlet is also regulated.

[0136] Furthermore, a face panel, a foot panel, and a defrost door (not shown) are respectively located upstream of the airflow from the face opening, foot opening, and defrost opening. The face panel adjusts the opening area of ​​the face opening. The foot panel adjusts the opening area of ​​the foot opening. The defrost door adjusts the opening area of ​​the defrost opening.

[0137] These face panels, foot panels, and defrost doors constitute a blowing mode switching device that switches the airflow outlet from which the air conditioning is blown. The face panels, foot panels, and defrost doors are rotated in conjunction with an electric actuator that drives the airflow outlet mode door via a linkage mechanism. The electric actuator controls its operation based on a control signal output from the control device 50.

[0138] Next, refer to Figure 3 The control system of the air conditioning device 1 according to the first embodiment will be described. The control device 50 is composed of a known microcomputer including a CPU, ROM and RAM, and its peripheral circuits.

[0139] Furthermore, the control device 50 performs various calculations and processes based on the control program stored in the ROM, controlling the operation of various controllable devices connected to its output side. These controllable devices include a compressor 11, a first expansion valve 14a, a second expansion valve 14b, an electric heater 24, a high-temperature side flow regulating valve 25, a high-temperature side pump 26, a low-temperature side flow regulating valve 33, a low-temperature side pump 34, and a blower 42, etc.

[0140] like Figure 3 As shown, a sensor group for air conditioning control is connected to the input side of the control device 50. This sensor group includes: an indoor air temperature sensor 52a, an outdoor air temperature sensor 52b, a sunlight sensor 52c, a high-pressure sensor 52d, an evaporator temperature sensor 52e, a supply air temperature sensor 52f, and a battery temperature sensor 52g. The detection signals from these air conditioning control sensor groups are input to the control device 50.

[0141] Interior air temperature sensor 52a is an interior air temperature detection unit that detects the interior temperature (interior air temperature) Tr. Outside air temperature sensor 52b is an outside air temperature detection unit that detects the outside temperature (outside air temperature) Tam. Sunlight sensor 52c is a sunlight intensity detection unit that detects the amount of sunlight As illuminating the interior of the vehicle. High-pressure sensor 52d is a refrigerant pressure detection unit that detects the high-pressure refrigerant pressure Pd in ​​the refrigerant flow path from the outlet side of compressor 11 to the inlet side of first expansion valve 14a or second expansion valve 14b.

[0142] Evaporator temperature sensor 52e is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 15. Supply air temperature sensor 52f is a supply air temperature detection unit that detects the supply air temperature TAV blown into the vehicle interior. Battery temperature sensor 52g is a battery temperature detection unit that detects the battery temperature TBA, which is the temperature of the battery 31.

[0143] The battery temperature sensor 52g has multiple temperature detection units to detect the temperature of multiple parts of the battery 31. Therefore, the control device 50 can also detect the temperature difference between different parts of the battery 31. Furthermore, the battery temperature TBA is calculated as the average value of the values ​​detected by the multiple temperature detection units.

[0144] Furthermore, in order to detect the temperature of the heat medium in each heat medium circuit of the high-temperature side heat medium circuit 21 and the low-temperature side heat medium circuit 30, multiple heat medium temperature sensors are connected to the input side of the control device 50. Among the multiple heat medium temperature sensors are the first heat medium temperature sensor 53a to the fifth heat medium temperature sensor 53e.

[0145] The first heat medium temperature sensor 53a is disposed at the outlet of the heat medium passage in the electric heater 24 to detect the temperature of the high-temperature side heat medium flowing out of the electric heater 24. The second heat medium temperature sensor 53b is disposed at the outlet of the radiator 22 to detect the temperature of the high-temperature side heat medium after passing through the radiator 22. The third heat medium temperature sensor 53c is disposed at the inlet of the heater core 23 to detect the temperature of the high-temperature side heat medium flowing into the heater core 23.

[0146] The fourth heat medium temperature sensor 53d is disposed at the outlet of the heat medium passage 16b in the chiller 16 to detect the temperature of the low-temperature side heat medium flowing out of the chiller 16. The fifth heat medium temperature sensor 53e is disposed at the outlet of the heat medium passage in the battery 31 to detect the temperature of the low-temperature side heat medium flowing out of the heat medium passage in the battery 31.

[0147] Furthermore, the air conditioning unit 1 switches the flow of the heat medium in the high-temperature side heat medium circuit 21 and the low-temperature side heat medium circuit 30 of the heating unit 20 based on the detection results of the first heat medium temperature sensor 53a to the fifth heat medium temperature sensor 53e. As a result, the air conditioning unit 1 can manage the heat in the vehicle using the high-temperature side heat medium and the low-temperature side heat medium.

[0148] Furthermore, an operation panel 51 located near the instrument panel at the front of the vehicle interior is connected to the input side of the control device 50. Multiple operation switches are arranged on the operation panel 51. Therefore, operation signals from these multiple operation switches are input to the control device 50. The various operation switches on the operation panel 51 include an automatic switch, a cooling switch, a fan speed setting switch, and a temperature setting switch.

[0149] The automatic switch is operated when setting or deactivating the automatic control operation of the air conditioning unit 1. The cooling switch is operated when cooling of the vehicle interior is requested. The airflow setting switch is operated when the airflow of the blower 42 is manually set. Furthermore, the temperature setting switch is operated when the target temperature Tset of the vehicle interior is set.

[0150] Furthermore, in the control device 50, the control unit that controls various controllable devices connected to its output side is integrally constructed, but the structure (hardware and software) that controls the operation of each controllable device constitutes the control unit that controls the operation of each controllable device. For example, the structure in the control device 50 that controls the operation of the high-temperature side flow regulating valve 25, which is a heat dissipation regulating unit of the heating unit 20, is the heat dissipation regulating control unit 50a.

[0151] Furthermore, the structure in the control device 50 that controls the heat output of the electric heater 24 that heats the high-temperature side heat medium is the electric heater control unit 50b. The electric heater control unit 50b is equivalent to the heating device control unit. In addition, the structure in the control device 50 that controls the operation of the low-temperature side flow regulating valve 33, which serves as a heat exchange quantity regulating unit in the low-temperature side heat medium circuit 30, is the heat exchange quantity regulating control unit 50c.

[0152] Furthermore, the structure in the control device 50 that adjusts and sets the target blowing temperature TAO of the airflow blown into the vehicle interior based on the battery temperature TBA of the battery 31 is the target temperature setting unit 50d. Additionally, the structure in the control device 50 that controls the operation of the low-temperature side pump 34, etc., when the cooling of the battery 31 begins is the equipment cooling control unit 50e.

[0153] Next, the operation of the air conditioning unit 1 in the first embodiment will be described. As described above, in the air conditioning unit 1 according to the first embodiment, the operating mode can be appropriately switched from multiple operating modes. The switching of these operating modes is performed by executing a control program pre-stored in the control device 50.

[0154] More specifically, in the control program, the target blowing temperature TAO of the air supply air to be blown into the vehicle interior is calculated based on the detection signal detected by the sensor group used for air conditioning control and the operation signal output from the operation panel 51.

[0155] Specifically, the target blowing temperature TAO is calculated using the following mathematical formula F1:

[0156] TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×As+C…(F1)

[0157] In addition, Tset is the target temperature inside the vehicle interior (set temperature inside the vehicle interior) set by the temperature setting switch, Tr is the interior air temperature detected by the interior air temperature sensor 52a, Tam is the outside air temperature detected by the outside air temperature sensor 52b, and As is the amount of sunlight detected by the sunlight sensor 52c. Kset, Kr, Kam, and Ks are control gains, and C is a constant used for calibration.

[0158] Furthermore, in the control program, when the air conditioner switch on the operation panel 51 is turned on, and the target blowing temperature TAO becomes lower than the predetermined cooling reference temperature α, the air conditioner operation mode is switched to cooling mode.

[0159] Furthermore, in the control program, when the air conditioner switch on the control panel 51 is turned on, and the target air outlet temperature TAO reaches or exceeds the cooling reference temperature α, the air conditioner operation mode is switched to dehumidification and heating mode. And, when the air conditioner switch is not turned on, when the target air outlet temperature TAO reaches or exceeds the cooling reference temperature α, the air conditioner operation mode is switched to heating mode.

[0160] Furthermore, the control program switches between cooling the battery 31 and not cooling it based on the battery temperature TBA. Specifically, when the battery temperature TBA is above the reference battery temperature KTBA, the program switches to the operation mode that performs cooling on the battery 31.

[0161] Therefore, the operating mode of the air conditioning unit 1 is determined by a combination of the air conditioning operating mode and the operating mode indicating whether or not cooling of the battery 31 is performed. For example, when the air conditioning in the vehicle interior is not performed, and the battery temperature TBA is above the reference battery temperature KTBA, the operating mode of the air conditioning unit 1 is switched to a separate cooling mode that does not perform air conditioning in the vehicle interior but cools the battery 31.

[0162] Therefore, the operating modes of the air conditioning unit 1 include cooling mode, heating mode, dehumidifying heating mode, stand-alone cooling mode, cooling cooling mode, cooling heating mode, and cooling dehumidifying heating mode. The following is a description of each operating mode.

[0163] (a) Cooling mode

[0164] The cooling mode is an operating mode in which the air supply air W is cooled by the indoor evaporator 15 and blown into the vehicle interior without cooling the battery 31. In this cooling mode, the control device 50 opens the first expansion valve 14a at a predetermined throttling degree and fully closes the second expansion valve 14b.

[0165] Therefore, in the heat pump cycle 10 of the cooling mode, a refrigerant circulation loop is formed in which the refrigerant flows in the following order: compressor 11, refrigerant heat exchanger 12, first expansion valve 14a, indoor evaporator 15, evaporation pressure regulating valve 17, and compressor 11. That is, in the cooling mode, the refrigerant loop is switched to use the indoor evaporator 15 to cool the supply air W blown by the blower 42.

[0166] Furthermore, in this loop structure, the control device 50 controls the operation of various controllable devices connected to the output side. For example, the control device 50 controls the operation of the compressor 11 so that the refrigerant evaporation temperature Tefin detected by the evaporator temperature sensor 52e becomes the target evaporation temperature TEO. The target evaporation temperature TEO is determined based on the target blow-out temperature TAO with reference to the control mapping for the refrigeration mode pre-stored in the control device 50.

[0167] Specifically, in this control mapping, the target evaporation temperature TEO increases as the target blowout temperature TAO increases, so that the supply air temperature TAV detected by the supply air temperature sensor 52f approaches the target blowout temperature TAO. Moreover, the target evaporation temperature TEO is determined to be a value that can suppress frost formation on the indoor evaporator 15 (specifically, above 1°C).

[0168] Furthermore, the control device 50 determines the control voltage (air delivery capacity) of the blower 42 based on the target blowout temperature TAO and with reference to a control mapping pre-stored in the control device 50. Specifically, in this control mapping, the air delivery volume of the blower 42 is set to the maximum in the extremely low temperature region (maximum cooling region) and the extremely high temperature region (maximum heating region) of the target blowout temperature TAO, and the air delivery volume is reduced as it approaches the intermediate temperature region.

[0169] Furthermore, for the heating section 20 in cooling mode, the control device 50 controls the operation of the high-temperature side pump 26 to enable it to perform the water pressure delivery capacity in the predetermined cooling mode. In addition, the control device 50 controls the high-temperature side flow regulating valve 25 to connect the inflow and outflow of the radiator 22 side with the inflow and outflow of the electric heater 24 side, and to close the inflow and outflow of the heater core 23 side.

[0170] Thus, in the high-temperature side heat medium circuit 21 of the cooling mode, a circulation loop of the high-temperature side heat medium is formed in the order of high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, radiator 22, and high-temperature side pump 26.

[0171] In addition, for the low-temperature side heat medium circuit 30 in the cooling mode, the control device 50 does not operate the equipment constituting the low-temperature side heat medium circuit 30 and keeps it in a stopped state.

[0172] Thus, in the heat pump cycle 10 of the cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the heat medium refrigerant heat exchanger 12. In the heat medium refrigerant heat exchanger 12, since the high-temperature side pump 26 is working, the high-pressure refrigerant exchanges heat with the high-temperature side heat medium of the high-temperature side heat medium circuit 21, thereby cooling and condensing the high-pressure refrigerant and heating the high-temperature side heat medium.

[0173] Furthermore, in the high-temperature side heat medium circuit 21, the high-temperature side heat medium, heated by the heat medium refrigerant heat exchanger 12, flows into the radiator 22 via the electric heater 24 and the high-temperature side flow regulating valve 25. The high-temperature side heat medium flowing into the radiator 22 exchanges heat with the outside air OA to dissipate heat. The high-temperature side heat medium cooled by the radiator 22 is drawn in by the high-temperature side pump 26 and pressurized again into the heat medium passage 12b of the heat medium refrigerant heat exchanger 12.

[0174] On the other hand, the high-pressure refrigerant in the refrigerant passage 12a after the heat medium refrigerant heat exchanger 12 flows into the first expansion valve 14a via the refrigerant branch and is depressurized. The throttling opening of the first expansion valve 14a is adjusted so that the superheat of the refrigerant on the outlet side of the indoor evaporator 15 is approximately 3°C.

[0175] Low-pressure refrigerant, reduced by pressure at the first expansion valve 14a, flows into the indoor evaporator 15. The refrigerant flowing into the indoor evaporator 15 absorbs heat from the supply air W blown by the blower 42 and evaporates, thus cooling the supply air W. The refrigerant flowing out of the indoor evaporator 15 is drawn into the compressor 11 via the evaporation pressure regulating valve 17 and the refrigerant confluence section and compressed again.

[0176] Therefore, in the air conditioning unit 1 in cooling mode, the vehicle interior can be cooled by blowing the supplied air W, which has been cooled by the indoor evaporator 15, into the vehicle interior.

[0177] Furthermore, in this cooling mode, since the structure in the high-temperature side heat medium circuit 21 dissipates heat from the high-temperature side heat medium to the outside gas OA, the electric heater 24 is not operated. Of course, the electric heater 24 can also be operated as needed.

[0178] (b) Heating mode

[0179] The heating mode is an operating mode in which the air supply air W is heated by the heater core 23 and blown into the vehicle interior without cooling the battery 31. In this heating mode, the control device 50 opens the second expansion valve 14b at a predetermined throttling degree, so that the first expansion valve 14a is fully closed.

[0180] Therefore, in the heat pump cycle 10 of the heating mode, a heat pump cycle is formed in which the refrigerant circulates in the order of compressor 11, heat medium refrigerant heat exchanger 12, second expansion valve 14b, chiller 16, and compressor 11.

[0181] In other words, in heating mode, the refrigerant circuit is switched to the following mode: the refrigerant flows into the chiller 16 and absorbs the heat absorbed from the low-temperature side heat medium circuit 30, and is used to heat the supply air W.

[0182] In this loop structure, the control device 50 controls the operation of various controlled devices connected to the output side. For example, the control device 50 controls the operation of the compressor 11 so that the high-pressure refrigerant pressure Pd detected by the high-pressure sensor 52d becomes the target high-pressure PCO.

[0183] The target high-pressure PCO is determined based on the target outlet temperature TAO, with reference to a control mapping for heating modes pre-stored in the control device 50. Specifically, in this control mapping, the target high-pressure PCO increases as the target outlet temperature TAO increases, so that the supply air temperature TAV approaches the target outlet temperature TAO.

[0184] In addition, the control device 50 determines the control voltage (air supply capacity) of the blower 42 in the same way as the cooling mode. The control device 50 controls the operation of the air mixing door 44 so that it sets the ventilation path on the heater core 23 side to be fully open and closes the cold air bypass passage 45.

[0185] Furthermore, for the heating unit 20 in the heating mode, the control device 50 causes the high-temperature side pump 26 to operate in a manner that utilizes the water pressure delivery capacity of the predetermined heating mode. In addition, the control device 50 controls the high-temperature side flow regulating valve 25 to connect the inflow and outflow outlet on the heater core 23 side with the inflow and outflow outlet on the electric heater 24 side, and to close the inflow and outflow outlet on the radiator 22 side.

[0186] Thus, in the high-temperature side heat medium circuit 21 of the heating mode, a circulation loop of the high-temperature side heat medium is formed in the order of high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, heater core 23, and high-temperature side pump 26.

[0187] In addition, for the low-temperature side heat medium circuit 30 in heating mode, the control device 50 controls the operation of the low-temperature side pump 34 so that it can exert the water pressure delivery capacity in heating mode. Moreover, the control device 50 controls the operation of the low-temperature side flow regulating valve 33 so that the inflow and outlet of the chiller 16 side are connected to the inflow and outlet of the outside air heat exchanger 32 side, and the inflow and outlet of the battery 31 side are closed.

[0188] Thus, in the low-temperature side heat medium circuit 30 of the heating mode, a circulation loop of the low-temperature side heat medium is formed in the order of low-temperature side pump 34, outside air heat exchanger 32, low-temperature side flow regulating valve 33, chiller 16, and low-temperature side pump 34.

[0189] Here, the low-temperature side heat medium in the low-temperature side heat medium circuit 30 exchanges heat with the outside air OA when passing through the outside air heat exchanger 32. Since the low-temperature side heat medium has been cooled by the chiller 16, it absorbs heat from the outside air OA based on the temperature difference with the outside air OA. In other words, the air conditioning unit 1 can use the outside air OA as a heat source for heating in the heating mode.

[0190] Furthermore, in the heat pump cycle 10 of the heating mode, the high-pressure refrigerant flowing out from the refrigerant passage 12a of the heat medium refrigerant heat exchanger 12 flows into the second expansion valve 14b and is depressurized. The throttling opening of the second expansion valve 14b is adjusted so that the refrigerant on the outlet side of the chiller 16 becomes a gas-liquid two-phase state. The low-pressure refrigerant can evaporate in the chiller 16 by exchanging heat with the low-temperature side heat medium, thereby absorbing heat from the low-temperature side heat medium.

[0191] The refrigerant, after absorbing heat from the low-temperature side heat medium, is compressed in compressor 11 and discharged as high-pressure refrigerant to the heat medium refrigerant heat exchanger 12. In the heat medium refrigerant heat exchanger 12, since the high-temperature side pump 26 is operating, the high-pressure refrigerant exchanges heat with the high-temperature side heat medium of the high-temperature side heat medium circuit 21, thereby cooling and condensing the high-pressure refrigerant. Thus, the high-temperature side heat medium is heated by the heat from the high-pressure refrigerant.

[0192] Furthermore, in the high-temperature side heat medium circuit 21, the high-temperature side heat medium, heated by the heat medium refrigerant heat exchanger 12, flows into the heater core 23 via the high-temperature side flow regulating valve 25. Since the air mixing door 44 sets the ventilation path on the heater core 23 side to be fully open, the high-temperature side heat medium flowing into the heater core 23 exchanges heat with the supply air W after passing through the indoor evaporator 15 to dissipate heat.

[0193] Therefore, in heating mode, the supply air W is heated, so that the temperature of the supply air W approaches the target blow-out temperature TAO. The high-temperature side heat medium flowing out from the heater core 23 is drawn in by the high-temperature side pump 26 and pressurized again into the heat medium passage 12b of the heat medium refrigerant heat exchanger 12.

[0194] That is, the air conditioning unit 1 in heating mode can use the heat pump cycle 10 to extract the heat absorbed from the outside air OA in the low-temperature side heat medium circuit 30, and then use it to heat the supply air W through the high-temperature side heat medium circuit 21.

[0195] (c) Dehumidification and heating mode

[0196] The dehumidification and heating mode is an operating mode in which the supply air W, cooled by the indoor evaporator 15, is heated in the heater core 23 and blown into the vehicle interior without cooling the battery 31. In this dehumidification and heating mode, the control device 50 opens the first expansion valve 14a and the second expansion valve 14b at a predetermined throttling degree.

[0197] Therefore, in the heat pump cycle 10 of the dehumidification and heating mode, the refrigerant circulates in the following order: compressor 11, heat medium refrigerant heat exchanger 12, first expansion valve 14a, indoor evaporator 15, evaporation pressure regulating valve 17, and compressor 11. Simultaneously, the refrigerant circulates in the following order: compressor 11, heat medium refrigerant heat exchanger 12, second expansion valve 14b, chiller 16, and compressor 11.

[0198] In other words, in the heat pump cycle 10 of the dehumidification and heating mode, the heat pump cycle that constitutes the parallel connection of the indoor evaporator 15 and the chiller 16 with respect to the flow of refrigerant flowing out from the heat medium refrigerant heat exchanger 12.

[0199] In this cycle structure, the control device 50 controls the operation of various controlled devices connected to the output side. For example, the control device 50 controls the operation of the compressor 11 in the same way as in the heating mode, so that the high-pressure refrigerant pressure Pd becomes the target high-pressure PCO.

[0200] Furthermore, for the heating unit 20 in the dehumidification and heating mode, the control device 50 causes the high-temperature side pump 26 to operate in a manner that utilizes the water pressure delivery capacity of the predetermined dehumidification and heating mode. In addition, the control device 50 controls the high-temperature side flow regulating valve 25 to connect the inflow and outflow of the heater core 23 side with the inflow and outflow of the electric heater 24 side, and to close the inflow and outflow of the radiator 22 side.

[0201] Thus, in the high-temperature side heat medium circuit 21 of the dehumidification and heating mode, a circulation loop of the high-temperature side heat medium is formed in the order of high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, heater core 23, and high-temperature side pump 26.

[0202] In addition, for the low-temperature side heat medium circuit 30 in the dehumidification and heating mode, the control device 50 controls the operation of the low-temperature side pump 34 to enable it to exert its water pressure delivery capacity in the dehumidification and heating mode. Moreover, the control device 50 controls the operation of the low-temperature side flow regulating valve 33 to connect the inflow and outflow of the chiller 16 side with the inflow and outflow of the outside air heat exchanger 32 side, and to close the inflow and outflow of the battery 31 side.

[0203] Thus, in the low-temperature side heat medium circuit 30 of the dehumidification and heating mode, a circulation loop of the low-temperature side heat medium is formed in the order of low-temperature side pump 34, outside air heat exchanger 32, low-temperature side flow regulating valve 33, chiller 16, and low-temperature side pump 34.

[0204] Furthermore, in the heat pump cycle 10 of the dehumidification and heating mode, the high-pressure refrigerant flowing out from the refrigerant passage 12a of the heat medium refrigerant heat exchanger 12 branches at the refrigerant branch section. The high-pressure refrigerant branched out at the refrigerant branch section flows into the first expansion valve 14a and is depressurized. The low-pressure refrigerant after being depressurized by the first expansion valve 14a flows into the indoor evaporator 15.

[0205] The refrigerant flowing into the indoor evaporator 15 absorbs heat from the supply air W blown by the blower 42 and evaporates, thus cooling the supply air W. The refrigerant flowing out of the indoor evaporator 15 is drawn into the compressor 11 and compressed again via the evaporation pressure regulating valve 17 and the refrigerant confluence section.

[0206] On the other hand, the high-pressure refrigerant branching out from the refrigerant branch flows into the second expansion valve 14b and is depressurized. The low-pressure refrigerant, depressurized by the second expansion valve 14b, flows into the chiller 16 and exchanges heat with the low-temperature side heat medium flowing in the heat medium passage 16b. Therefore, the low-pressure refrigerant can evaporate by exchanging heat with the low-temperature side heat medium, thereby absorbing heat from the low-temperature side heat medium. The refrigerant that has absorbed heat from the low-temperature side heat medium is drawn into the compressor 11 and compressed again.

[0207] The high-pressure refrigerant discharged from the compressor 11 condenses in the heat exchanger 12, where it exchanges heat with the high-temperature side heat medium in the high-temperature side heat medium circuit 21. Thus, the heat from the high-pressure refrigerant is used to heat the high-temperature side heat medium.

[0208] Furthermore, in the high-temperature side heat medium circuit 21, the high-temperature side heat medium, heated by the heat medium refrigerant heat exchanger 12, flows into the heater core 23 via the high-temperature side flow regulating valve 25. The high-temperature side heat medium flowing into the heater core 23 dissipates heat by exchanging heat with the supply air W cooled by the indoor evaporator 15.

[0209] Therefore, in the dehumidification and heating mode, the supply air W cooled by the indoor evaporator 15 can be heated to achieve dehumidification and heating in the vehicle interior. The high-temperature side heat medium flowing out from the heater core 23 is drawn into the high-temperature side pump 26 and pressurized again into the heat medium passage 12b of the heat medium refrigerant heat exchanger 12.

[0210] That is, the air conditioning unit 1 in dehumidification and heating mode can use the heat pump cycle 10 to extract the heat absorbed from the outside air OA in the low-temperature side heat medium circuit 30, and then use it as a heat source to heat the cooled supply air W through the high-temperature side heat medium circuit 21.

[0211] (d) Individual Cooling Mode

[0212] The stand-alone cooling mode is an operating mode that cools the battery 31 without operating the air conditioning in the vehicle interior. In this stand-alone cooling mode, the control device 50 opens the second expansion valve 14b at a predetermined throttling degree and keeps the first expansion valve 14a fully closed.

[0213] Therefore, in the heat pump cycle 10 of the standalone cooling mode, a heat pump cycle is formed in which the refrigerant circulates in the order of compressor 11, heat medium refrigerant heat exchanger 12, second expansion valve 14b, chiller 16, and compressor 11.

[0214] In other words, in the standalone cooling mode, the refrigerant circuit is switched to the following mode: the refrigerant flows into the chiller 16 and the heat absorbed from the low-temperature side heat medium of the low-temperature side heat medium circuit 30 is transferred to the high-temperature side heat medium of the heating unit 20.

[0215] In this cycle structure, the control device 50 controls the operation of various controllable devices connected to the output side. For example, the control device 50 controls the operation of the compressor 11 so that it performs the refrigerant discharge capacity set in the individual cooling mode.

[0216] Furthermore, for the heating unit 20 in the independent cooling mode, the control device 50 controls the operation of the high-temperature side pump 26 to enable it to perform the water pressure delivery capacity in the predetermined independent cooling mode. In addition, the control device 50 controls the high-temperature side flow regulating valve 25 to connect the inflow and outflow of the radiator 22 side with the inflow and outflow of the electric heater 24 side, and to close the inflow and outflow of the heater core 23 side.

[0217] Thus, in the high-temperature side heat medium circuit 21 of the separate cooling mode, a circulation loop of the high-temperature side heat medium is formed in the order of high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, radiator 22, and high-temperature side pump 26.

[0218] In addition, for the low-temperature side heat medium circuit 30 in the standalone cooling mode, the control device 50 controls the operation of the low-temperature side pump 34 so that it can exert the water pressure delivery capacity in the standalone cooling mode. Moreover, the control device 50 controls the operation of the low-temperature side flow regulating valve 33 so that the inflow and outlet of the chiller 16 side are connected to the inflow and outlet of the battery 31 side, and the inflow and outlet of the outside air heat exchanger 32 side are closed.

[0219] Thus, in the low-temperature side heat medium circuit 30 of the separate cooling mode, a circulation loop of the low-temperature side heat medium is formed in the order of low-temperature side pump 34, battery 31, low-temperature side flow regulating valve 33, chiller 16, and low-temperature side pump 34.

[0220] Here, in the low-temperature side heat medium circuit 30, the low-temperature side heat medium cooled by the chiller 16 flows into the battery 31 via the low-temperature side flow regulating valve 33. In the heat medium passage of the battery 31, the low-temperature side heat medium absorbs heat from the battery 31, thereby cooling the battery 31. The low-temperature side heat medium flowing out of the battery 31 is drawn in by the low-temperature side pump 34 and pumped back into the heat medium passage 16b of the chiller 16.

[0221] In other words, according to the air conditioning unit 1 with a separate cooling mode, the low-pressure refrigerant of the heat pump cycle 10 can be used by the chiller 16 to absorb the heat absorbed by the low-temperature side heat medium of the low-temperature side heat medium circuit 30 when cooling the battery 31.

[0222] Furthermore, the air conditioning unit 1 can extract the heat absorbed in the chiller 16 through the heat pump cycle 10, and dissipate the heat to the high-temperature side heat medium in the high-temperature side heat medium circuit 21 through the heat medium refrigerant heat exchanger 12. Further, the air conditioning unit 1 can also dissipate the heat of the high-temperature side heat medium to the outside air OA through the radiator 22.

[0223] (e) Cooling / Refrigeration Mode

[0224] The cooling mode is an operating mode in which the air supply air W is cooled and blown into the vehicle interior through the indoor evaporator 15 in parallel with the cooling of the battery 31. In this cooling mode, the control device 50 opens the first expansion valve 14a and the second expansion valve 14b at a predetermined throttling degree.

[0225] Therefore, in the heat pump cycle 10 of the cooling mode, the refrigerant circulates in the following order: compressor 11, heat medium refrigerant heat exchanger 12, first expansion valve 14a, indoor evaporator 15, evaporation pressure regulating valve 17, and compressor 11. Simultaneously, the refrigerant circulates in the following order: compressor 11, heat medium refrigerant heat exchanger 12, second expansion valve 14b, chiller 16, and compressor 11.

[0226] In other words, in the heat pump cycle 10 of the cooling mode, the heat pump cycle that constitutes the parallel connection of the indoor evaporator 15 and the chiller 16 with respect to the flow of refrigerant flowing out from the heat medium refrigerant heat exchanger 12.

[0227] In this cycle structure, the control device 50 controls the operation of various controlled devices connected to the output side. For example, the control device 50 controls the operation of the compressor 11 so that it can perform the refrigerant discharge capacity set for the cooling mode.

[0228] Furthermore, for the heating section 20 in the cooling mode, the control device 50 controls the operation of the high-temperature side pump 26 to enable it to perform the water pressure delivery capacity in the predetermined cooling mode. In addition, the control device 50 controls the high-temperature side flow regulating valve 25 to connect the inflow and outflow of the radiator 22 side with the inflow and outflow of the electric heater 24 side, and to close the inflow and outflow of the heater core 23 side.

[0229] Thus, in the high-temperature side heat medium circuit 21 of the cooling and refrigeration mode, a circulation loop of the high-temperature side heat medium is formed in the order of high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, radiator 22, and high-temperature side pump 26.

[0230] In addition, for the low-temperature side heat medium circuit 30 in the cooling mode, the control device 50 controls the operation of the low-temperature side pump 34 to enable it to exert its water pressure delivery capacity in the cooling mode. Moreover, the control device 50 controls the operation of the low-temperature side flow regulating valve 33 to connect the inlet and outlet of the chiller 16 side with the inlet and outlet of the battery 31 side, and to close the inlet and outlet of the outside air heat exchanger 32 side.

[0231] Thus, in the low-temperature side heat medium circuit 30 of the cooling and refrigeration mode, a circulation loop of the low-temperature side heat medium is formed, which circulates in the order of low-temperature side pump 34, battery 31, low-temperature side flow regulating valve 33, chiller 16, and low-temperature side pump 34.

[0232] Therefore, in the low-temperature side heat medium circuit 30 of the cooling mode, the cooling water cooled by the chiller 16 flows into the battery 31 via the low-temperature side flow regulating valve 33. In the heat medium passage of the battery 31, the low-temperature side heat medium absorbs heat from the battery 31, thereby cooling the battery 31. The low-temperature side heat medium flowing out of the battery 31 is drawn in by the low-temperature side pump 34 and pumped back into the heat medium passage 16b of the chiller 16.

[0233] In other words, according to the cooling mode, the air conditioning unit 1 can use the chiller 16 to make the low-pressure refrigerant of the heat pump cycle 10 absorb the heat absorbed by the low-temperature side heat medium of the low-temperature side heat medium circuit 30 when cooling the battery 31.

[0234] Furthermore, in the cooling mode, the low-pressure refrigerant in the indoor evaporator 15 cools the airflow W by evaporating through heat exchange with the air blown into the vehicle interior. Thus, the air conditioning unit 1 in cooling mode can achieve cooling of the vehicle interior.

[0235] Furthermore, in the cooling mode, the heat absorbed by the refrigerant when cooling the battery 31 and the supply air W is dissipated to the high-temperature side heat medium through the heat medium refrigerant heat exchanger 12. In the high-temperature side heat medium circuit 21, the high-temperature side heat medium dissipates heat to the outside air 0A in the radiator 22. Therefore, the air conditioning unit 1 in the cooling mode can cool the battery 31 and improve comfort through cooling of the vehicle interior.

[0236] (f) Cooling and heating modes

[0237] The cooling / heating mode is an operating mode in which the air supply air W is heated by the heater core 23 and blown into the vehicle interior in parallel with the cooling of the battery 31. In this cooling / heating mode, the control device 50 opens the second expansion valve 14b at a predetermined throttling degree and keeps the first expansion valve 14a fully closed.

[0238] Therefore, in the heat pump cycle 10 of the cooling and heating mode, a heat pump cycle is formed in which the refrigerant circulates in the order of compressor 11, heat medium refrigerant heat exchanger 12, second expansion valve 14b, chiller 16, and compressor 11.

[0239] In other words, in the cooling and heating mode, the refrigerant circuit is switched to the following mode: the refrigerant can flow into the chiller 16, absorb the heat absorbed from the low-temperature side heat medium of the low-temperature side heat medium circuit 30, and use it to heat the supply air W.

[0240] In this cycle structure, the control device 50 controls the operation of various controllable devices connected to the output side. For example, the control device 50 controls the operation of the compressor 11 so that it can perform the refrigerant discharge capacity set in the cooling and heating mode.

[0241] Furthermore, for the heating unit 20 in the cooling / heating mode, the control device 50 controls the operation of the high-temperature side pump 26 to ensure it performs its predetermined water pressure delivery capacity in the cooling / heating mode. Additionally, the control device 50 controls the operation of the high-temperature side flow regulating valve 25, thereby adjusting the flow rate ratio between the high-temperature side heat medium flowing to the radiator 22 and the high-temperature side heat medium flowing to the heater core 23. The control of the high-temperature side flow regulating valve 25 in this case will be explained later with reference to the accompanying drawings.

[0242] Furthermore, the control device 50 regulates the heat output of the electric heater 24 by controlling its operation. The control of the electric heater 24 in this case will be explained later with reference to the accompanying drawings.

[0243] Therefore, in the high-temperature side heat medium circuit 21 of the cooling and heating mode, a circulation loop is formed for the high-temperature side heat medium, which circulates in the following order: high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, heater core 23, and high-temperature side pump 26. Simultaneously, a circulation loop is formed for the high-temperature side heat medium, which circulates in the following order: high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, radiator 22, and high-temperature side pump 26.

[0244] In other words, in the high-temperature side heat medium circuit 21 of the cooling and heating mode, the heat medium circuit that constitutes the parallel connection of the radiator 22 and the heater core 23 with respect to the flow of the high-temperature side heat medium flowing out from the heat medium refrigerant heat exchanger 12.

[0245] In addition, for the low-temperature side heat medium circuit 30 in the cooling and heating mode, the control device 50 controls the operation of the low-temperature side pump 34 so that it can exert the water pressure delivery capacity in the cooling and heating mode. Moreover, the control device 50 controls the operation of the low-temperature side flow regulating valve 33 so that the inflow and outlet of the chiller 16 side are connected to the inflow and outlet of the battery 31 side, and the inflow and outlet of the outside air heat exchanger 32 side are closed.

[0246] Thus, in the low-temperature side heat medium circuit 30 of the cooling and heating mode, a circulation loop of the low-temperature side heat medium is formed in the order of low-temperature side pump 34, battery 31, low-temperature side flow regulating valve 33, chiller 16, and low-temperature side pump 34.

[0247] In addition, such as Figure 1 As shown, in the low-temperature side heat medium circuit 30, the battery 31 and the external air heat exchanger 32 are connected in parallel relative to the flow of the low-temperature side heat medium after passing through the chiller 16. Therefore, by controlling the operation of the low-temperature side flow regulating valve 33, the flow ratio of the low-temperature side heat medium flowing to the battery 31 to the low-temperature side heat medium flowing to the external air heat exchanger 32 can also be adjusted. In this case, in addition to the above-mentioned circulation circuit, the low-temperature side heat medium circuit 30 also forms a circulation circuit that circulates in the order of low-temperature side pump 34, external air heat exchanger 32, low-temperature side flow regulating valve 33, chiller 16, and low-temperature side pump 34.

[0248] According to the air conditioning unit 1 in the cooling and heating mode, in the low-temperature side heat medium circuit 30, the low-pressure refrigerant of the heat pump cycle 10 can absorb the heat absorbed when cooling the battery 31 by the chiller 16. Moreover, according to the air conditioning unit 1 in the cooling and heating mode, in the heat pump cycle 10, the heat absorbed from the low-temperature side heat medium can be dissipated to the high-temperature side heat medium by the heat medium refrigerant heat exchanger 12.

[0249] Furthermore, in the high-temperature side heat medium circuit 21, by controlling the operation of the high-temperature side flow regulating valve 25, the heat dissipation of the high-temperature side heat medium in the heater core 23 and the heat dissipation of the high-temperature side heat medium in the radiator 22 can be adjusted. In other words, the air conditioning unit 1 can use the radiator 22 to dissipate the heat of the high-temperature side heat medium remaining in the heating of the supply air W to the outside air OA.

[0250] Furthermore, in the cooling / heating mode, the high-temperature side heat medium can be heated by the electric heater 24 in the high-temperature side heat medium circuit 21. Therefore, by appropriately adjusting the heat output of the electric heater 24, the air conditioning unit 1 can appropriately heat the supply air W using the heater core 23 to heat the vehicle interior.

[0251] (g) Cooling, dehumidification, and heating mode

[0252] The cooling, dehumidifying, and heating mode operates as follows: In parallel with the cooling of the battery 31, the supplied air W, cooled by the indoor evaporator 15, is heated in the heater core 23 and blown into the vehicle interior. In this cooling, dehumidifying, and heating mode, the control device 50 opens the first expansion valve 14a and the second expansion valve 14b at a predetermined throttling degree.

[0253] Therefore, in the heat pump cycle 10 of the cooling, dehumidifying, and heating mode, the refrigerant circulates in the following order: compressor 11, heat medium refrigerant heat exchanger 12, first expansion valve 14a, indoor evaporator 15, evaporating pressure regulating valve 17, and compressor 11. Simultaneously, the refrigerant circulates in the following order: compressor 11, heat medium refrigerant heat exchanger 12, second expansion valve 14b, chiller 16, and compressor 11.

[0254] In other words, in the heat pump cycle 10 of the cooling, dehumidifying and heating mode, the heat pump cycle that constitutes the parallel connection of the indoor evaporator 15 and the chiller 16 with respect to the flow of refrigerant flowing out from the heat medium refrigerant heat exchanger 12.

[0255] In this cycle structure, the control device 50 controls the operation of various controllable devices connected to the output side. For example, the control device 50 controls the operation of the compressor 11 so that it can perform the refrigerant discharge capacity set in the cooling, dehumidifying, and heating mode.

[0256] Furthermore, for the heating unit 20 in the cooling and dehumidifying heating mode, the control device 50 controls the operation of the high-temperature side pump 26 to ensure that it performs the predetermined water pressure delivery capacity in the cooling and dehumidifying heating mode. Additionally, similar to the cooling and heating mode, the control device 50 controls the operation of the high-temperature side flow regulating valve 25 to adjust the flow ratio between the high-temperature side heat medium flowing to the radiator 22 and the high-temperature side heat medium flowing to the heater core 23.

[0257] Furthermore, the control device 50 regulates the heat output of the electric heater 24 by controlling its operation. The control of the electric heater 24 in this case will be explained later with reference to the accompanying drawings.

[0258] Therefore, in the high-temperature side heat medium circuit 21 of the cooling, dehumidification, and heating mode, a circulation loop is formed for the high-temperature side heat medium, which circulates in the following order: high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, heater core 23, and high-temperature side pump 26. Simultaneously, a circulation loop is formed for the high-temperature side heat medium, which circulates in the following order: high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, radiator 22, and high-temperature side pump 26.

[0259] In other words, in the high-temperature side heat medium circuit 21 of the cooling, dehumidifying and heating mode, the heat medium circuit that constitutes the parallel connection of the radiator 22 and the heater core 23 with respect to the flow of the high-temperature side heat medium flowing out from the heat medium refrigerant heat exchanger 12.

[0260] In addition, for the low-temperature side heat medium circuit 30 in the cooling and dehumidifying heating mode, the control device 50 controls the operation of the low-temperature side pump 34 to enable it to exert its water pressure delivery capacity in the cooling and dehumidifying heating mode. Moreover, the control device 50 controls the operation of the low-temperature side flow regulating valve 33 to connect the inflow and outflow of the chiller 16 side with the inflow and outflow of the battery 31 side, and to close the inflow and outflow of the outside air heat exchanger 32 side.

[0261] Thus, in the low-temperature side heat medium circuit 30 of the cooling, dehumidification and heating mode, a circulation loop is formed in which the low-temperature side pump 34, battery 31, low-temperature side flow regulating valve 33, chiller 16 and low-temperature side pump 34 circulate in sequence.

[0262] According to the air conditioning unit 1 in the cooling dehumidification heating mode, in the low-temperature side heat medium circuit 30, the low-pressure refrigerant of the heat pump cycle 10 can absorb the heat absorbed when cooling the battery 31 using the chiller 16. Furthermore, according to the air conditioning unit 1 in the cooling dehumidification heating mode, in the heat pump cycle 10, the heat absorbed from the low-temperature side heat medium and the heat absorbed when dehumidifying the supply air W can be dissipated to the high-temperature side heat medium using the heat medium refrigerant heat exchanger 12.

[0263] Furthermore, in the high-temperature side heat medium circuit 21, by controlling the operation of the high-temperature side flow regulating valve 25, the heat dissipation of the high-temperature side heat medium in the heater core 23 and the heat dissipation of the high-temperature side heat medium in the radiator 22 can be adjusted. In other words, the air conditioning unit 1 can use the radiator 22 to dissipate the heat of the high-temperature side heat medium remaining in the heating of the dehumidified supply air W to the outside air OA.

[0264] Furthermore, in the cooling, dehumidifying, and heating mode, the high-temperature side heat medium can be heated using the electric heater 24 in the high-temperature side heat medium circuit 21. Therefore, by appropriately adjusting the heat output of the electric heater 24, the air conditioning unit 1 can appropriately heat the dehumidified supply air W to achieve dehumidification and heating of the vehicle interior.

[0265] Here, in the cooling and heating mode and the cooling and dehumidifying heating mode, the amount of heat that can be dissipated to the high-temperature side heat medium in the heat medium refrigerant heat exchanger 12 is equivalent to the sum of the heat absorbed from the supply air W in the indoor evaporator 15, the heat absorbed from the low-temperature side heat medium in the chiller 16, and the compression work in the compressor 11.

[0266] Furthermore, the output of the battery 31 in the air conditioning unit 1 tends to decrease when its temperature is low, and deterioration tends to progress when its temperature is high. Therefore, if the low-temperature side heat medium is circulated in order to keep the battery 31 within an appropriate temperature range, the heat absorbed from the low-temperature side heat medium in the chiller 16 will vary depending on the amount of waste heat generated by the battery 31.

[0267] In this way, the amount of heat dissipated from the refrigerant heat exchanger 12 to the high-temperature side heat medium varies depending on the amount of waste heat generated by the battery 31. As a result, assuming that all the heat dissipated in the refrigerant heat exchanger 12 to the high-temperature side heat medium is used to heat the supply air W in the heater core 23, the following situation can be envisioned: the temperature variation of the supply air W affects the comfort of the vehicle interior.

[0268] In the air conditioning device 1 according to the first embodiment, the temperature fluctuation of the air supply air W in the cooling heating mode and the cooling dehumidification heating mode is suppressed by controlling the operation of the high temperature side flow regulating valve 25 and controlling the heat generation of the electric heater 24, thereby improving the comfort of the vehicle interior.

[0269] Next, refer to Figures 4-6 The content of heat dissipation regulation control via high-temperature side flow regulating valve 25 and heat generation regulation control via electric heater 24 in the air conditioning device 1 according to the first embodiment will be described.

[0270] Figure 4 This indicates the control settings related to the initiation of heat dissipation regulation via the high-temperature side flow regulating valve 25 and the initiation of heat generation regulation via the electric heater 24. Figure 4 The control program involved is executed by the control device 50 when the operating mode is switched to either the cooling and heating mode or the cooling and dehumidifying heating mode.

[0271] In step S1, it is determined whether the supply air temperature detected by the supply air temperature sensor 52f is excessive. Here, an excessive supply air temperature means that the supply air temperature is higher than the upper limit of a predetermined temperature range determined based on the target blow-out temperature TAO. If the supply air temperature is determined to be excessive, proceed to step S2. On the other hand, if the supply air temperature is determined not to be excessive, proceed to step S3.

[0272] In step S2, in order to make the supply air temperature the target blowing temperature TAO, the heat dissipation in the radiator 22 of the high-temperature side heat medium circuit 21 is adjusted due to the excess heat of the high-temperature side heat medium.

[0273] That is, the initial balance adjustment is achieved between the heat dissipation from the high-temperature side heat medium to the outside air OA in radiator 22 and the heat dissipation from the high-temperature side heat medium used for heating the supply air W in heater core 23. Afterwards, the process ends. Figure 4 The control program.

[0274] When the supply air temperature is excessive relative to the target blow-out temperature TAO, by adjusting the heat dissipation in the radiator 22 in the high-temperature side heat medium circuit 21, the remaining heat can be dissipated from the high-temperature side heat medium to the outside air OA, and the supply air temperature can be brought close to the target blow-out temperature TAO.

[0275] Then, in step S3, it is determined whether the supply air temperature detected by the supply air temperature sensor 52f is insufficient. Here, insufficient supply air temperature means that the supply air temperature is lower than the lower limit of a specified temperature range determined based on the target blow-out temperature TAO as the target temperature.

[0276] If the supply air temperature is determined to be insufficient, proceed to step S4. If the supply air temperature is determined to be sufficient, end the process. Figure 4 The control program ends when the supply air temperature is within the temperature range determined based on the target blowout temperature (TAO).

[0277] When transitioning to step S4, in order to achieve the target blowout temperature TAO for the supplied air, heating of the electric heater 24 in the high-temperature side heat medium circuit 21 is initiated due to insufficient heat from the high-temperature side heat medium. Afterwards, the process ends. Figure 4 The control program.

[0278] When the supply air temperature is insufficient relative to the target blowing temperature TAO, the insufficient heat can be compensated by heating the high-temperature side heat medium in the high-temperature side heat medium circuit 21 using an electric heater 24, so that the supply air temperature can be close to the target blowing temperature TAO.

[0279] Next, with reference to the accompanying drawings, the control of heat dissipation regulation via the high-temperature side flow regulating valve 25 in the first embodiment will be described. Figure 5 The control program shown is executed by the control device 50 at the same time as the heat dissipation is adjusted by the high-temperature side flow regulating valve 25 in step S2 above.

[0280] like Figure 5 As shown, in step S10, it is determined whether the supply air temperature detected by the supply air temperature sensor 52f has increased. If it is determined that the supply air temperature has increased, the process proceeds to step S11. On the other hand, if it is determined that the supply air temperature has not increased, the process proceeds to step S12.

[0281] In step S11, since the heat dissipation in the heat exchanger 12 is greater than the sum of the heat dissipation in the heater core 23 and the radiator 22, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 rises. As a result, the system is determined to be in a state where the supply air temperature has risen. Therefore, the high-temperature side flow regulating valve 25 is controlled to increase the flow rate of the high-temperature side heat medium to the radiator 22.

[0282] As a result, the heat dissipation in radiator 22 increases, and therefore the heat dissipation in the heat medium refrigerant heat exchanger 12 approaches the sum of the heat dissipation in heater core 23 and radiator 22. Therefore, by operating the high-temperature side flow regulating valve 25 in step S11, the temperature rise of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 can be suppressed, thereby also suppressing the rise of the supply air temperature. As a result, the supply air temperature approaches the target outlet temperature TAO. Then, the process ends. Figure 5 The control program is shown.

[0283] In step S12, since the heat dissipation in the heat exchanger 12 is less than the sum of the heat dissipation in the heater core 23 and the radiator 22, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 decreases, resulting in a determination that the supply air temperature has decreased. Therefore, the high-temperature side flow regulating valve 25 is controlled to reduce the flow rate of the high-temperature side heat medium.

[0284] As a result, the heat dissipation in radiator 22 decreases, and the sum of the heat dissipation in heater core 23 and radiator 22 approaches the heat dissipation in heat medium refrigerant heat exchanger 12. Therefore, by operating the high-temperature side flow regulating valve 25 in step S12, the temperature drop of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 can be suppressed, thereby suppressing the drop in the supply air temperature. As a result, the supply air temperature approaches the target blow-out temperature TAO. Then, the process ends. Figure 5 The control program shown.

[0285] In addition, Figure 5 In the control program shown, if the heat dissipation adjustment through the high-temperature side flow regulating valve 25 is started in step S2, the program will be executed repeatedly as long as the operating mode of the air conditioning unit 1 does not switch from cooling mode and cooling dehumidification heating mode.

[0286] Moreover, by means of Figure 5 The control program shown controls the operation of the high-temperature side flow regulating valve 25, thereby enabling the adjustment of the proportion of heat remaining in the heat dissipated from the high-temperature side heat medium containing waste heat associated with the cooling of the battery 31 to the outside air OA via the radiator 22.

[0287] Therefore, by controlling the operation of the high-temperature side flow regulating valve 25 in both cooling and heating modes, the air conditioning unit 1 can suppress the influence of the amount of waste heat from the battery 31 and make the supply air temperature close to the target blowing temperature TAO.

[0288] Furthermore, between the radiator 22 and the heater core 23, the radiator increases the heat exchange capacity. Specifically, in terms of both the heat transfer area on the heat medium side and the heat transfer area on the air side, the radiator 22 is configured to be larger than the heater core 23. Therefore, the amount of heat dissipation capacity regulation of the radiator 22 by the high-temperature side flow regulating valve 25 is relatively greater than the amount of heat dissipation capacity regulation of the heater core 23. Thus, the influence of greater waste heat from the battery 31 can be suppressed, and the supply air temperature can be brought closer to the target blow-out temperature TAO.

[0289] Next, the control of the heat generation regulation of the electric heater 24 in the first embodiment will be described with reference to the accompanying drawings. Figure 6 The control program shown is executed by the control device 50 at the same time the electric heater 24 starts heating the high-temperature side heat medium in step S4 above.

[0290] like Figure 6 As shown, firstly, in step S20, it is determined whether the supply air temperature detected by the supply air temperature sensor 52f has increased. If it is determined that the supply air temperature has increased, the process proceeds to step S21. On the other hand, if it is determined that the supply air temperature has not increased, the process proceeds to step S22.

[0291] In step S21, since the sum of the heat dissipation in the heat exchanger 12 and the heat generation of the electric heater 24 is greater than the heat dissipation of the heater core 23, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 rises, and the system is determined to be in a state where the supply air temperature has risen. Therefore, the electric heater 24 is controlled to reduce the heat generation of the electric heater 24.

[0292] Therefore, the sum of the heat dissipation in the heat exchanger 12 and the heat generated by the electric heater 24 is close to the heat dissipation of the heater core 23. Therefore, by suppressing the temperature rise of the high-temperature side heat medium in the high-temperature side heat medium circuit 21, the temperature rise of the supply air can also be suppressed. Therefore, the supply air temperature approaches the target outlet temperature (TAO). Then, [the process ends]. Figure 6 The control program shown.

[0293] In step S21, since the sum of the heat dissipation in the heat exchanger 12 and the heat generated by the electric heater 24 is greater than the heat dissipation of the heater core 23, the temperature of the heat medium in the high-temperature side heat medium circuit 21 rises. As a result, the system is determined to be in a state where the supply air temperature has risen. Therefore, the electric heater 24 is controlled to reduce the heat generated by the electric heater 24.

[0294] Therefore, the sum of the heat dissipation in the heat exchanger 12 and the heat generated by the electric heater 24 is close to the heat dissipation of the heater core 23. Thus, by suppressing the temperature rise of the high-temperature side heat medium in the high-temperature side heat medium circuit 21, the temperature rise of the supply air can also be suppressed. As a result, the supply air temperature approaches the target outlet temperature (TAO). Then, [the process ends]. Figure 6 The control program shown.

[0295] In step S22, since the sum of the heat dissipation in the heat exchanger 12 and the heat generation of the electric heater 24 is less than the heat dissipation of the heater core 23, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 decreases, resulting in a state where the supply air temperature is determined to have decreased. Therefore, the electric heater 24 is controlled to increase its heat generation.

[0296] Therefore, the sum of the heat dissipation in the heat exchanger 12 and the heat generated by the electric heater 24 is close to the heat dissipation of the heater core 23. Thus, by suppressing the temperature decrease of the high-temperature side heat medium in the high-temperature side heat medium circuit 21, the rise in the supply air temperature can also be suppressed. Therefore, the supply air temperature approaches the target outlet temperature (TAO). Then, [the process ends]. Figure 6 The control program shown.

[0297] Furthermore, if the heating of the high-temperature heat medium by the electric heater 24 begins in step S4, the process will continue as long as the operating mode of the air conditioning unit 1 does not switch between cooling / cooling mode and cooling / dehumidifying / heating mode. Figure 6 The control program shown.

[0298] Moreover, by means of Figure 6 The control program shown controls the operation of the electric heater 24 and can add heat to the high-temperature side heat medium containing waste heat associated with the cooling of the battery 31 to compensate for the insufficient heat in order to achieve the target blow-out temperature TAO.

[0299] Thus, according to the air conditioning device 1 of the first embodiment, in the cooling heating mode and the cooling dehumidification heating mode, the heat pump cycle 10 can extract the waste heat absorbed as the battery 31 cools and use it to heat the supply air W.

[0300] Furthermore, in both cooling and heating modes, the air conditioning unit 1 can adjust the heat dissipation of the radiator 22 and the heat generation of the electric heater 24 by adjusting the high-temperature side flow regulating valve 25 based on the relationship between the supply air temperature and the target blow-out temperature TAO in both cooling and dehumidifying heating modes.

[0301] That is, by controlling the operation of the high-temperature side flow regulating valve 25, the air conditioning unit 1 can use the radiator 22 to dissipate an appropriate amount of residual heat from the high-temperature side heat medium to the outside air OA. In addition, by controlling the heat output of the electric heater 24, the air conditioning unit 1 can compensate for the heat required to make the supply air temperature reach the target blow-out temperature TAO by heating the high-temperature side heat medium through the electric heater 24.

[0302] Therefore, the air conditioning device 1 according to the first embodiment can suppress the influence of heat fluctuation of waste heat of battery 31 by adjusting the heat of the high-temperature side heat medium, so that the temperature of the supplied air is close to the target blowing temperature TAO.

[0303] Furthermore, in the air conditioning unit 1 according to the first embodiment, the switching of the operating mode is performed by executing a control program pre-stored in the control device 50. The switching of the operating mode of the air conditioning unit 1 includes switching from the cooling and heating mode to the cooling and dehumidifying heating mode and switching from the cooling and dehumidifying heating mode back to the cooling and heating mode.

[0304] Here, switching from cooling heating mode to cooling dehumidification heating mode is equivalent to the following: while the battery 31 is being cooled, cooling of the supply air W begins from a state where cooling of the supply air W using the indoor evaporator 15 has stopped. Similarly, switching from cooling dehumidification heating mode to cooling heating mode is equivalent to the following: while the battery 31 is being cooled, cooling of the supply air W ends from a state where cooling of the supply air W using the indoor evaporator 15 has stopped.

[0305] When switching from cooling / heating mode to cooling / dehumidifying / heating mode, the control device 50 reduces the opening degree of the second expansion valve 14b compared to the opening degree in cooling / heating mode. This reduces the refrigerant opening area in the second expansion valve 14b, thereby reducing the refrigerant flow rate in the chiller 16 and thus reducing the amount of heat absorbed from the low-temperature side heat medium in the chiller 16. In other words, according to the air conditioning unit 1, the battery 31 is not excessively cooled, thus preventing a decrease in the heat absorption capacity of the indoor evaporator 15.

[0306] Furthermore, when switching from cooling / heating mode to cooling / dehumidifying / heating mode, the control device 50 increases the opening degree of the first expansion valve 14a compared to the opening degree in cooling / heating mode. This increases the opening area of ​​the first expansion valve 14a, thereby increasing the refrigerant flow rate in the indoor evaporator 15 and thus enhancing the heat absorption capacity of the indoor evaporator 15 from the supply air W. In other words, according to the air conditioning device 1, the heat absorption capacity of the indoor evaporator 15 can be utilized while maintaining the cooling performance of the battery 31.

[0307] Thus, when the ratio of the opening area in the second expansion valve 14b to the sum of the opening areas in the first expansion valve 14a and the second expansion valve 14b is set as the opening area ratio, the control can be performed as follows.

[0308] The air conditioning unit 1 according to the first embodiment controls the opening area ratio when switching from cooling / heating mode to cooling / dehumidifying / heating mode, so that the opening area ratio after the cooling of the supply air begins is less than the opening area ratio before the cooling of the supply air begins. If this condition is met, either the first expansion valve 14a or the second expansion valve 14b can be controlled independently. By performing these controls when switching from cooling / heating mode to cooling / dehumidifying / heating mode, the air conditioning unit 1 can maintain the cooling performance of the battery 31 while utilizing the heat absorption capacity of the indoor evaporator 15.

[0309] When switching from cooling / dehumidification / heating mode to cooling / heating mode, the control device 50 increases the opening degree of the second expansion valve 14b compared to the opening degree in cooling / dehumidification / heating mode. This increases the opening area of ​​the second expansion valve 14b, thereby increasing the refrigerant flow rate in the chiller 16 and thus improving the amount of heat absorbed from the low-temperature side heat medium in the chiller 16. In other words, according to the air conditioning device 1, the low-temperature side heat medium can be supplied to the heat medium passage of the battery 31, thereby improving the cooling performance of the battery 31.

[0310] Furthermore, when switching from the cooling / dehumidifying heating mode to the cooling / heating mode, the control device 50 reduces the opening degree of the first expansion valve 14a compared to the opening degree in the cooling / heating mode. This reduces the opening area of ​​the first expansion valve 14a, thereby decreasing the refrigerant flow rate in the indoor evaporator 15 and thus reducing the amount of heat absorbed from the supply air W in the indoor evaporator 15. In other words, according to the air conditioning device 1, the cooling capacity used for the supply air W in the cooling / dehumidifying heating mode can be used for cooling the battery 31, thus improving the cooling performance of the battery 31.

[0311] The air conditioning unit 1 according to the first embodiment controls the opening area ratio when switching from cooling / dehumidifying / heating mode to cooling / heating mode, such that the opening area ratio after the cooling of the supply air begins is greater than the opening area ratio before the cooling of the supply air begins. If this condition is met, either the first expansion valve 14a or the second expansion valve 14b can be controlled independently. By performing these controls when switching from cooling / dehumidifying / heating mode to cooling / heating mode, the air conditioning unit 1 can maintain the cooling performance of the battery 31 while utilizing the heat absorption capacity of the indoor evaporator 15.

[0312] As explained above, according to the air conditioning device 1 of the first embodiment, by coordinating the operation of the heat pump cycle 10, the heating unit 20 and the low-temperature side heat medium circuit 30, multiple operating modes, including a cooling heating mode and a cooling dehumidification heating mode, can be realized.

[0313] In both cooling / heating and cooling / dehumidifying / heating modes, the air conditioning unit 1 can cool the battery 31 via a low-temperature heat transfer medium and utilize the waste heat from the battery 31 extracted by the heat pump cycle 10 for heating the supply air W. In other words, the air conditioning unit 1 can simultaneously cool the battery 31 and regulate the air of the target space by utilizing the waste heat from the battery 31.

[0314] In addition, air conditioning unit 1 is transmitted via, for example Figure 5 The high-temperature side flow regulating valve 25 is used to regulate the heat dissipation in the radiator 22, thereby regulating the amount of heat dissipated from the heater core 23 to the supply air W. Therefore, by adjusting the operation of the high-temperature side flow regulating valve 25, the effect of the heat generated by the battery 31 on the temperature of the supply air supplied to the vehicle interior can be adjusted, so that the supply air temperature is close to the predetermined target blowing temperature TAO.

[0315] That is, when the air conditioning unit 1 is in cooling and heating mode and cooling and dehumidifying and heating mode, it can improve the comfort of the air-conditioned space by utilizing the waste heat of the battery 31.

[0316] In addition, such as Figure 4 As shown, when the supply air temperature is excessive relative to the target blowout temperature TAO, the air conditioning unit 1 begins to adjust the heat dissipation of the radiator 22 using the high-temperature side flow regulating valve 25.

[0317] Therefore, the air conditioning unit 1 can properly dissipate the remaining heat from the radiator 22 to the outside air OA in order to make the supply air temperature reach the target blowing temperature TAO. Thus, even if the heat generated by the battery 31 increases, the comfort of the vehicle interior can be ensured.

[0318] Furthermore, in the air conditioning unit 1, the heat exchange capacity of the radiator 22 is higher than that of the heater core 23. Therefore, in the air conditioning unit 1, the amount of heat dissipation capacity adjustment of the radiator 22 using the high-temperature side flow regulating valve 25 is relatively greater than the amount of heat dissipation capacity adjustment of the heater core 23. As a result, the influence of the larger waste heat from the battery 31 can be suppressed, and the supply air temperature can be brought closer to the target outlet temperature TAO.

[0319] like Figure 1As shown, the heating unit 20 has a high-temperature side heat medium circuit 21, which is formed by connecting the radiator 22 and the heater core 23 in parallel with respect to the heat medium refrigerant heat exchanger 12.

[0320] The air conditioning unit 1 consists of a heating section 20 formed by a high-temperature side heat medium circuit 21 including a radiator 22 and a heater core 23. This allows the heat dissipation of the radiator 22 to the outside air OA and the heat dissipation of the heater core 23 to the supply air W to be adjusted by regulating the flow rate of the high-temperature side heat medium.

[0321] Furthermore, the high-temperature side flow regulating valve 25 in the air conditioning unit 1 continuously regulates the ratio of the flow rate of the high-temperature side heat medium to the heater core 23 to the flow rate of the high-temperature side heat medium to the radiator 22 in the high-temperature side heat medium circuit 21.

[0322] Therefore, the air conditioning unit 1 can adjust the heat dissipation in the heater core 23 according to the heat dissipation of the radiator 22, and can ensure the comfort of the vehicle interior with a simpler structure and better precision.

[0323] Furthermore, the air conditioning unit 1 has an electric heater 24 in the high-temperature side heat medium circuit 21, which is capable of heating the high-temperature side heat medium with any amount of heat, such as... Figure 6 As shown, the heat output of the electric heater 24 is adjusted so that the temperature of the supplied air is close to the target blowing temperature TAO.

[0324] Therefore, the air conditioning unit 1 can regulate the heat of the high-temperature side heat medium by adjusting the heat output of the electric heater 24, and as a result, can regulate the heat dissipated from the heater core 23 to the supply air W.

[0325] That is, when the air conditioning unit 1 is in cooling and heating mode and cooling and dehumidifying and heating mode, it can improve the comfort of the air-conditioned space by utilizing the waste heat of the battery 31.

[0326] In addition, such as Figure 4 As shown, when the supply air temperature is insufficient relative to the target blowout temperature TAO, the air conditioning unit 1 starts heating the high-temperature side heat medium by the electric heater 24.

[0327] Therefore, the air conditioning unit 1 can compensate for the insufficient heat required to make the supply air temperature reach the target blowing temperature TAO by heating by the electric heater 24, so that the comfort of the vehicle interior can be ensured even when the heat generated by the battery 31 is reduced.

[0328] like Figure 1As shown, in the heat pump cycle 10 of the air conditioning unit 1, the first expansion valve 14a and the indoor evaporator 15 are connected in parallel with the second expansion valve 14b and the chiller 16.

[0329] Therefore, according to the air conditioning unit 1, the indoor evaporator 15 can also be used to cool the air W blown into the vehicle interior in parallel with the cooling of the battery 31 using the chiller 16. That is, the air conditioning unit 1 can further improve the comfort of the vehicle interior while cooling the battery 31.

[0330] Furthermore, when the air conditioning unit 1 starts cooling the supply air W from a state where cooling of the supply air W has stopped while cooling the battery 31 is in progress, the opening area ratio determined by the opening areas of the first expansion valve 14a and the second expansion valve 14b is controlled. In this case, the opening area ratio is controlled such that the opening area ratio after cooling of the supply air W begins is less than the opening area ratio before cooling of the supply air W begins.

[0331] Therefore, when the air conditioning unit 1 starts cooling the supply air W from a state where cooling of the supply air W has stopped while cooling the battery 31 is in progress, it can appropriately adjust the heat absorption in the indoor evaporator 15 and the chiller 16. Thus, the air conditioning unit 1 can maintain the cooling performance of the battery 31 while utilizing the heat absorption capacity of the indoor evaporator 15.

[0332] Furthermore, when the air conditioning unit 1 stops cooling the supply air W while it is cooling the battery 31, it controls the opening area ratio determined by the opening areas of the first expansion valve 14a and the second expansion valve 14b. In this case, the opening area ratio is controlled such that the opening area ratio after the cooling of the supply air W ends is greater than the opening area ratio before the cooling of the supply air W ends.

[0333] Therefore, even when the air conditioning unit 1 stops cooling the supply air W while it is cooling the battery 31, it can still appropriately adjust the heat absorption in the indoor evaporator 15 and the chiller 16. Thus, the air conditioning unit 1 can maintain the cooling performance of the battery 31 while maximizing the heat absorption capacity of the indoor evaporator 15.

[0334] (Second Implementation)

[0335] Next, refer to Figures 7-9 The second embodiment, which differs from the first embodiment, will now be described. In the second embodiment, the control of the heating unit 20 is performed in the same way as in the first embodiment, and the control of the low-temperature side heat medium circuit 30 is also performed in the cooling heating mode and the cooling dehumidification heating mode.

[0336] Specifically, in the second embodiment, by controlling the low-temperature side flow regulating valve 33, the temperature fluctuation of the supply air W, which is associated with the fluctuation of waste heat from the battery 31, is suppressed while maintaining the cooling capacity of the battery 31, thereby improving the comfort inside the vehicle. The difference between the air conditioning device 1 in the second embodiment and the first embodiment lies in the control of the low-temperature side heat medium circuit 30; the basic structure of the air conditioning device 1 is the same as that in the first embodiment.

[0337] In the second embodiment, in the cooling and heating mode and the cooling and dehumidifying heating mode, the heat that can be dissipated to the high-temperature side heat medium in the heat medium refrigerant heat exchanger 12 also includes the heat absorbed from the low-temperature side heat medium in the chiller 16.

[0338] In the cooling and heating mode and cooling and dehumidifying heating mode involved in the second embodiment, the control device 50 adjusts the flow ratio of the flow of the low-temperature side heat medium to the battery 31 and the flow of the low-temperature side heat medium to the outside air heat exchanger 32 by controlling the operation of the low-temperature side flow regulating valve 33.

[0339] Therefore, the heat absorbed by the cooler 16 from the low-temperature side heat medium includes the heat absorbed by the low-temperature side heat medium from the battery 31 when cooling the battery 31 and the heat exchanged between the low-temperature side heat medium and the outside air OA in the outside air heat exchanger 32.

[0340] Therefore, the amount of heat that can be dissipated to the high-temperature side heat medium in the heat medium refrigerant heat exchanger 12 can be adjusted by the heat absorbed by the low-temperature side heat medium from the battery 31 when cooling the battery 31 in the low-temperature side heat medium circuit 30, and the heat exchanged between the low-temperature side heat medium and the outside air OA in the outside air heat exchanger 32.

[0341] In the air conditioning device 1 of the second embodiment, by controlling the low-temperature side flow regulating valve 33 in the cooling heating mode and the cooling dehumidification heating mode, the temperature fluctuation of the supply air W that is associated with the fluctuation of the waste heat of the battery 31 is suppressed while maintaining the cooling capacity of the battery 31, thereby improving the comfort of the vehicle interior.

[0342] Reference Figures 7-9 The operation control of the low-temperature side flow regulating valve 33 of the air conditioning unit 1 according to the second embodiment will be explained. First, the control related to the adjustment of heat dissipation in the low-temperature side heat medium circuit 30 according to the second embodiment will be explained with reference to the accompanying drawings.

[0343] Figure 7The control program shown is executed by the control device 50 when switching between the cooling / heating mode and the cooling / dehumidifying / heating mode. Furthermore, the control program is repeatedly executed until switching from the cooling / heating mode and the cooling / dehumidifying / heating mode to another operating mode.

[0344] In step S30, it is determined whether the outside air temperature detected by the outside air temperature sensor 52b is lower than the battery temperature detected by the battery temperature sensor 52g. If it is determined that the outside air temperature is lower than the battery temperature, proceed to step S31. If it is determined that the outside air temperature is not lower than the battery temperature, the process ends. Figure 7 The control program shown.

[0345] In step S31, the operation of the low-temperature side flow regulating valve 33 is controlled to reduce the flow rate of the low-temperature side heat medium to the outside air heat exchanger 32. After reducing the flow rate of the low-temperature side heat medium to the outside air heat exchanger 32, the process ends. Figure 7 The control program shown.

[0346] As described above, in both the cooling heating mode and the cooling dehumidification heating mode, the low-temperature side heat transfer medium absorbs the waste heat from the battery 31 while cooling the battery 31. Therefore, when the outside air temperature is lower than the battery temperature, the heat from the low-temperature side heat transfer medium that has absorbed the waste heat from the battery 31 will dissipate to the outside air OA through the outside air heat exchanger 32.

[0347] As a result, the amount of heat absorbed from the low-temperature side heat medium in the chiller 16 is reduced by a corresponding amount to the amount of heat dissipated from the outside air heat exchanger 32 to the outside air OA, ultimately leading to a reduction in the amount of heat that can be dissipated from the high-temperature side heat medium to the supply air W in the heater core 23.

[0348] In order to suppress useless heat dissipation in the external air heat exchanger 32 of the low-temperature side heat medium circuit 30, when the external air temperature is lower than the battery temperature, the heat exchange capacity in the external air heat exchanger 32 is reduced by adjusting the flow rate of the low-temperature side heat medium.

[0349] Therefore, according to the air conditioning device 1, even when the outside air temperature is lower than the battery temperature, it is possible to suppress the useless heat dissipation to the outside air OA by using the outside air heat exchanger 32, and to efficiently utilize the waste heat absorbed from the battery 31 to heat the supply air W.

[0350] Next, the heat absorption control in the low-temperature side heat medium circuit 30 when the outside air temperature is lower than the battery temperature will be explained with reference to the attached figure. Figure 8 The control program shown is executed by the control device 50 when switching between the cooling / heating mode and the cooling / dehumidifying / heating mode. Furthermore, the control program is repeatedly executed until switching from the cooling / heating mode and the cooling / dehumidifying / heating mode to another operating mode.

[0351] Here, when the outside air temperature is lower than the battery temperature, in the low-temperature side heat medium circuit 30, the side that absorbs heat from the battery 31 is more efficient at absorbing heat than the side that absorbs heat from the outside air OA. In other words, in the low-temperature side heat medium circuit 30 under this condition, the battery 31 is a more efficient heat source than the outside air heat exchanger 32.

[0352] like Figure 8 As shown, firstly, in step S40, it is determined whether the supply air temperature detected by the supply air temperature sensor 52f has increased. If it is determined that the supply air temperature has increased, the process proceeds to step S41. On the other hand, if it is determined that the supply air temperature has not increased, the process proceeds to step S42.

[0353] The transition to step S41 occurs when the heat dissipation in the heat exchanger 12 is greater than the heat dissipation in the heater core 23. Furthermore, heat dissipation also occurs in the radiator 22 when the heat dissipation in the heat exchanger 12 is greater than the sum of the heat dissipation from the radiator 22 and the heater core 23. Therefore, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 rises, and the condition is determined to be an increase in the supply air temperature.

[0354] Therefore, the low-temperature side flow regulating valve 33 is controlled to increase the flow rate of the low-temperature side heat medium to the outside air heat exchanger 32. As a result, the flow rate of the low-temperature side heat medium through the outside air heat exchanger 32 in the low-temperature side heat medium circuit 30 increases, thereby reducing the flow rate of the low-temperature side heat medium through the heat medium passage of the battery 31.

[0355] In other words, when the outside air temperature is lower than the battery temperature, by increasing the heat absorption in the outside air heat exchanger 32, the heat of the low-temperature side heat medium can be suppressed to a low level while maintaining the cooling performance of the battery 31.

[0356] Furthermore, in step S41, by suppressing the heat present in the low-temperature side heat medium to a lower level, the heat dissipation in the heat medium refrigerant heat exchanger 12 is reduced. As a result, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 decreases, reducing the heat used for heating the supply air W in the heater core 23. That is, the supply air temperature can be gradually reduced, bringing it closer to the target blow-out temperature TAO. Then, the process ends. Figure 8 The control program shown.

[0357] On the other hand, the transition to step S42 occurs when the heat dissipation in the heat medium refrigerant heat exchanger 12 is less than the heat dissipation in the heater core 23. Furthermore, heat dissipation also occurs in the radiator 22 when the heat dissipation in the heat medium refrigerant heat exchanger 12 is less than the sum of the heat dissipation of the radiator 22 and the heater core 23. Therefore, the temperature of the heat medium in the high-temperature side heat medium circuit 21 decreases, resulting in a state where the supply air temperature is determined to be decreasing.

[0358] Therefore, the low-temperature side flow regulating valve 33 is controlled to reduce the flow rate of the low-temperature side heat medium to the outside air heat exchanger 32. As a result, the flow rate of the low-temperature side heat medium through the outside air heat exchanger 32 in the low-temperature side heat medium circuit 30 is reduced, thereby increasing the flow rate of the low-temperature side heat medium through the heat medium passage of the battery 31.

[0359] In other words, when the outside air temperature is lower than the battery temperature, by reducing the heat absorbed in the outside air heat exchanger 32, it can actively be used as a heat source while maintaining the cooling performance of the battery 31, thus maximizing the heat of the low-temperature side heat medium.

[0360] Furthermore, step S42 increases the heat dissipation in the refrigerant heat exchanger 12 by increasing the heat possessed by the low-temperature side heat medium. As a result, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 rises, increasing the amount of heat utilized for heating the supply air W in the heater core 23. That is, the supply air temperature can be gradually increased, bringing it close to the target outlet temperature TAO. Then, the process ends. Figure 8 The control program shown.

[0361] Thus, according to the air conditioning device 1 of the second embodiment, when the outside air temperature is lower than the battery temperature, by appropriately utilizing the outside air OA and the battery 31 as the heat absorption source of the low-temperature side heat medium circuit 30, the temperature of the supplied air can be efficiently brought close to the target blow-out temperature TAO.

[0362] Next, the heat absorption control in the low-temperature side heat medium circuit 30 when the outside air temperature is higher than the battery temperature will be explained with reference to the attached figure. Figure 9 The control program shown is executed by the control device 50 when switching between the cooling / heating mode and the cooling / dehumidifying / heating mode. Furthermore, the control program is repeatedly executed until switching from the cooling / heating mode and the cooling / dehumidifying / heating mode to another operating mode.

[0363] Here, when the outside air temperature is higher than the battery temperature, in the low-temperature side heat medium circuit 30, the side that absorbs heat from the outside air OA is more efficient at absorbing heat than the side that absorbs heat from the battery 31, serving as the heat source for absorbing heat from the low-temperature side heat medium. In other words, in the low-temperature side heat medium circuit 30 under this condition, the outside air heat exchanger 32 is a more efficient heat source than the battery 31.

[0364] like Figure 9 As shown, firstly, in step S50, it is determined whether the supply air temperature detected by the supply air temperature sensor 52f has increased. If it is determined that the supply air temperature has increased, the process proceeds to step S51. On the other hand, if it is determined that the supply air temperature has not increased, the process proceeds to step S52.

[0365] The transition to step S51 occurs when the heat dissipation in the heat exchanger 12 is greater than the heat dissipation in the heater core 23. Furthermore, heat dissipation also occurs in the radiator 22 when the heat dissipation in the heat exchanger 12 is greater than the sum of the heat dissipation of the radiator 22 and the heater core 23. Therefore, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 rises, resulting in a state where the supply air temperature is determined to be rising.

[0366] Therefore, the low-temperature side flow regulating valve 33 is controlled to reduce the flow rate of the low-temperature side heat medium to the outside air heat exchanger 32. As a result, the flow rate of the low-temperature side heat medium through the outside air heat exchanger 32 in the low-temperature side heat medium circuit 30 is reduced, thereby increasing the flow rate of the low-temperature side heat medium through the heat medium passage of the battery 31.

[0367] In other words, when the outside air temperature is higher than the battery temperature, by increasing the heat absorption in the battery 31, it is possible to maintain the cooling performance of the battery 31 while suppressing the heat of the low-temperature side heat medium to a low level.

[0368] Furthermore, in step S51, the heat dissipation in the heat medium refrigerant heat exchanger 12 is reduced by suppressing the heat present in the low-temperature side heat medium. As a result, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 decreases, reducing the heat used to heat the supply air W in the heater core 23. That is, the supply air temperature can be gradually reduced, bringing it closer to the target blow-out temperature TAO. Then, the process ends. Figure 9 The control program shown.

[0369] On the other hand, the transition to step S52 occurs when the heat dissipation in the heat exchanger 12 is less than the heat dissipation in the heater core 23. Furthermore, heat dissipation also occurs in the radiator 22 when the heat dissipation in the heat exchanger 12 is less than the sum of the heat dissipation of the radiator 22 and the heater core 23. Therefore, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 decreases, resulting in a state where the supply air temperature is determined to be decreasing.

[0370] Therefore, the low-temperature side flow regulating valve 33 is controlled to increase the flow rate of the low-temperature side heat medium to the outside air heat exchanger 32. As a result, the flow rate of the low-temperature side heat medium through the outside air heat exchanger 32 in the low-temperature side heat medium circuit 30 increases, thereby reducing the flow rate of the low-temperature side heat medium through the heat medium passage of the battery 31.

[0371] In other words, when the outside air temperature is higher than the battery temperature, by increasing the heat absorption in the outside air heat exchanger 32, it is possible to maintain the cooling performance of the battery 31 while maximizing the heat of the low-temperature side heat medium.

[0372] Furthermore, in step S52, by increasing the heat possessed by the low-temperature side heat medium, the heat dissipation in the heat medium refrigerant heat exchanger 12 is increased. As a result, the temperature of the high-temperature side heat medium in the high-temperature side heat medium circuit 21 rises, and consequently, the heat utilized for heating the supply air W in the heater core 23 can be increased. That is, the supply air temperature can be gradually increased, and the supply air temperature can be brought close to the target blow-out temperature TAO. Then, the process ends. Figure 9 The control program shown.

[0373] Thus, according to the air conditioning device 1 of the second embodiment, when the outside air temperature is higher than the battery temperature, by appropriately utilizing the outside air OA and the battery 31 as the heat absorption source of the low-temperature side heat medium circuit 30, the temperature of the supplied air can be efficiently brought close to the target blow-out temperature TAO.

[0374] As explained above, the air conditioning unit 1 according to the second embodiment includes, in addition to the battery 31, an outside air heat exchanger 32 and a low-temperature side flow regulating valve 33 in the low-temperature side heat medium circuit 30. Figures 7-9 As shown, while maintaining the cooling capacity generated by the heat exchange between the battery 31 and the low-temperature side heat medium, the air conditioning unit 1 uses the low-temperature side flow regulating valve 33 to regulate the heat exchange in the outside air heat exchanger 32 so that the temperature of the supplied air is close to the target blowing temperature TAO.

[0375] Therefore, the air conditioning unit 1 can regulate the heat of the low-temperature side heat medium containing the waste heat of the battery 31 in the low-temperature side heat medium circuit 30 while maintaining the cooling capacity of the battery 31. As a result, it can regulate the heat used to heat the supply air W in the heater core 23.

[0376] That is, when the air conditioning unit 1 is in cooling and heating mode and cooling and dehumidifying and heating mode, and is using the waste heat of the battery 31 to regulate the air of the air-conditioned space, it can improve the comfort of the air-conditioned space independently of the heat generated by the battery 31 by adjusting the heat of the low-temperature side heat medium.

[0377] (Third Implementation)

[0378] Next, refer to Figure 10 , Figure 11 A third embodiment, different from the first embodiment described above, will be described. In the third embodiment, the control provisions related to the start of the adjustment operation of the high-temperature side flow regulating valve 25 and the control provisions related to the start of heating of the electric heater 24 differ from those in the first embodiment. Since the basic structure and other structures of the air conditioning unit 1 are the same as those in the first embodiment, further description is omitted.

[0379] First, refer to Figure 10 The control measures related to the start of heating of the electric heater 24 as described in the third embodiment will be explained. Figure 10 The control program involved is executed by the control device 50 when the operating mode is switched to cooling and heating mode or cooling and dehumidifying heating mode.

[0380] like Figure 10 As shown, in step S60, it is determined whether the supply air temperature is insufficient. The determination process in step S60 is the same as the control content of step S3 in the first embodiment. If the supply air temperature is insufficient, proceed to step S61. On the other hand, if the supply air temperature is not insufficient, proceed to step S63.

[0381] In step S61, it is determined whether the heat dissipation of the radiator 22 to the outside air OA is below a predetermined benchmark. This benchmark is determined, for example, to be the state in which the heat dissipation of the radiator 22 is at its lowest while ensuring the controllability of the flow control of the high-temperature side heat medium through the high-temperature side flow regulating valve 25.

[0382] Specifically, the determination can be made based on whether the flow rate of the high-temperature side heat medium to the radiator 22 is set below a reference level by the high-temperature side flow regulating valve 25. If the heat dissipation in the radiator 22 is below the reference level, proceed to step S62. On the other hand, if the heat dissipation in the radiator 22 is not below the reference level, proceed to step S63.

[0383] Furthermore, the state in which the heat dissipation in the external air radiator is below a predetermined reference can also be the state in which the flow rate of the high-temperature side heat medium in the radiator 22 is 0. Alternatively, it can be the state in which the flow rate is at its minimum in the flow distribution that can be achieved by the high-temperature side flow regulating valve 25.

[0384] In step S62, similar to step S4 in the first embodiment, heating begins via the electric heater 24 of the high-temperature side heat medium circuit 21. Here, the state transitioning to step S62 refers to a state where the supply air temperature is insufficient, even though as much heat drawn from the low-temperature side heat medium circuit 30 as possible is used to heat the supply air W.

[0385] That is, even if the waste heat absorbed by the cooling of the battery 31 is exhausted but the temperature of the supply air is still insufficient, the heating of the electric heater 24 is started. At this time, the heat output of the electric heater 24 is determined to make up for the deficiency, and therefore becomes the minimum necessary heat.

[0386] In other words, according to the air conditioning unit 1, when heating the supply air W, the waste heat of the battery 31 can be utilized preferentially, and the utilization of the electric heater 24 can be limited to a minimum, thus contributing to energy saving. After the electric heater 24 starts heating, the control program ends.

[0387] On the other hand, the transition to step S63 occurs because the heat dissipation of the radiator 22 is not below a reference level, thus allowing the heat dissipated by the radiator 22 to the outside air OA to be utilized in the heater core 23 for heating the supply air W. Therefore, in step S63, the heat dissipation of the radiator 22 is adjusted. Afterward, the control program ends.

[0388] As described above, the heat dissipation in radiator 22 is adjusted according to... Figure 5 The control program shown is executed. Therefore, the heat dissipated by the radiator 22 to the outside air OA is used to heat the supply air W, and the waste heat of the battery 31 absorbed from the low-temperature side heat medium circuit 30 is used to the maximum extent to heat the supply air W.

[0389] First, refer to Figure 11 The control measures related to the start of the regulating action of the high-temperature side flow regulating valve 25 as described in the third embodiment will be explained. Figure 11 The control program involved is executed by the control device 50 when the operating mode is switched to cooling and heating mode or cooling and dehumidifying heating mode.

[0390] like Figure 11As shown, in step S70, it is determined whether the supply air temperature is excessive. The determination process in step S70 is the same as the control content of step S1 in the first embodiment. If the supply air temperature is excessive, proceed to step S71. On the other hand, if the supply air temperature is not excessive, proceed to step S73.

[0391] In step S71, it is determined whether the heat output of the electric heater 24 is below a predetermined threshold. This threshold is determined, for example, to represent the state where the heat output of the heater core 23 is at its lowest while ensuring controllability of heat output control in the heater core 23.

[0392] Specifically, the determination can be made based on whether the control current of the electric heater 24 is 0 or whether the control current of the electric heater 24 is below a predetermined current value. If the heat output of the electric heater 24 is below a threshold value, proceed to step S72. On the other hand, if the heat output of the electric heater 24 is not below a threshold value, proceed to step S73.

[0393] In step S72, similar to step S2 in the first embodiment, the adjustment of the heat dissipation in the radiator 22 is started via the high-temperature side flow regulating valve 25. Here, the state transitioning to step S72 refers to a state where the supply air temperature is excessive, and the heat drawn from the low-temperature side heat medium circuit 30 is used to heat the supply air W without heating by the electric heater 24.

[0394] In other words, the state is as follows: when heating the supply air W, the supply air temperature can be sufficiently adjusted to the target blow-out temperature TAO by utilizing the waste heat of the battery 31, without using the heat generated by the electric heater 24. Therefore, according to the air conditioning unit 1, the utilization of the electric heater 24 is preferentially adjusted to a minimum, thus contributing to energy saving related to the heating of the supply air W. After that, the control program ends.

[0395] On the other hand, when proceeding to step S73, since the heat output of the electric heater 24 is not below a threshold, the heat output of the electric heater 24 is adjusted. Afterwards, the control program ends. As described above, the adjustment of the heat output in the electric heater 24 is based on... Figure 6 The control program shown is executed. Therefore, when the supply air temperature is excessive, the heat output of the electric heater 24 gradually decreases and approaches the threshold.

[0396] As explained above, the air conditioning device 1 according to the third embodiment can achieve the same effect as the first embodiment by means of the structure and operation common to the first embodiment, even if the conditions for starting the heat dissipation adjustment in the heating unit 20 and starting the heating of the electric heater 24 are changed.

[0397] like Figure 10 As shown, in the case where the heat dissipation of the air conditioning device 1 in the radiator 22 is reduced to below the reference level and the supply air temperature is insufficient, the electric heater 24 starts heating the high-temperature side heat medium.

[0398] Therefore, when the air conditioning unit 1 heats the supplied air W, it uses the electric heater 24 to heat the air while exhausting the waste heat of the battery 31. Thus, it can make priority use of the waste heat of the battery 31 and limit the energy consumption associated with the heating of the electric heater 24 to a minimum.

[0399] In addition, such as Figure 11 As shown, in the case of the third embodiment, when the heat output of the electric heater 24 is below the threshold and the supply air temperature is excessive, the air conditioning device 1 begins to adjust the heat dissipation in the radiator 22 through the high-temperature side flow regulating valve 25.

[0400] In this case, according to the air conditioning unit 1, the utilization of the electric heater 24 is preferentially adjusted to the minimum possible state, which can help to save energy related to the heating of the supply air and improve the comfort of the air-conditioned space.

[0401] (Fourth Implementation)

[0402] Next, refer to Figure 12 The fourth embodiment, which differs from the embodiments described above, will now be described. In the fourth embodiment, the structure of the heating unit 20 differs from that of the first embodiment.

[0403] Reference Figure 12 The structure of the air conditioning device 1 according to the fourth embodiment will be described. The air conditioning device 1 according to the fourth embodiment has the same heat pump cycle 10, heating unit 20, low-temperature side heat medium circuit 30, indoor air conditioning unit 40 and control device 50 as the embodiment described above.

[0404] The heat pump cycle 10 involved in the fourth embodiment has the same compressor 11, heat medium refrigerant heat exchanger 12, first expansion valve 14a, second expansion valve 14b, indoor evaporator 15, chiller 16 and evaporation pressure regulating valve 17 as the first embodiment.

[0405] Furthermore, the heating unit 20 in the fourth embodiment is similarly constructed to that in the first embodiment, consisting of a high-temperature side heat medium circuit 21 for circulating high-temperature side heat medium. For example... Figure 12As shown, the high-temperature side heat medium circuit 21 includes a heat medium passage 12b of the heat medium refrigerant heat exchanger 12, a heater core 23, an electric heater 24, and a high-temperature side pump 26. That is to say, the heating unit 20 according to the fourth embodiment does not have a radiator 22 and a high-temperature side flow regulating valve 25, which is different from the heating unit 20 in the above-described embodiments.

[0406] Furthermore, the low-temperature side heat medium circuit 30 in the fourth embodiment also includes a battery 31, an external air heat exchanger 32, a low-temperature side flow regulating valve 33, and a low-temperature side pump 34, just like in the first embodiment.

[0407] Therefore, in the air conditioning device 1 according to the fourth embodiment, it is possible to achieve Figure 6 The regulation and control of the heating capacity of the electric heater 24 in the high-temperature side heat medium circuit 21 shown, and Figures 7-9 The regulation and control of the heat exchange quantity in the external gas heat exchanger 32 of the low-temperature side heat medium circuit 30 shown.

[0408] As explained above, according to the air conditioning device 1 of the fourth embodiment, by coordinating the operation of the heat pump cycle 10, the heating unit 20, and the low-temperature side heat medium circuit 30, a cooling heating mode and a cooling dehumidification heating mode can be achieved. That is, the air conditioning device 1 can cool the battery 31 via the low-temperature side heat medium, and extract the waste heat of the battery 31 through the heat pump cycle 10 for use in heating the supply air W.

[0409] Furthermore, in the fourth embodiment, the air conditioning device 1 maintains the cooling capacity generated by the heat exchange between the battery 31 and the low-temperature side heat medium, and uses the low-temperature side flow regulating valve 33 to regulate the amount of heat exchange in the outside air heat exchanger 32 so that the temperature of the supplied air is close to the target blowing temperature TAO.

[0410] Therefore, the air conditioning unit 1 can regulate the heat of the low-temperature side heat medium containing the waste heat of the battery 31 in the low-temperature side heat medium circuit 30 while maintaining the cooling capacity of the battery 31. As a result, it can regulate the heat used to heat the supply air W in the heater core 23.

[0411] That is, when the air conditioning unit 1 is in cooling and heating mode and cooling and dehumidifying and heating mode, it can improve the comfort of the air-conditioned space by adjusting the heat of the low-temperature side heat medium, regardless of the heat generated by the battery 31.

[0412] (Fifth Implementation)

[0413] Next, refer to Figure 13A fifth embodiment, which differs from the embodiments described above, will now be described. In this fifth embodiment, the specific structures of the heat pump cycle 10 and the heating unit 20 differ from those in the embodiments described above. The other structures are the same as in the first embodiment, and therefore, further description is omitted.

[0414] Reference Figure 13 The structure of the heat pump cycle 10 and heating unit 20 according to the fifth embodiment will be described. The heat pump cycle 10 according to the fifth embodiment, like the embodiments described above, includes a compressor 11, a refrigerant heat exchanger 12, a first expansion valve 14a, a second expansion valve 14b, an indoor evaporator 15, a chiller 16, and an evaporation pressure regulating valve 17. In addition to having the same configuration as the first embodiment, the heat pump cycle 10 of the fifth embodiment also includes an indoor condenser 13.

[0415] like Figure 13 As shown, the indoor condenser 13 is disposed between the outlet side of the compressor 11 and the inlet side of the refrigerant passage 12a in the heat medium refrigerant heat exchanger 12. Moreover, the indoor condenser 13 is housed within the housing 41 of the indoor air conditioning unit 40 and is disposed at the position of the heater core 23 in the above embodiment.

[0416] That is, the indoor condenser 13 is a heat exchanger used for heating, in which the high-pressure refrigerant discharged from the compressor 11 exchanges heat with the supply air W after passing through the indoor evaporator 15. Therefore, the indoor condenser 13 is equivalent to an example of a heat exchanger for heating.

[0417] Furthermore, the high-temperature side heat medium circuit 21 according to the fifth embodiment includes a heat medium passage 12b of the heat medium refrigerant heat exchanger 12, a radiator 22, and a high-temperature side pump 26. That is, the heating unit 20 according to the fifth embodiment does not include a heater core 23, an electric heater 24, and a high-temperature side flow regulating valve 25, which is different from the high-temperature side heat medium circuit 21 in the first embodiment.

[0418] Therefore, in the fifth embodiment, by adjusting the pressure delivery capacity of the high-temperature side heat medium in the high-temperature side pump 26, the heat dissipation of the heat exchanger 22 to the external air OA can be adjusted.

[0419] Here, in the fifth embodiment, the radiator increases the heat exchange capacity between the radiator 22 and the indoor condenser 13. Specifically, in terms of air-side heat transfer area, the radiator 22 is configured to be larger than the indoor condenser 13. Therefore, the heat dissipation capacity adjustment of the radiator 22 in the fifth embodiment is relatively greater than that of the indoor condenser 13. Thus, the influence of the larger waste heat from the battery 31 can be suppressed, and the supply air temperature can be brought closer to the target outlet temperature (TAO).

[0420] Therefore, in the air conditioning device 1 according to the fifth embodiment, it is possible to achieve Figure 5 The heat dissipation adjustment and control in the radiator 22 shown above and Figures 7-9 The regulation and control of the heat exchange quantity in the external gas heat exchanger 32 of the low-temperature side heat medium circuit 30 shown.

[0421] As explained above, the air conditioning device 1 according to the fifth embodiment can achieve the same effect as the above-described embodiment by means of a structure and operation common to the above-described embodiment, even if the structure of the heating unit 20 is changed.

[0422] (Sixth Implementation Method)

[0423] Next, refer to Figure 14 The sixth embodiment, which differs from the embodiments described above, will now be described. In the sixth embodiment, a first high-temperature side pump 27a and a second high-temperature side pump 27b are used instead of the high-temperature side flow regulating valve 25 as the heat dissipation regulating unit of the heating unit 20.

[0424] Furthermore, in the sixth embodiment, with the adoption of the first high-temperature side pump 27a and the second high-temperature side pump 27b, the high-temperature side pump 26 in the above embodiments is eliminated.

[0425] like Figure 14 As shown, in the high-temperature side heat medium circuit 21 according to the sixth embodiment, a heat medium branch with a three-way connector structure is arranged at the position of the high-temperature side flow regulating valve 25 according to the first embodiment. The inlet side of the heat medium branch is connected to the outlet of the heat medium passage in the electric heater 24.

[0426] Furthermore, a first high-temperature side pump 27a is disposed between one of the outlets in the heat medium branch section and the inlet in the radiator 22. The first high-temperature side pump 27a is a heat medium pump that pressurizes the high-temperature side heat medium to the radiator 22. The basic structure of the first high-temperature side pump 27a is the same as that of the high-temperature side pump 26 described above.

[0427] Furthermore, a second high-temperature side pump 27b is disposed between another outlet in the heat medium branch and an inlet in the heater core 23. The second high-temperature side pump 27b is a heat medium pump that pressurizes the high-temperature side heat medium to the heater core 23. The basic structure of the second high-temperature side pump 27b is the same as that of the high-temperature side pump 26 described above.

[0428] Therefore, according to the air conditioning device 1 of the sixth embodiment, the pressure delivery capacity of the high-temperature side heat medium in the first high-temperature side pump 27a and the second high-temperature side pump 27b can be adjusted respectively. Thus, in the sixth embodiment, by controlling the operation of the first high-temperature side pump 27a and the second high-temperature side pump 27b, the flow rate ratio of the high-temperature side heat medium on the radiator 22 side to the high-temperature side heat medium on the heater core 23 side can be adjusted.

[0429] As explained above, the air conditioning device 1 according to the sixth embodiment, when the heat dissipation regulating unit is composed of the first high-temperature side pump 27a and the second high-temperature side pump 27b, can also obtain the same effect of the structure and operation as the above embodiment.

[0430] (Seventh Implementation)

[0431] Next, refer to Figure 15 A seventh embodiment, which differs from the embodiments described above, will be described. In the seventh embodiment, a radiator on / off valve 28 is used instead of a high-temperature side flow regulating valve 25 as the heat dissipation regulating unit of the heating unit 20.

[0432] like Figure 15 As shown, in the high-temperature side heat medium circuit 21 according to the seventh embodiment, a heat medium branch with a three-way connector structure is arranged at the position of the high-temperature side flow regulating valve 25 according to the first embodiment. The inlet side of the heat medium branch is connected to the outlet of the heat medium passage in the electric heater 24.

[0433] A radiator on / off valve 28 is provided between one of the outlets in the heat medium branch and the inlet in the radiator 22. The radiator on / off valve 28 is a solenoid valve that opens and closes the heat medium flow path connecting the heat medium branch and the radiator 22. The radiator on / off valve 28 continuously changes the opening degree in the heat medium flow path according to the control signal output from the control device 50.

[0434] Therefore, according to the air conditioning device 1 of the seventh embodiment, by adjusting the opening degree of the radiator on / off valve 28, the flow rate ratio of the high-temperature side heat medium on the radiator 22 side to the high-temperature side heat medium on the heater core 23 side can be adjusted.

[0435] As explained above, the air conditioning device 1 according to the seventh embodiment can achieve the same effect as the above-described embodiment by using a radiator on / off valve 28 instead of a high-temperature side flow regulating valve 25.

[0436] (Eighth Implementation Method)

[0437] Next, refer to Figure 16 An eighth embodiment, which differs from the embodiments described above, will be described. In this eighth embodiment, a gate device 29 is used instead of the high-temperature side flow regulating valve 25 as the heat dissipation regulating unit in the heating unit 20.

[0438] like Figure 16 As shown, in the air conditioning device 1 according to the eighth embodiment, a gate device 29 is arranged on the front side of the radiator 22. The gate device 29 is configured to have multiple blades arranged in a rotatable manner at the opening of the frame-shaped frame. The multiple blades rotate in conjunction with the operation of an electric actuator (not shown), adjusting the opening area in the opening of the frame.

[0439] Therefore, the gate device 29 can regulate the flow rate of the outside air OA passing through the heat exchange section of the radiator 22, and thus can regulate the heat exchange capacity of the radiator 22. In other words, the heat dissipation regulating unit in this invention is not limited to regulating the flow rate of the high-temperature side heat medium; it can also be structured to regulate the flow rate of the medium on the side dissipated by the radiator 22.

[0440] As explained above, the air conditioning device 1 according to the eighth embodiment can achieve the same effect as the above-described embodiment by using a gate device 29 instead of a high-temperature side flow regulating valve 25.

[0441] (Ninth Implementation)

[0442] Next, refer to Figure 17 A ninth embodiment, which differs from the embodiments described above, will be described. The air conditioning unit 1 of the ninth embodiment has the same basic structure as the air conditioning unit 1 of the first embodiment, and uses a cold heat storage exchanger 15a instead of the indoor evaporator 15 in the first embodiment.

[0443] The cold and heat storage exchanger 15a is an evaporator having a cold storage section 15b that stores the cold and heat of the low-pressure refrigerant after it has been depressurized by the first expansion valve 14a; it is an example of an evaporator for refrigeration. Furthermore, in Figure 17 The structure of the cold heat exchanger 15a and the cold storage unit 15b is shown in a simplified manner.

[0444] The cold storage heat exchanger 15a is a so-called box-tube type heat exchanger structure, which has multiple tubes through which refrigerant flows and a box for distributing or collecting the refrigerant flowing in the multiple tubes.

[0445] Furthermore, the heat storage heat exchanger 15a is constructed such that refrigerant flowing through tubes stacked at intervals in a certain direction exchanges heat with air flowing through air passages formed between adjacent tubes. The air passages between the multiple tubes in the heat storage heat exchanger 15a are equipped with fins to increase the contact area with the air supplied to the vehicle compartment. The fins are composed of multiple corrugated fins and are joined to two adjacent tubes by a bonding material with excellent heat transfer properties.

[0446] The cold storage unit 15b is disposed inside an air passage formed between two adjacent pipes. The cold storage unit 15b contains a cold storage material inside a casing made of a metal such as aluminum or aluminum alloy. This cold storage material is fixed by the condensation of heat from the refrigerant and released to the outside by the melting of the fixed heat. The casing of the cold storage unit 15b is thermally joined to each of the adjacent pipes.

[0447] Furthermore, PCM (phase change material) with a phase change temperature adjusted to below 0°C (specifically around -10°C) can be used as a cold storage material. Alternatively, materials made by adding non-volatile additives to water or alcohol can also be used as cold storage materials.

[0448] With this configuration of the heat storage exchanger 15a, in cooling mode, dehumidification and heating mode, the heat of the low-pressure refrigerant can be stored in the heat storage material of the heat storage section 15b while cooling the supply air using the heat of the low-pressure refrigerant. In other words, according to the air conditioning device 1 of the ninth embodiment, by using the heat storage exchanger 15a instead of the indoor evaporator 15, the heat stored during the cooling of the supply air can be effectively utilized.

[0449] Here, we examine an air conditioning unit 1 in which the indoor evaporator 15 and the chiller 16 are connected in parallel in a heat pump cycle 10. In this configuration, if the cooling of the supply air in the indoor evaporator 15 continues while the cooling of the battery 31 by the chiller 16 is started, it is conceivable that the refrigerant flow into the indoor evaporator 15 will temporarily decrease.

[0450] When the refrigerant flow to the indoor evaporator 15 decreases, the cooling capacity for the supply air also decreases. Consequently, the supply air temperature (TAV) detected by the supply air temperature sensor 52f will temporarily rise. Therefore, it is conceivable that this could impair the comfort of the vehicle interior or cause the windows to fog up.

[0451] In this regard, according to the air conditioning device 1 of the ninth embodiment, while the cooling of the supply air in the cold and heat storage exchanger 15a continues, the cooling of the battery 31 by the chiller 16 is about to begin, and the cold and heat of the low-pressure refrigerant are stored in the cold storage section 15b.

[0452] Furthermore, while continuing to cool the supply air in the cold storage heat exchanger 15a, the cooling of the battery 31 by the chiller 16 is also started. Although the cooling performance of the low-pressure refrigerant on the supply air will decrease, it can be compensated by using the cold and heat stored in the cold storage section 15b to cool the supply air.

[0453] According to the ninth embodiment of the air conditioning device 1, it is possible to suppress the transitional rise in the temperature of the air supply air when the cooling of the battery 31 begins while the cooling of the air supply air continues, thereby suppressing the decrease in comfort inside the vehicle.

[0454] As explained above, according to the ninth embodiment, even when the air conditioning device 1 uses a cold heat storage exchanger 15a as an evaporator for cooling the supply air, it can achieve the same effect as the above-described embodiment by using the same structure and operation.

[0455] Furthermore, according to the air conditioning device 1 of the ninth embodiment, when cooling of the supply air in the indoor evaporator 15 is continued while cooling of the battery 31 by the chiller 16 is started, the decrease in comfort due to transition can be suppressed by utilizing the cold and heat stored in the cold storage section 15b.

[0456] (Tenth Implementation)

[0457] Next, refer to Figure 18 The tenth embodiment, which differs from the embodiments described above, will be described. The air conditioning device 1 according to the tenth embodiment has the same basic structure as the air conditioning device 1 of the first embodiment, but differs in the control of cooling the battery 31 using the chiller 16 and heating the supply air using the heat exchanger 12.

[0458] Specifically, in the tenth embodiment, when executing the cooling heating mode or the cooling dehumidification heating mode, the control device 50 executes... Figure 18 The flowchart shown. Execution. Figure 18 The control device 50 shown in the flowchart is an example of the target temperature setting unit 50d.

[0459] Here, the cooling-heating mode and the cooling-dehumidifying-heating mode are examined. In both modes, the cooling of the battery 31 using the chiller 16 and the heating of the supply air using the heat exchanger 12 are performed simultaneously. Therefore, it is necessary to adjust the temperature of the low-temperature side heat medium in the low-temperature side heat medium circuit 30 appropriately, while also adjusting the temperature of the high-temperature side heat medium, so that the supply air temperature TAV becomes an appropriate temperature.

[0460] When the temperature of the high-temperature side heat medium is adjusted to meet the requirement of raising the temperature of the supply air, the high pressure in heat pump cycle 10 will also increase. When the high pressure in heat pump cycle 10 increases, from the perspective of the balance of the refrigeration cycle, the enthalpy difference decreases, which can be considered as potentially leading to insufficient cooling performance of the low-temperature side heat medium.

[0461] In view of this, the control device 50 executes the operation in cooling / heating mode and cooling / dehumidifying / heating mode. Figure 18 The flowchart is shown. When the cooling-heating mode or cooling-dehumidifying-heating mode is started, firstly, in step S80, it is determined whether the battery temperature TBA detected by the battery temperature sensor 52g has risen.

[0462] In other words, in step S80, it is determined whether the necessity of cooling the battery 31 of the target device has increased. If it is determined that the battery temperature TBA is rising, proceed to step S81; if it is determined that the battery temperature TBA is not rising, proceed to step S82.

[0463] In step S81, since the necessity of cooling the battery 31 increases as the battery temperature TBA rises, the target blowout temperature TAO, which is the target value of the supply air temperature TAV, is set to decrease. The target blowout temperature TAO is an example of a target temperature. By decreasing the target blowout temperature TAO, the high pressure in the heat pump cycle 10 can be reduced to ensure the enthalpy difference, thus ensuring the cooling performance of the battery 31. After decreasing the target blowout temperature TAO, the process ends. Figure 18 The control program.

[0464] On the other hand, in step S82, since the battery temperature TBA has not risen, it is considered that the necessity to cool the battery 31 is not very high. Therefore, the target blowout temperature TAO is set to rise.

[0465] In other words, by increasing the high pressure of the heat pump cycle 10, the heating performance of the supplied air is improved, while the cooling performance of the battery 31 is reduced. After raising the target blowout temperature TAO, the process ends. Figure 18 The control program. Furthermore... Figure 18The control program shown is repeatedly executed during the continuous operation of either the cooling / heating mode or the cooling / dehumidifying / heating mode.

[0466] According to the tenth embodiment, in the cooling heating mode or the cooling dehumidification heating mode, by executing... Figure 18 The control process shown can appropriately adjust the heating capacity of the supply air and the cooling capacity of the battery 31 according to the necessity related to the cooling of the battery 31.

[0467] As explained above, the air conditioning device 1 according to the tenth embodiment can achieve the same effect as the structure and operation common to the above-described embodiments even when the setting method of the target blow-out temperature TAO in the cooling heating mode and the cooling dehumidification heating mode is changed.

[0468] Furthermore, according to the air conditioning device 1 of the tenth embodiment, in the cooling and heating mode and the cooling and dehumidifying heating mode, when the battery temperature TBA rises, the target blowout temperature TAO can be reduced to ensure the cooling performance of the battery 31 with priority over the comfort of the vehicle interior.

[0469] (Eleventh Implementation Method)

[0470] Next, refer to Figure 19 An eleventh embodiment, which differs from the embodiments described above, will be described. In this eleventh embodiment, the control content of the target temperature setting unit 50d in the tenth embodiment is changed.

[0471] In the eleventh embodiment, when executing the cooling heating mode or the cooling dehumidification heating mode, the control device 50 is used to execute the operation. Figure 19 The flowchart shown. Execution. Figure 19 The control device 50 shown in the flowchart is an example of the target temperature setting unit 50d.

[0472] Figure 19 The flowchart shown is executed by the control device 50 in the same manner as in the tenth embodiment during cooling / heating mode and cooling / dehumidifying / heating mode. When the cooling / heating mode or cooling / dehumidifying / heating mode is started, firstly, in step S90, it is determined whether the battery temperature TBA detected by the battery temperature sensor 52g is above a predetermined threshold. The threshold is determined, for example, to be a battery temperature TBA that is higher than the reference battery temperature KTBA within a suitable temperature range of the battery 31, and the threshold indicates a state where the necessity for cooling the battery 31 is high.

[0473] In other words, in step S90, it is determined whether the necessity of cooling the battery 31 of the target device has increased to a threshold level or above. If it is determined that the battery temperature TBA is above the threshold, the process proceeds to step S91; if it is determined that the battery temperature TBA is not above the threshold, the process proceeds to step S92.

[0474] In step S91, since the battery temperature TBA exceeds the threshold and the necessity of cooling the battery 31 exceeds the reference, the target blow-out temperature TAO, which is the target value of the supply air temperature TAV, is set to be lower. Similar to the tenth embodiment, by lowering the target blow-out temperature TAO, the enthalpy difference in the heat pump cycle 10 can be ensured, thus ensuring the cooling performance of the battery 31. After lowering the target blow-out temperature TAO, the process ends. Figure 19 The control program.

[0475] On the other hand, in step S92, since the battery temperature TBA is lower than the threshold, and it is considered that the necessity for cooling the battery 31 is not very high, the target blowout temperature TAO is set to increase. That is, by increasing the high pressure of the heat pump cycle 10, the heating performance of the supply air is improved, and the cooling performance of the battery 31 is reduced. After the target blowout temperature TAO is increased, the process ends. Figure 19 The control program. Furthermore... Figure 19 The control program shown is also repeatedly executed during the continuous cooling / heating mode or cooling / dehumidifying / heating mode.

[0476] According to the eleventh embodiment, in the cooling heating mode or the cooling dehumidification heating mode, by executing... Figure 19 The control process shown can appropriately adjust the heating capacity of the supply air and the cooling capacity of the battery 31 according to the necessity related to the cooling of the battery 31.

[0477] As explained above, according to the eleventh embodiment, the air conditioning device 1 can still achieve the same effect as the above-described embodiment by changing the setting method of the target blow-out temperature TAO in the cooling heating mode and the cooling dehumidification heating mode.

[0478] Furthermore, according to the air conditioning device 1 of the eleventh embodiment, when the battery temperature TBA is above the threshold in the cooling heating mode and the cooling dehumidification heating mode, the cooling performance of the battery 31 can be ensured with priority over the comfort of the vehicle interior by reducing the target blow-out temperature TAO.

[0479] (Twelfth Implementation)

[0480] Next, refer to Figures 20-22A twelfth embodiment, which differs from the embodiments described above, will be described. In the twelfth embodiment, the placement position of the fourth heat medium temperature sensor 53d is determined based on its relationship with the internal volume of the chiller 16.

[0481] As described above, the fourth heat medium temperature sensor 53d is disposed at the outlet portion of the heat medium passage 16b in the chiller 16 to detect the temperature of the low-temperature side heat medium flowing out of the chiller 16. Therefore, the fourth heat medium temperature sensor 53d is equivalent to an example of a low-temperature side temperature sensor. In addition, the low-temperature side heat medium flowing out of the chiller 16 cools the battery 31, which is the device to be regulated by temperature.

[0482] Therefore, the location of the fourth heat medium temperature sensor 53d can be determined by the evaporator side internal volume Vc associated with the chiller 16, the low temperature sensor side internal volume Vt associated with the fourth heat medium temperature sensor 53d, and the low temperature side device internal volume Vb associated with the battery 31.

[0483] First, refer to Figure 20 The internal volume Vc of the evaporator side is explained. Since the chiller 16 cools the low-temperature side heat medium, which is the object of measurement for the fourth heat medium temperature sensor 53d, it is believed that the internal volume Vc of the evaporator side will affect the measurement accuracy of the fourth heat medium temperature sensor 53d.

[0484] The chiller 16 according to the twelfth embodiment is composed of a so-called stacked heat exchanger, having a heat exchange section 16e in which a plurality of generally flat heat transfer plates are stacked at intervals. In the heat exchange section 16e of the chiller 16, a refrigerant passage 16a and a heat medium passage 16b are formed in the same way as in the embodiment described above.

[0485] The refrigerant passage 16a allows low-pressure refrigerant, after being depressurized by the second expansion valve 14b, to flow through. The heat medium passage 16b allows the low-temperature heat medium circulating in the low-temperature heat medium circuit 30 to flow through. Therefore, in the chiller 16, the low-pressure refrigerant can evaporate and absorb heat from the low-temperature heat medium through heat exchange between the low-pressure refrigerant flowing in the refrigerant passage 16a and the low-temperature heat medium flowing in the heat medium passage 16b.

[0486] One side of the heat exchange section 16e in the refrigeration unit 16 ( Figure 20 The upper side of the heat exchange section 16e has a refrigerant outlet 16ao and a heat medium inlet 16bi. On the other hand, the other side of the heat exchange section 16e... Figure 20 The upper side of the surface has a refrigerant inlet 16ai and a heat medium outlet 16bo.

[0487] The refrigerant inlet 16ai constitutes one end of the refrigerant passage 16a, and the refrigerant outlet 16ao constitutes the other end of the refrigerant passage 16a. That is, in the heat exchange section 16e, the refrigerant flows into the refrigerant passage 16a from the refrigerant inlet 16ai and flows out to the outside of the heat exchange section 16e from the refrigerant outlet 16ao.

[0488] A first connector 16ci is installed at the refrigerant inlet 16ai. The first connector 16ci is a connecting component for connecting the refrigerant piping extending from the outlet of the second expansion valve 14b. Furthermore, a second connector 16co is installed at the refrigerant outlet 16ao. The second connector 16co is a connecting component for connecting the refrigerant piping extending toward the suction inlet of the compressor 11.

[0489] Additionally, a first connecting pipe 16di is installed at the hot medium inlet 16bi. The first connecting pipe 16di is a connecting component for connecting to the hot medium piping extending from the outlet of the cryogenic pump 34 in the cryogenic side hot medium circuit 30. Furthermore, a second connecting pipe 16do is installed at the hot medium outlet 16bo. The second connecting pipe 16do is a connecting component for connecting to the hot medium piping extending towards the suction port of the cryogenic pump 34 in the cryogenic side hot medium circuit 30.

[0490] Here, in the twelfth embodiment, the evaporator-side internal volume Vc represents the internal volume of the low-temperature heat medium side in the region where the low-temperature heat medium and refrigerant can exchange heat via the constituent material of the heat exchange section 16e. That is, Figure 20 The evaporator-side internal volume Vc is the area represented by the shading line extending to the lower left, which can also be described as the internal volume of the heat medium passage 16b formed inside the heat exchange section 16e.

[0491] Next, the internal volume Vt of the cryogenic sensor side will be explained. The fourth heat medium temperature sensor 53d is a sensor that detects the temperature of the cryogenic heat medium flowing out of the chiller 16. Therefore, as... Figure 20 As shown, the fourth heat medium temperature sensor 53d is installed on the second connecting pipe 16do or on the heat medium piping connected to the second connecting pipe 16do.

[0492] Furthermore, the internal volume Vt of the low-temperature sensor side represents the internal volume of the region downstream of the area where the low-temperature heat medium and refrigerant can exchange heat through the constituent materials of the heat exchange section 16e, and up to the temperature that can be measured by the fourth heat medium temperature sensor 53d.

[0493] Therefore, in the twelfth embodiment, the volume Vt of the low-temperature sensor side represents the volume of the low-temperature side heat medium within the range from the heat medium outlet 16bo of the chiller 16 to the temperature measuring section 53dc of the fourth heat medium temperature sensor 53d. That is, Figure 20 The internal volume Vt of the cryogenic sensor can be represented by a shading line extending downwards to the right.

[0494] Next, the internal volume Vb of the low-temperature side device will be explained. The internal volume Vb of the low-temperature side device means the internal volume occupied by the low-temperature side heat medium that cools the battery 31, which is the object of temperature regulation. Here, in the twelfth embodiment, a battery heat exchanger 35 is provided for regulating the temperature of the battery 31, and the heat medium passage of the battery 31 means the space inside the battery heat exchanger 35 for the low-temperature side heat medium to circulate.

[0495] use Figure 22 , Figure 23 The structure of the battery 31 and the battery heat exchanger 35 in the twelfth embodiment, as well as the internal volume Vb of the low-temperature side equipment, will be explained. Figure 22 As shown, the battery 31 is composed of a battery pack, which has multiple battery cells 31a stacked on top of each other and connected in series or in parallel.

[0496] The battery heat exchanger 35 has a heat medium inflow section 35a, a heat exchange section 35b and a heat medium outflow section 35c, which allows the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 30 to exchange heat with each battery cell 31a of the battery 31.

[0497] The heat exchange section 35b of the battery heat exchanger 35 is made of a material with good thermal conductivity and has a space inside for the flow of the low-temperature heat medium. The side of the heat exchange section 35b is formed as a plane and contacts the side of each battery cell 31a constituting the battery 31 in a manner that enables heat exchange.

[0498] Furthermore, on one side of the heat exchange section 35b (in Figure 22 , Figure 23 A heat medium inflow section 35a is provided on the lower side (in the middle). The heat medium inflow section 35a is the part that allows the low-temperature heat medium to flow into the interior of the heat exchange section 35b.

[0499] Additionally, on the other side of the heat exchange section 35b (in Figure 22 , Figure 23 A heat medium outlet 35c is provided on the upper side (center). The heat medium outlet 35c is a portion that allows the low-temperature side heat medium circuit 30, which passes through the interior of the heat exchange section 35b, to flow out to the outside of the battery heat exchanger 35. Therefore, the heat medium passage in the battery heat exchanger 35 is composed of the heat medium inlet 35a, the heat exchange section 35b, and the heat medium outlet 35c.

[0500] Furthermore, the internal volume Vb of the low-temperature side device represents the internal volume of the area where the temperature-regulating device (i.e., the battery 31) and the low-temperature side heat medium can exchange heat. Therefore, the internal volume Vb of the low-temperature side device in the twelfth embodiment can be referred to as: the internal volume occupied by the low-temperature side heat medium in the area of ​​the heat exchange section 35b of the battery heat exchanger 35 that is in contact with the battery 31 in a manner that allows for heat exchange.

[0501] Therefore, as in Figure 22 As shown by the shading in the middle, even the internal space of the heat exchange section 35b, being either above or below the contact area of ​​the battery 31, does not conform to the internal volume Vb of the low-temperature side device.

[0502] Furthermore, in the twelfth embodiment, the fourth heat medium temperature sensor 53d is configured in the heat medium piping on the heat medium outlet 16bo side of the chiller 16 such that the volume Vt of the low-temperature sensor side is smaller than the volume Vb of the low-temperature device side.

[0503] Consider the following scenario: the cooling performance of the low-temperature side heat medium in the chiller 16 is adjusted based on the temperature of the low-temperature side heat medium detected by the fourth heat medium temperature sensor 53d. For example, suppose that the internal volume Vt of the low-temperature sensor is larger than the internal volume Vb of the low-temperature device, and the fourth heat medium temperature sensor 53d detects a rise in the temperature of the low-temperature side heat medium. In this case, even if the cooling performance of the chiller 16 is improved, the low-temperature side heat medium located in the battery heat exchanger 35 is not present inside the chiller 16. Therefore, the adjustment of the cooling performance of the chiller 16 is difficult to reflect the temperature of the low-temperature side heat medium.

[0504] Regarding this, when the volume Vt of the low-temperature sensor side is configured to be smaller than the volume Vb of the low-temperature device side, at the moment when the temperature rise of the low-temperature heat medium is detected by the fourth heat medium temperature sensor 53d, the low-temperature heat medium in the battery heat exchanger 35 is present inside the chiller 16. Therefore, the adjustment of the cooling performance of the chiller 16 corresponding to the detection result of the fourth heat medium temperature sensor 53d can be easily reflected in the temperature of the low-temperature heat medium, enabling efficient cooling of the battery 31 via the low-temperature heat medium.

[0505] Furthermore, the fourth heat medium temperature sensor 53d is configured in the heat medium piping on the heat medium outlet 16bo side of the chiller 16 such that the sum of the internal volume Vt of the low temperature sensor side and the internal volume Vc of the evaporator side is smaller than the internal volume Vb of the low temperature equipment side.

[0506] With this configuration, when the temperature rise of the low-temperature side heat medium is detected by the fourth heat medium temperature sensor 53d, the interior of the chiller 16 is filled with the low-temperature side heat medium located in the battery heat exchanger 35. Therefore, the adjustment of the cooling performance of the chiller 16 corresponding to the detection result of the fourth heat medium temperature sensor 53d is more easily reflected in the temperature of the low-temperature side heat medium, thereby improving the cooling efficiency of the battery 31 via the low-temperature side heat medium.

[0507] Furthermore, the fourth heat transfer medium temperature sensor 53d is configured such that the volume Vt on the low-temperature sensor side is smaller than the volume Vc on the evaporator side. With this configuration, the low-temperature heat transfer medium detected by the fourth heat transfer medium temperature sensor 53d reliably exists inside the chiller 16. Therefore, control fluctuations can be suppressed in the control of the cooling performance of the chiller 16 based on the detection results of the fourth heat transfer medium temperature sensor 53d.

[0508] As explained above, the air conditioning device 1 according to the twelfth embodiment can achieve the same effect as the above-described embodiment by means of the structure and operation common to the above-described embodiment, even when the configuration of the fourth heat medium temperature sensor 53d is limited.

[0509] Furthermore, according to the air conditioning device 1 of the twelfth embodiment, by configuring the fourth heat medium temperature sensor 53d such that the internal volume Vt of the low-temperature sensor side is smaller than the internal volume Vb of the low-temperature device side, the adjustment of the cooling performance of the chiller 16 can be easily reflected in the temperature of the low-temperature heat medium. Therefore, the air conditioning device 1 of the twelfth embodiment can efficiently cool the battery 31 via the low-temperature heat medium.

[0510] Furthermore, in the air conditioning device 1 according to the twelfth embodiment, the fourth heat medium temperature sensor 53d is configured such that the sum of the volume Vt on the low-temperature sensor side and the volume Vc on the evaporator side is smaller than the volume Vb on the low-temperature side device. This makes it easier to adjust the cooling performance of the chiller 16 in accordance with the temperature of the low-temperature side heat medium, thereby improving the cooling efficiency of the battery 31 via the low-temperature side heat medium.

[0511] Furthermore, in the air conditioning device 1 according to the twelfth embodiment, the fourth heat medium temperature sensor 53d is configured such that the internal volume Vt of the low-temperature sensor side is smaller than the internal volume Vc of the evaporator side. As a result, the air conditioning device 1 can suppress control fluctuations related to the control of the cooling performance of the chiller 16 using the detection results of the fourth heat medium temperature sensor 53d.

[0512] (Thirteenth Implementation Method)

[0513] Next, refer to Figure 23 , Figure 24 A thirteenth embodiment, which differs from the embodiments described above, will be described. In the thirteenth embodiment, for example, its basic structure is the same as that of the air conditioning device 1 of the first embodiment, but it differs in the control of cooling the battery 31 when the chiller 16 is first used.

[0514] Specifically, in the thirteenth embodiment, when cooling of the battery 31 using the cooler 16 is performed in an environment where the outside air temperature is extremely low, the control device 50 executes... Figure 23 The flowchart shown. Execution. Figure 23 The control device 50 shown in the flowchart is an example of the equipment cooling control unit 50e.

[0515] It is also envisioned that the cooling of the battery 31 using the refrigeration unit 16 will be performed in an environment with extremely low outside air temperature. For example, in an extremely low temperature environment, the battery 31 generates heat during rapid charging, so it is necessary to cool the battery 31.

[0516] At this time, due to the extremely low temperature of the outside air, the temperature of the low-temperature heat medium in the low-temperature heat medium circuit 30 is also low. Therefore, it is conceivable that if cooling of the battery 31 is started under the original conditions, it will not be able to achieve its full performance. In addition, it is also conceivable that if the temperature of the refrigerant drawn into the compressor 11 is too low, the return of the refrigeration oil contained in the refrigerant will be poor, affecting the operation of the compressor 11.

[0517] In the air conditioning device 1 according to the thirteenth embodiment, considering these aspects, when cooling the battery 31 in an environment where the outside air temperature is extremely low, the following procedures are performed: Figure 23 The flowchart shown is as follows. Figure 23 As shown, firstly, in step S100, before starting the cooling of the battery 31 and before starting the heat pump cycle 10, the operation of the cryogenic side pump 34 is started. Thus, in the cryogenic side heat medium circuit 30, the cryogenic side heat medium circulates via the battery 31 and the chiller 16.

[0518] In the low-temperature side heat transfer medium circuit 30, the low-temperature side heat transfer medium circulates through the heat transfer medium passage of the battery 31, thus the low-temperature side heat transfer medium is heated by the heat generated in the battery 31. Figure 24 As shown, the temperature of the low-temperature side heat medium varies with the heat generated in the battery 31 due to the circulation of the low-temperature side heat medium, and stabilizes at a higher temperature.

[0519] In step S101, it is determined whether the refrigerant flow start condition is met. The refrigerant flow start condition means the condition for starting the flow of low-pressure refrigerant into the refrigerant passage 16a of the chiller 16, indicating that the temperature of the low-temperature side heat medium has stabilized at a relatively high temperature.

[0520] As described above, with the operation of the cryogenic pump 34, the temperature is heated and stabilized by the heat generated in the battery 31. Therefore, in step S101, it is determined whether a predetermined cycle period has elapsed since the start of operation of the cryogenic pump 34. If it is determined that the cycle period has elapsed, it is assumed that the temperature of the cryogenic heat medium has stabilized at a certain level, and therefore the process proceeds to step S102. If not, the circulation of the cryogenic heat medium in the cryogenic heat medium circuit 30 continues until the cycle period has elapsed.

[0521] In step S102, the compressor 11 begins operation, initiating the flow of low-pressure refrigerant into the chiller 16. At the moment of transition to step S102, the low-temperature side heat medium flowing into the chiller 16 has already been heated to a certain degree. Therefore, by starting the compressor 11 in this state, the refrigerant pressure on the low-pressure side of the refrigeration cycle can be pre-increased to a certain extent. Consequently, the cooling performance of the battery 31 using the chiller 16 in extremely low-temperature environments can be improved in the initial stage.

[0522] Furthermore, in step S102, other methods can be used as long as the flow of low-pressure refrigerant into the chiller 16 can begin. That is, it is not limited to the method of starting the compressor 11, and the process can proceed to step S102 when the compressor 11 is already running, and in step S102 the second expansion valve 14b is switched from the fully closed state to the throttling state.

[0523] As explained above, according to the thirteenth embodiment, the air conditioning device 1 can achieve the same effect as the above-described embodiment by means of the structure and operation common to the above-described embodiment, even if the operation of cooling the battery 31 at the start of the cooling in an extremely low temperature environment is changed.

[0524] (First variation of the thirteenth embodiment)

[0525] In step S101 of the thirteenth embodiment, it is determined that the refrigerant flow start condition has been met based on the condition that the cycle period has elapsed, but this method is not limited to this. For example, the refrigerant flow start condition can also be that the temperature change of the low-temperature side heat medium detected by the fourth heat medium temperature sensor 53d is within a predetermined range.

[0526] The fact that the temperature fluctuation of the low-temperature side heat medium is within a predetermined range indicates that the low-temperature side heat medium has been heated to a certain extent due to the heat generated in the battery 31. Therefore, even with the refrigerant flow start conditions employing this feature, the same effect as described in the thirteenth embodiment can be obtained.

[0527] (Second variation of the thirteenth embodiment)

[0528] Furthermore, as a condition for starting refrigerant flow in step S101, the following can also be adopted: the temperature of the low-temperature side heat medium detected by the fourth heat medium temperature sensor 53d is higher than a predetermined reference value.

[0529] With this refrigerant flow initiation condition, since the temperature of the low-temperature side heat medium is higher than the reference value, the refrigerant pressure on the low-pressure side of the heat pump cycle 10 can be pre-raised to within the guaranteed temperature range. As a result, similar to the thirteenth embodiment, performance in the initial stage can be ensured regarding the cooling of the battery 31 in the extremely low temperature environment.

[0530] (Fourteenth Implementation)

[0531] Next, refer to Figure 25 A fourteenth embodiment, different from the embodiments described above, will be described. In this fourteenth embodiment, the structures of the high-temperature side heat medium circuit 21 and the low-temperature side heat medium circuit 30 are changed compared to the embodiments described above. In addition, a sixth heat medium temperature sensor 53f is provided in the high-temperature side heat medium circuit 21 to detect the temperature of the high-temperature side heat medium flowing out of the heat medium refrigerant heat exchanger 12.

[0532] like Figure 25 As shown, the high-temperature side heat transfer medium circuit 21 in the fourteenth embodiment is configured by connecting the battery 31 to the high-temperature side heat transfer medium circuit 21 in the first embodiment via a preheating passage 29a. One end of the preheating passage 29a is connected to a heat transfer medium passage that connects the remaining inlet / outlet of the high-temperature side flow regulating valve 25 and the inlet of the radiator 22. Furthermore, the other end of the preheating passage 29a is connected to a heat transfer medium passage that connects the outlet of the radiator 22 and the suction port of the high-temperature side pump 26.

[0533] A heat transfer medium passage for battery 31 is connected to a preheating passage 29a. The structure of battery 31 and its heat transfer medium passage is the same as in the embodiment described above. That is, battery 31 is connected in a way that allows for temperature regulation via a high-temperature side heat transfer medium. Therefore, in the high-temperature side heat transfer medium circuit 21 of the fourteenth embodiment, radiator 22, heater core 23, and battery 31 are connected in parallel with respect to the flow of the high-temperature side heat transfer medium through the heat transfer medium passage 12b of the heat transfer medium refrigerant heat exchanger 12.

[0534] Furthermore, a radiator on / off valve 28 is provided on the inlet side of the radiator 22. The radiator on / off valve 28, like in the above embodiment, is an on / off valve that switches the flow of high-temperature heat medium into the radiator 22. In addition, the low-temperature heat medium circuit 30 of the fourteenth embodiment is constructed by connecting the heat medium passage 16b of the chiller 16, the low-temperature pump 34, and the external air heat exchanger 32.

[0535] In the air conditioning device 1 according to the fourteenth embodiment configured in this way, a preheating mode for preheating the battery 31 can be executed. In the preheating mode, the heat of the high-pressure refrigerant of the heat pump cycle 10 is used as a heat source and the battery 31 is preheated by heating it via a high-temperature side heat medium.

[0536] Specifically, the operation of the preheating mode will be explained. The heat pump cycle 10 operates in a predetermined mode in which the heat of the high-pressure refrigerant is used to heat the high-temperature side heat medium in the heat medium refrigerant heat exchanger 12.

[0537] Furthermore, in the high-temperature side heat medium circuit 21, the control device 50 operates the high-temperature side pump 26 and closes the radiator on / off valve 28. Additionally, for the high-temperature side flow regulating valve 25, the control device 50 connects the inflow and outlet of the electric heater 24 side with the inflow and outlet of the radiator 22 side while closing the inflow and outlet of the heater core 23 side.

[0538] Thus, in the preheating mode of the fourteenth embodiment, the high-temperature side heat medium circulates in the order of high-temperature side pump 26, heat medium refrigerant heat exchanger 12, electric heater 24, high-temperature side flow regulating valve 25, battery 31, and high-temperature side pump 26.

[0539] In other words, the high-temperature side heat medium discharged from the high-temperature side pump 26 is heated by heat exchange with the high-pressure refrigerant during its passage through the heat medium refrigerant heat exchanger 12. The high-temperature side heat medium, heated by the high-pressure refrigerant, flows into the heat medium passage of the battery 31 after passing through the electric heater 24 and the high-temperature side flow regulating valve 25. During its passage through the heat medium passage of the battery 31, the high-temperature side heat medium exchanges heat with the battery 31; therefore, the air conditioning unit 1 can preheat the battery 31 via the high-temperature side heat medium.

[0540] Here, in the preheating mode of the fourteenth embodiment, the control device 50 adjusts the refrigerant discharge capacity of the compressor 11 according to the temperature of the high-temperature side heat medium flowing out from the heat medium refrigerant heat exchanger 12. Therefore, as Figure 25As shown, a sixth heat medium temperature sensor 53f is disposed on the outlet side of the heat medium passage 12b in the heat medium refrigerant heat exchanger 12. The sixth heat medium temperature sensor 53f detects the temperature of the high-temperature side heat medium flowing out of the heat medium refrigerant heat exchanger 12. The sixth heat medium temperature sensor 53f is equivalent to an example of a high-temperature side temperature sensor.

[0541] As in the twelfth embodiment described above, the location of the sixth heat medium temperature sensor 53f can be determined using the internal volume Vth of the high-temperature sensor side, the internal volume Vbh of the high-temperature device side, and the internal volume Vch of the condenser side. The internal volumes Vth of the high-temperature sensor side, Vbh of the high-temperature device side, and Vch of the condenser side can be defined in the same way as in the twelfth embodiment.

[0542] In the fourteenth embodiment, the condenser-side internal volume Vch means the internal volume of the high-temperature side heat medium in the region where the high-temperature side heat medium and refrigerant can exchange heat through the constituent material of the heat exchange section in the heat medium-refrigerant heat exchanger 12.

[0543] Furthermore, in the fourteenth embodiment, the high-temperature sensor-side internal volume Vth means the internal volume downstream of the outlet of the heat medium passage 12b in the heat medium refrigerant heat exchanger 12, extending from the outlet of the heat medium passage 12b to the temperature measuring section of the sixth heat medium temperature sensor 53f. Additionally, the high-temperature device internal volume Vbh means the internal volume occupied by the high-temperature heat medium used to heat the battery 31, which is the object of temperature regulation in the preheating mode.

[0544] Furthermore, in the fourteenth embodiment, the sixth heat medium temperature sensor 53f is configured on the outlet side of the heat medium passage 12b of the heat medium refrigerant heat exchanger 12 such that the internal volume Vth of the high-temperature sensor side is smaller than the internal volume Vbh of the high-temperature device side.

[0545] In the preheating mode of the fourteenth embodiment, the refrigerant discharge capacity of the compressor 11 is changed according to the temperature of the high-temperature side heat medium detected by the sixth heat medium temperature sensor 53f, thereby adjusting the heating performance of the high-temperature side heat medium in the heat medium refrigerant heat exchanger 12.

[0546] Therefore, when the volume Vth of the high-temperature sensor side is configured to be smaller than the volume Vbh of the high-temperature device side, at the moment when the temperature rise of the high-temperature heat medium is detected by the sixth heat medium temperature sensor 53f, the high-temperature heat medium in the battery heat exchanger 35 is present inside the heat medium refrigerant heat exchanger 12. Therefore, the adjustment of the heating performance of the heat medium refrigerant heat exchanger 12 corresponding to the detection result of the sixth heat medium temperature sensor 53f is easily reflected in the temperature of the high-temperature heat medium, enabling efficient preheating of the battery 31 via the high-temperature heat medium.

[0547] Furthermore, the sixth heat medium temperature sensor 53f is configured in the heat medium piping on the outlet side of the heat medium passage 12b of the heat medium refrigerant heat exchanger 12 such that the sum of the internal volume Vth on the high temperature sensor side and the internal volume Vch on the condenser side is smaller than the internal volume Vbh on the high temperature side of the equipment.

[0548] With this configuration, when the temperature change of the high-temperature side heat medium is detected by the sixth heat medium temperature sensor 53f, the interior of the heat medium refrigerant heat exchanger 12 is filled with the high-temperature side heat medium that was previously in the battery heat exchanger 35. Therefore, the adjustment of the heating performance of the heat medium refrigerant heat exchanger 12 corresponding to the detection result of the sixth heat medium temperature sensor 53f is more easily reflected in the temperature of the high-temperature side heat medium, which can improve the preheating efficiency of the battery 31 via the high-temperature side heat medium.

[0549] Furthermore, the sixth heat medium temperature sensor 53f is configured such that the internal volume Vth on the high-temperature sensor side is smaller than the internal volume Vch on the condenser side. With this configuration, the high-temperature heat medium detected by the sixth heat medium temperature sensor 53f reliably exists inside the heat medium refrigerant heat exchanger 12. Therefore, control fluctuations can be suppressed in the control of the heating performance of the heat medium refrigerant heat exchanger 12 based on the detection results of the sixth heat medium temperature sensor 53f.

[0550] As explained above, the air conditioning device 1 according to the fourteenth embodiment can achieve the same effects as the embodiments described above through its common structure and operation. Furthermore, in the air conditioning device 1 according to the fourteenth embodiment, the sixth heat medium temperature sensor 53f is configured such that the internal volume Vth of the high-temperature sensor side is smaller than the internal volume Vbh of the high-temperature device side. Therefore, the air conditioning device 1 of the fourteenth embodiment can easily adjust the heating performance of the heat medium refrigerant heat exchanger 12 in preheating mode in accordance with the temperature of the high-temperature heat medium. Thus, the air conditioning device 1 according to the fourteenth embodiment can efficiently preheat the battery 31 via the high-temperature heat medium.

[0551] Furthermore, in the air conditioning device 1 according to the fourteenth embodiment, the sixth heat medium temperature sensor 53f is configured such that the sum of the internal volume Vth of the high-temperature sensor side and the internal volume Vch of the condenser side is smaller than the internal volume Vbh of the high-temperature side equipment. This makes it easier to adjust the heating performance of the heat medium refrigerant heat exchanger 12 in the preheating mode to reflect the temperature of the high-temperature side heat medium, thereby improving the preheating efficiency of the battery 31 via the high-temperature side heat medium.

[0552] Furthermore, in the air conditioning device 1 according to the fourteenth embodiment, the sixth heat medium temperature sensor 53f is configured such that the internal volume Vth of the high-temperature sensor side is smaller than the internal volume Vch of the condenser side. As a result, the air conditioning device 1 can suppress control fluctuations related to the control of the heating performance of the heat medium refrigerant heat exchanger 12, which uses the detection results of the sixth heat medium temperature sensor 53f.

[0553] The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the spirit of the present invention as follows.

[0554] In the above-described embodiment, the heat pump cycle 10 adopts a structure in which the first expansion valve 14a and the indoor evaporator 15 are connected in parallel with the second expansion valve 14b and the chiller 16, but it is not limited to this method.

[0555] As the heat pump cycle 10 in this invention, it is sufficient to have at least a pressure reducing section for absorbing heat from the low-temperature side heat medium circuit 30 and an evaporator (e.g., a second expansion valve 14b and a chiller 16), and other structures can be appropriately modified.

[0556] For example, it can be configured as a structure after removing the first expansion valve 14a and the indoor evaporator 15 from the structure of the heat pump cycle 10 of the above embodiment, or it can be configured as a structure in which a heat absorber different from the indoor evaporator 15 and the chiller 16 is connected in parallel with them. Alternatively, in the heat pump cycle 10, a structure in which the indoor evaporator 15 and the chiller 16 are connected in series can also be adopted.

[0557] Furthermore, while electrically operated expansion valves were used as the first expansion valve 14a and the second expansion valve 14b in the above embodiment, this method is not the only limitation. In the heat pump cycle 10, various methods can be used as long as the high-pressure refrigerant can be depressurized. For example, the second expansion valve 14b could still be an electrically operated expansion valve, while the first expansion valve 14a could be replaced with a temperature-controlled expansion valve.

[0558] Furthermore, while a heat exchanger 12 for the refrigerant heat medium is used as the condenser in this invention, it is not limited to the structure described above. Specifically, a subcooling type condenser having a heat exchange section, a receiver section, and a subcooling section can also be used as the condenser in this invention.

[0559] Furthermore, in the above embodiments, various structures were employed for the heat dissipation adjustment section in the high-temperature side heat medium circuit 21, but further different structures could also be used. For example, in the first embodiment described above, the heat dissipation in the radiator 22 and the heat dissipation in the heater core 23 were adjusted by the opening degree of the outlet relative to the radiator 22 and the heater core 23, but this method is not limited to this one.

[0560] Alternatively, the structure can be configured as follows: the heat dissipation in the radiator 22 and the heat dissipation in the heater core 23 can be adjusted by the ratio of the time the outlet is open relative to the radiator 22 and the heater core 23 to the time the outlet is closed. In this case, either a three-way valve like the high-temperature side flow regulating valve 25 in the first embodiment can be used, or a structure in which on- and off valves are respectively configured on the radiator 22 side and the heater core 23 side can be used.

[0561] Furthermore, in the above-described embodiment, the supply air temperature detected by the supply air temperature sensor 52f is used to determine whether the supply air is excessive or insufficient relative to the target temperature, but this method is not limited to this.

[0562] As long as it is a physical quantity related to the temperature of the supply air supplied to the air-conditioned space, the same determination process as described in the above-described implementation can be performed. For example, the temperature of the high-temperature side heat medium at the inlet side of the heater core 23, detected by the third heat medium temperature sensor 53c, can also be used. Alternatively, the refrigerant temperature on the high-pressure side of the heat pump cycle 10 can also be used. Furthermore, the refrigerant pressure on the high-pressure side of the heat pump cycle 10, or the saturation temperature estimated from the refrigerant pressure on the high-pressure side, can also be used.

[0563] Furthermore, while the battery 31 was used as the heating device in the above embodiment, the invention is not limited to this method. Various devices can be used as the heating device in this invention, as long as they are mounted in a vehicle and incidentally generate heat during operation to perform their intended function.

[0564] For example, inverters, electric generators, chargers, and components of advanced driver assistance systems can also be used as heat-generating devices. An inverter is a power conversion unit that converts direct current into alternating current. Furthermore, an electric generator is a device that outputs driving force for travel by being supplied with electricity and generates regenerative electricity during deceleration, etc.

[0565] The charger is a device that charges the battery 31 with electricity. Additionally, the components of an advanced driver assistance system are systems developed to automate, adapt, and enhance vehicle systems for safer and better driving; examples include the control devices of that system.

[0566] While the present invention has been described with reference to embodiments, it should be understood that the invention is not limited to those embodiments or constructions. The invention also includes various modifications and equivalent variations. Furthermore, various combinations, methods, and other combinations and methods comprising only one element, more than one element, or less than one element are also included within the scope and spirit of the invention.

Claims

1. An air conditioning device, characterized in that, have: A heat pump cycle (10) includes a compressor (11), a condenser (12), a pressure reducing unit (14b), and an evaporator (16). The compressor compresses and discharges refrigerant, the condenser condenses the high-pressure refrigerant compressed by the compressor through heat exchange, the pressure reducing unit reduces the pressure of the refrigerant flowing out of the condenser, and the evaporator causes the low-pressure refrigerant after pressure reduction by the pressure reducing unit to evaporate by heat exchange with a low-temperature side heat medium. Heating unit (20), which has a heat exchanger (23) for heating, which heats the air blown into the air-conditioned space using the heat of the high-pressure refrigerant as a heat source; A low-temperature side heat medium circuit (30) is configured to circulate the low-temperature side heat medium that has absorbed heat through heat exchange in the evaporator, and includes: a heating device (31), an outside air heat exchanger (32), and a heat exchange quantity adjustment unit (33). The heating device is configured to be cooled by heat exchange with the low-temperature side heat medium, the outside air heat exchanger allows the low-temperature side heat medium to exchange heat with outside air, and the heat exchange quantity adjustment unit adjusts the heat exchange quantity in the heating device and the heat exchange quantity in the outside air heat exchanger. as well as A heat exchange quantity regulation and control unit (50c) controls the operation of the heat exchange quantity regulation unit. The heat exchange quantity regulation and control unit regulates the heat exchange quantity in the outside air heat exchanger while maintaining the cooling capacity generated by the heat exchange between the heating device and the low-temperature side heat medium, so that the temperature of the supply air heated by the heating heat exchanger is close to the predetermined target temperature (TAO).

2. The air conditioning device according to claim 1, characterized in that, The heat exchange capacity adjustment unit is composed of a flow regulating valve, which continuously adjusts the flow ratio of the low-temperature side heat medium flowing to the heating device and the low-temperature side heat medium flowing to the outside air heat exchanger in the low-temperature side heat medium circuit.

3. The air conditioning device according to claim 1, characterized in that, The heat pump cycle includes: a refrigeration evaporator (15, 15a) connected in parallel with the evaporator to cool the supply air through heat exchange; and a refrigeration pressure reducing unit (14a) disposed on the refrigerant inlet side of the refrigeration evaporator to reduce the pressure of the refrigerant flowing out of the condenser.

4. The air conditioning device according to claim 3, characterized in that, The evaporator for refrigeration is a cold and heat storage exchanger, which is configured to have a cold storage section (15b) that stores the cold and heat of the refrigerant after it has been depressurized by the refrigeration depressurization section, and uses the cold and heat stored in the cold storage section to cool the supply air.

5. The air conditioning device according to claim 3, characterized in that, When the heating device is being cooled, and when the cooling of the supply air begins after the cooling of the supply air has stopped, the opening area ratio after the cooling of the supply air begins is less than the opening area ratio before the cooling of the supply air begins. The opening area ratio is determined by the ratio of the opening area of ​​the pressure reducing unit to the sum of the opening areas of the pressure reducing unit and the opening areas of the cooling pressure reducing unit.

6. The air conditioning device according to claim 3, characterized in that, When the heating device is being cooled, and the cooling of the air supply ends after the cooling of the air supply ends, the opening area ratio after the cooling of the air supply ends is greater than the opening area ratio before the cooling of the air supply ends. The opening area ratio is determined by the ratio of the opening area of ​​the pressure reducing unit to the sum of the opening areas of the pressure reducing unit and the opening areas of the cooling pressure reducing unit.

7. The air conditioning device according to any one of claims 1 to 6, characterized in that, It includes a target temperature setting unit (50d) that sets a target temperature (TAO) related to the temperature of the supply air. When the temperature of the heating device rises during cooling of the heating device and heating of the supply air, the target temperature setting unit lowers the target temperature.

8. The air conditioning device according to any one of claims 1 to 6, characterized in that, It includes a target temperature setting unit (50d) that sets a target temperature (TAO) related to the temperature of the supply air. When the temperature of the heating device reaches or exceeds a predetermined threshold during the cooling of the heating device and the heating of the supply air, the target temperature setting unit lowers the target temperature.

9. The air conditioning device according to any one of claims 1 to 6, characterized in that, It includes a low-temperature side temperature sensor (53d) that detects the temperature of the low-temperature side heat medium flowing out of the evaporator. The low-temperature side temperature sensor is configured such that the internal volume (Vt) of the low-temperature sensor side is smaller than the internal volume (Vb) of the low-temperature side device. The internal volume of the low-temperature sensor side extends from the outlet of the low-temperature side heat medium in the evaporator to the low-temperature side temperature sensor. The internal volume of the low-temperature side device is the internal volume of the heating device through which the low-temperature side heat medium circulates.

10. The air conditioning device according to claim 9, characterized in that, When the volume occupied by the low-temperature side heat medium that flows inside the evaporator in a manner that enables heat exchange with the refrigerant is defined as the evaporator-side internal volume (Vc), The low-temperature side temperature sensor is configured such that the sum of the internal volume of the low-temperature sensor side and the internal volume of the evaporator side is smaller than the internal volume of the low-temperature side device.

11. The air conditioning device according to claim 10, characterized in that, The low-temperature side temperature sensor is configured such that the internal volume of the low-temperature sensor side is smaller than the internal volume of the evaporator side.

12. The air conditioning device according to any one of claims 1 to 6, characterized in that, It includes a device cooling control unit (50e) that performs control related to the cooling of the heat-generating device. When the cooling control unit of the equipment begins to cool the heat-generating equipment, it starts the circulation of the low-temperature side heat medium through the evaporator in the low-temperature side heat medium circuit, and then starts the flow of the refrigerant relative to the evaporator.

13. The air conditioning device according to claim 12, characterized in that, The cooling control unit of the equipment initiates the flow of refrigerant relative to the evaporator by starting the operation of the compressor or by adjusting the flow rate of the refrigerant in the pressure reducing unit.

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