JP2020040429A - Refrigeration cycle device - Google Patents

Abstract

To provide a refrigeration cycle device that achieves both of realization of appropriate temperature adjustment of a temperature adjustment object, and restriction of temperature fluctuation of blast air accompanying the temperature adjustment of the temperature adjustment object.SOLUTION: A refrigeration cycle device includes: a water-refrigerant heat exchanger 12 which constitutes a heating part for heating blast air blown to an air-conditioning object space by using a refrigerant discharged from a compressor as a heat source; a first cooling expansion valve 14b for decompressing the refrigerant flowing out from the water-refrigerant heat exchanger 12; a first chiller 19a performing heat exchange between the refrigerant flowing out from the first cooling expansion valve 14b and a temperature adjustment side heating medium for adjusting the temperature of a battery 80 that is a temperature adjustment object; a second cooling expansion valve 14c for decompressing the refrigerant flowing out from the first chiller 19a; and a second chiller 19b performing heat exchange between the refrigerant flowing out from the second cooling expansion valve 14c and a heat absorption side heating medium. Further, an opening ratio EX1/EX2 of the first cooling expansion valve 14b to the second cooling expansion valve 14c is changed and the temperature of the temperature adjustment side heating medium is changed.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a refrigeration cycle device applied to an air conditioner.

  BACKGROUND ART Conventionally, Patent Document 1 discloses a vapor compression refrigeration cycle device used for temperature control of a secondary battery as a temperature control target.

  The refrigeration cycle device of Patent Literature 1 includes a battery heat exchanger for exchanging heat between a secondary battery and a refrigerant. When warming up the secondary battery, the high-pressure refrigerant discharged from the compressor flows into the battery heat exchanger to heat the secondary battery. Further, when cooling the secondary battery, the refrigerant circuit is switched so as to reverse the flow direction of the refrigerant circulating in the cycle, and the low-pressure refrigerant flows into the battery heat exchanger to cool the secondary battery.

  Patent Document 2 discloses a refrigeration cycle device applied to an air conditioner, which can cool a secondary battery. The refrigeration cycle device of Patent Literature 2 is a heating unit that heats blast air blown to a space to be air-conditioned using a high-pressure refrigerant discharged from a compressor as a heat source, an indoor evaporator that cools blast air by evaporating a low-pressure refrigerant, And a cooling unit for evaporating the low-pressure refrigerant to cool the battery.

  More specifically, the heating unit is connected to a water-refrigerant heat exchanger for exchanging heat between the high-pressure refrigerant and the high-temperature side heat medium, a heater core for exchanging heat between the high-temperature side heat medium and the blown air, and heating the blown air. The high-temperature side heat medium circuit is configured. The cooling unit includes a chiller for exchanging heat between the low-pressure refrigerant and the low-temperature side heat medium, and a low-temperature side to which a heat exchange unit for exchanging heat between the low-temperature side heat medium and the secondary battery and cooling the secondary battery is connected. It is composed of a heat medium circuit.

  Further, in the refrigeration cycle device of Patent Document 2, the chiller and the indoor evaporator are connected in parallel to the flow of the refrigerant.

JP 2014-203736 A JP 2014-37180 A

  By the way, the output of the secondary battery tends to decrease at low temperatures, and the deterioration tends to progress at high temperatures. For this reason, the temperature of the secondary battery needs to be maintained within an appropriate temperature range in which the charge / discharge capacity of the secondary battery can be sufficiently utilized. However, the refrigeration cycle device of Patent Document 2 cannot warm up the secondary battery. Therefore, in the refrigeration cycle device of Patent Document 2, there is a possibility that the temperature of the secondary battery cannot be maintained within an appropriate temperature range.

  On the other hand, in the refrigerating cycle device of Patent Document 2, as in Patent Document 1, it is conceivable to switch the refrigerant circuit to cool and warm up the secondary battery. However, when the refrigerant circuit is switched so as to reverse the flow direction of the refrigerant, the temperature of the refrigerant flowing into the water-refrigerant heat exchanger or the chiller changes suddenly. As a result, appropriate air conditioning of the air-conditioned space cannot be performed.

  In view of the above points, the present invention realizes appropriate temperature adjustment of a temperature adjustment target, and suppresses temperature fluctuation of blast air blown to an air conditioning target space caused by performing temperature adjustment of the temperature adjustment target. It is an object of the present invention to provide a refrigeration cycle device capable of achieving both.

In order to achieve the above object, the invention according to claim 1 is a refrigeration cycle device applied to an air conditioner,
A compressor (11) that compresses and discharges the refrigerant, a heating unit (12, 40) that heats the blast air that is blown into the air-conditioned space using the refrigerant discharged from the compressor as a heat source, and flows out of the heating unit. A first cooling decompression unit (14b) for decompressing the refrigerant, a temperature adjustment unit (19a, 50) for adjusting the temperature of the temperature adjustment target (80) with the refrigerant flowing out of the first cooling decompression unit, and a temperature adjustment A second cooling decompression section (14c) for decompressing the refrigerant flowing out of the section, and a heat absorption section (19b, 60) for cooling the heat absorption target (82) with the refrigerant flowing out of the cooling decompression section,
In the heating temperature adjustment mode in which the heating unit heats the blown air and adjusts the temperature of the temperature adjustment target with the temperature adjustment unit, the first cooling decompression unit with respect to the throttle opening (EX2) of the second cooling decompression unit. This is a refrigeration cycle apparatus that adjusts the temperature of the temperature adjustment target by changing the opening ratio (EX1 / EX2) of the throttle opening (EX1).

  According to this, in the heating temperature control mode, a vapor compression refrigeration cycle is configured in which the heating unit (12, 40) functions as a radiator and the heat absorbing unit (19b, 60) functions as an evaporator. The blast air can be heated in the sections (12, 40). That is, it is possible to heat the space to be air-conditioned.

  Furthermore, by changing the opening degree ratio (EX1 / EX2), it is possible to change the temperature of the refrigerant flowing into the temperature adjusting units (19a, 50). Thereby, cooling or heating of the temperature adjustment target (80) can be performed. That is, appropriate temperature adjustment of the temperature adjustment target (80) can be performed.

  At this time, since it is not necessary to reverse the flow direction of the refrigerant flowing into the heating units (12, 40) and to stop the compressor (11), the heating capacity of the blower air in the heating units (12, 40) is reduced. Fluctuations can be suppressed. Therefore, it is possible to suppress the temperature fluctuation of the blown air heated by the heating units (12, 40).

  That is, according to the first aspect of the present invention, refrigeration that enables both realization of appropriate temperature adjustment of an object to be temperature-controlled and suppression of temperature fluctuation of blast air caused by temperature adjustment of the object to be temperature-controlled. A cycle device can be provided.

  Note that reference numerals in parentheses of each means described in this section and in the claims are examples showing the correspondence with specific means described in the embodiments described later.

1 is an overall configuration diagram of a vehicle air conditioner according to a first embodiment. It is a block diagram which shows the electric control part of the vehicle air conditioner of 1st Embodiment. FIG. 4 is a Mollier chart showing a change in the state of the refrigerant in a cooling mode of the refrigeration cycle device of the first embodiment. FIG. 4 is a Mollier chart showing a change in a state of a refrigerant in a heating / cooling mode of the refrigeration cycle device of the first embodiment. FIG. 4 is a Mollier chart showing a change in a state of a refrigerant in a heating and warming-up mode of the refrigeration cycle device of the first embodiment. It is a time chart which shows the change of the battery temperature and the ventilation air temperature at the time of heating temperature control mode. It is a whole block diagram of the air conditioner for vehicles of 2nd Embodiment. It is a block diagram which shows the electric control part of the air conditioner for vehicles of 2nd Embodiment.

(1st Embodiment)
A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the refrigeration cycle device 10 according to the present invention is applied to a vehicle air conditioner 1 mounted on an electric vehicle that obtains a driving force for traveling from an electric motor. The vehicle air conditioner 1 has a function of performing air conditioning of the vehicle interior, which is a space to be air-conditioned, and a function of adjusting the temperature of the battery 80. For this reason, the vehicle air conditioner 1 can also be called a vehicle air conditioner with a battery temperature adjustment function.

  The battery 80 is a secondary battery that stores electric power supplied to in-vehicle devices such as an electric motor. The battery 80 of the present embodiment is a lithium ion battery. The battery 80 is a so-called assembled battery formed by stacking a plurality of battery cells 81 and electrically connecting these battery cells 81 in series or in parallel.

  The output of such a battery (that is, a secondary battery) tends to decrease when the temperature is low, and deteriorates easily when the temperature is high. For this reason, the temperature of the battery needs to be maintained within an appropriate temperature range (in this embodiment, 10 ° C. or more and 50 ° C. or less) in which the charge / discharge capacity of the battery can be sufficiently utilized. .

  Therefore, in the vehicle air conditioner 1 of the present embodiment, the temperature of the battery 80 is adjusted by the refrigeration cycle device 10 while adjusting the temperature of the blown air blown into the vehicle interior, which is the space to be air-conditioned. Therefore, in the refrigeration cycle device 10 of the present embodiment, the temperature adjustment target different from the blast air is the battery 80.

  Furthermore, in the vehicle air conditioner 1, in addition to the normal air conditioning that is performed when the occupant is in the vehicle, pre-air conditioning that starts air conditioning in the vehicle compartment before the occupant enters the vehicle can be performed. Have been.

  As shown in the overall configuration diagram of FIG. 1, the vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioning unit 30, a high-temperature side heat medium circuit 40, a temperature adjustment side heat medium circuit 50, a heat absorption side heat medium circuit 60, and the like. It has.

  First, the refrigeration cycle device 10 will be described. The refrigeration cycle device 10 is configured to be able to switch the refrigerant circuit according to the operation mode in order to adjust the temperature of the blown air and the temperature of the battery 80.

  In the refrigeration cycle device 10, an HFO-based refrigerant (specifically, R1234yf) is employed as a refrigerant, and a vapor compression subcritical fluid in which the pressure of the refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Constructs a refrigeration cycle. Further, a refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. Part of the refrigerating machine oil circulates through the cycle together with the refrigerant.

  Among the components of the refrigeration cycle device 10, the compressor 11 sucks, compresses, and discharges the refrigerant in the refrigeration cycle device 10. The compressor 11 is disposed in front of a vehicle compartment and is disposed in a drive device compartment in which a traveling electric motor and the like are accommodated. The compressor 11 is an electric compressor in which a fixed displacement compression mechanism having a fixed discharge capacity is rotationally driven by an electric motor. The rotation speed (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from a control device 70 described later.

  The inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the discharge port of the compressor 11. The water-refrigerant heat exchanger 12 has a refrigerant passage through which the high-pressure refrigerant discharged from the compressor 11 flows, and a water passage through which the high-temperature side heat medium circulating through the high-temperature side heat medium circuit 40 flows. The water-refrigerant heat exchanger 12 is a heat exchanging unit that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage to heat the high-temperature heat medium.

  The inflow side of a first three-way joint 13a having three inflow and outflow ports communicating with each other is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12. As such a three-way joint, one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.

  One inlet of the first three-way joint 13a is connected to an inlet of a cooling expansion valve 14a. An inlet side of the first cooling expansion valve 14b is connected to the other outlet of the first three-way joint 13a.

  The cooling expansion valve 14a depressurizes the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 and adjusts the flow rate (mass flow rate) of the refrigerant flowing out to the downstream side at least in the operation mode of cooling the blown air. This is a cooling decompression unit. The cooling expansion valve 14a is configured to include a valve body configured to change the degree of opening of a throttle and an electric actuator (specifically, a stepping motor) that changes the degree of opening of the valve body. This is a variable aperture mechanism.

  The operation of the cooling expansion valve 14a is controlled by a control signal (control pulse) output from the control device 70. Further, the refrigeration cycle device 10 includes a first cooling expansion valve 14b and a second cooling expansion valve 14c, as described later. The basic configuration of the first cooling expansion valve 14b and the second cooling expansion valve 14c is the same as that of the cooling expansion valve 14a.

  The cooling expansion valve 14a, the first cooling expansion valve 14b, and the second cooling expansion valve 14c function as mere refrigerant passages with little or no refrigerant depressurizing action and flow rate adjusting action by fully opening the valve opening. And a fully closing function of closing the refrigerant passage by fully closing the valve opening.

  The cooling expansion valve 14a, the first cooling expansion valve 14b, and the second cooling expansion valve 14c can switch the refrigerant circuit by the fully open function and the fully closed function. Therefore, the cooling expansion valve 14a, the first cooling expansion valve 14b, and the second cooling expansion valve 14c also have a function as a refrigerant circuit switching unit.

  The refrigerant inlet side of the indoor evaporator 18 is connected to the outlet of the cooling expansion valve 14a. The indoor evaporator 18 is arranged in an air-conditioning case 31 of an indoor air-conditioning unit 30 described later. The indoor evaporator 18 blows air by exchanging heat between the low-pressure refrigerant depressurized by the cooling expansion valve 14a and the blast air blown from the blower 32 to evaporate the low-pressure refrigerant and exerting an endothermic effect on the low-pressure refrigerant. This is a heat exchange unit that cools air.

  One inlet side of the second three-way joint 13b is connected to a refrigerant outlet of the indoor evaporator 18. The basic configuration of the second three-way joint 13b is the same as that of the first three-way joint 13a.

  The first cooling expansion valve 14b is a first cooling pressure reducing unit that reduces the pressure of the refrigerant flowing out of the water-refrigerant heat exchanger 12 and adjusts the flow rate of the refrigerant flowing downstream.

  The outlet side of the first cooling expansion valve 14b is connected to the inlet side of the refrigerant passage of the first chiller 19a. The first chiller 19a has a refrigerant passage through which the refrigerant flowing out of the first cooling expansion valve 14b flows, and a water passage through which the temperature adjustment side heat medium circulating through the temperature adjustment side heat medium circuit 50 flows. . The first chiller 19a is a heat exchange unit that exchanges heat between the refrigerant flowing through the refrigerant passage and the temperature adjustment-side heat medium flowing through the water passage to adjust the temperature of the temperature adjustment-side heat medium.

  More specifically, the first chiller 19a functions as a condensing unit that condenses the refrigerant when the temperature of the refrigerant flowing into the refrigerant passage is higher than the temperature control-side heat medium flowing through the water passage. On the other hand, when the temperature of the refrigerant flowing into the refrigerant passage is lower than the temperature control side heat medium flowing through the water passage, the refrigerant functions as an evaporating unit for evaporating the refrigerant.

  The inlet side of the second cooling expansion valve 14c is connected to the outlet of the refrigerant passage of the first chiller 19a. The second cooling expansion valve 14c is a second cooling pressure reducing unit that reduces the pressure of the refrigerant flowing out of the refrigerant passage of the first chiller 19a and adjusts the flow rate of the refrigerant flowing downstream.

  The inlet side of the refrigerant passage of the second chiller 19b is connected to the outlet of the second cooling expansion valve 14c. The basic configuration of the second chiller 19b is the same as that of the first chiller 19a. The second chiller 19b exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage and the heat-absorbing heat medium flowing through the water passage to evaporate the low-pressure refrigerant, and causes the low-pressure refrigerant to exhibit an endothermic effect, thereby forming a heat-absorbing heat medium. This is a heat exchange unit for cooling.

  The other inlet side of the second three-way joint 13b is connected to the outlet of the refrigerant passage of the second chiller 19b.

  The inlet of the evaporation pressure regulating valve 20 is connected to the outlet of the second three-way joint 13b. The evaporation pressure adjusting valve 20 has a function of maintaining the refrigerant evaporation pressure in the indoor evaporator 18 at or above a predetermined reference pressure in order to suppress frost formation on the indoor evaporator 18. The evaporating pressure adjusting valve 20 is configured by a mechanical variable throttle mechanism that increases the valve opening as the pressure of the refrigerant on the outlet side of the indoor evaporator 18 increases.

  As a result, the evaporation pressure regulating valve 20 maintains the refrigerant evaporation temperature in the indoor evaporator 18 at a frost formation suppression temperature (1 ° C. in the present embodiment) capable of suppressing frost formation on the indoor evaporator 18. . Further, the evaporating pressure regulating valve 20 is arranged downstream of the second three-way joint 13b in the refrigerant flow. For this reason, the evaporation pressure regulating valve 20 also maintains the refrigerant evaporation temperature in the second chiller 19b at a temperature equal to or higher than the frost formation suppression temperature.

  An outlet of the evaporating pressure regulating valve 20 is connected to an inlet of an accumulator 21. The accumulator 21 is a gas-liquid separator that separates the gas-liquid of the refrigerant flowing into the inside and stores the surplus liquid-phase refrigerant in the cycle. The suction side of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 21.

  As is clear from the above description, the first three-way joint 13a is a branch portion that branches the flow of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12. Further, the second three-way joint 13 b is a junction where the flow of the refrigerant flowing out of the indoor evaporator 18 and the flow of the refrigerant flowing out of the second chiller 19 b are merged and flow out to the suction side of the compressor 11.

  Next, the high-temperature side heat medium circuit 40 will be described. The high-temperature-side heat medium circuit 40 is a heat medium circulation circuit that circulates the high-temperature-side heat medium. As the high-temperature side heat medium, ethylene glycol, dimethylpolysiloxane, a solution containing a nanofluid, or the like, an antifreeze, or the like can be used. The high-temperature heat medium circuit 40 includes a water passage of the water-refrigerant heat exchanger 12, a high-temperature heat medium pump 41, a heater core 42, a high-temperature three-way valve 43, a high-temperature radiator 44, and the like.

  The high-temperature side heat medium pump 41 is a water pump that pumps the high-temperature side heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12. The high-temperature side heat medium pump 41 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 70.

  The outlet of the water passage of the water-refrigerant heat exchanger 12 is connected to the heat medium inlet side of the heater core 42. The heater core 42 is a heat exchanger that heats the blown air by exchanging heat between the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 18. The heater core 42 is arranged inside the air conditioning case 31 of the indoor air conditioning unit 30.

  The inflow side of the high-temperature three-way valve 43 is connected to the heat medium outlet of the heater core 42. The high temperature side three-way valve 43 is an electric three-way flow control valve having one inlet and two outlets and capable of continuously adjusting the passage area ratio of the two outlets. The operation of the high-temperature side three-way valve 43 is controlled by a control signal output from the control device 70.

  The heat medium inlet side of the high-temperature side radiator 44 is connected to one outlet of the high-temperature side three-way valve 43. The suction port side of the high-temperature side heat medium pump 41 is connected to the other outlet of the high-temperature side three-way valve 43. Accordingly, the high-temperature side three-way valve 43 determines the flow rate of the high-temperature side heat medium flowing out of the heater core 42 into the high-temperature side radiator 44 and the flow rate of the high-temperature side heat medium pump 41 bypassing the high-temperature side radiator 44 and sucking into the high-temperature side heat medium pump 41. Performs the function of adjusting the flow ratio.

  The high-temperature side radiator 44 is a heat exchanger that exchanges heat between the high-temperature side heat medium flowing out of the heater core 42 and the outside air blown by an outside air fan (not shown), and radiates heat of the high-temperature side heat medium to the outside air.

  The high-temperature side radiator 44 is disposed on the front side in the drive device chamber. Therefore, when the vehicle is traveling, the traveling wind can be applied to the high-temperature side radiator 44. The heat medium outlet of the high temperature radiator 44 is connected to the suction port side of the high temperature heat medium pump 41.

  Accordingly, in the high-temperature side heat medium circuit 40, the control device 70 operates the high-temperature side heat medium pump 41, so that the refrigerant discharged from the compressor 11 in the water-refrigerant heat exchanger 12 and the high-temperature side heat medium are separated. The high-temperature side heat medium can be heated by heat exchange. Further, in the heater core 42, the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12 and the blown air can be heat-exchanged to heat the blown air.

  In other words, in the present embodiment, the heating unit that heats the blast air is configured by the respective components of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40, using the refrigerant discharged from the compressor 11 as a heat source. I have.

  Next, the temperature adjustment-side heat medium circuit 50 will be described. The temperature adjustment-side heat medium circuit 50 is a heat medium circulation circuit that circulates the temperature adjustment-side heat medium. The same fluid as the high-temperature-side heat medium can be used as the temperature-adjustment-side heat medium. In the temperature adjustment-side heat medium circuit 50, a water passage of the first chiller 19a, a temperature adjustment-side heat medium pump 51, a temperature adjustment heat exchange section 52, and the like are arranged.

  The temperature adjustment-side heat medium pump 51 is a water pump that pressure-feeds the temperature adjustment-side heat medium to the inlet side of the water passage of the first chiller 19a. The basic configuration of the temperature adjustment side heat medium pump 51 is the same as that of the high temperature side heat medium pump 41.

  The inlet side of the temperature adjusting heat exchange section 52 is connected to the outlet of the water passage of the first chiller 19a. The temperature-adjusting heat exchanging section 52 has a plurality of heat medium passages formed by metal plates arranged to be in contact with a plurality of battery cells 81 forming the battery 80. The heat exchange unit is a heat exchange unit that adjusts the temperature of the battery 80 by exchanging heat between the battery cell 81 and the temperature control heat medium flowing through the heat medium flow path.

  As such a temperature-adjusting heat exchange unit 52, a unit in which a heat medium flow path is arranged between the battery cells 81 arranged in a stack may be adopted. Further, the temperature-adjusting heat exchange section 52 may be formed integrally with the battery 80. For example, the battery case may be formed integrally with the battery 80 by providing a heat medium flow path in a dedicated case for accommodating the stacked battery cells 81. The outlet of the temperature control heat exchange unit 52 is connected to the suction port side of the temperature control-side heat medium pump 51.

  Therefore, in the temperature-adjustment-side heat medium circuit 50, the controller 70 operates the temperature-adjustment-side heat medium pump 51, so that the refrigerant flowing out of the first cooling expansion valve 14b in the first chiller 19a and the temperature adjustment-side heat By exchanging heat with the medium, the temperature of the temperature adjusting-side heat medium can be adjusted. Further, in the temperature-adjusting heat exchanging section 52, the temperature of the battery 80 can be adjusted by exchanging heat between the temperature-adjusted heat medium whose temperature has been adjusted and the battery 80.

  That is, in the present embodiment, the respective components of the first chiller 19a and the temperature adjustment-side heat medium circuit 50 constitute a temperature adjustment unit that adjusts the temperature of the battery 80 by the refrigerant flowing out of the first cooling expansion valve 14b. ing. The temperature adjustment-side heat medium is a temperature adjustment-side heat medium, and the temperature adjustment-side heat medium circuit 50 is a temperature adjustment-side heat medium circuit that circulates the temperature adjustment-side heat medium.

  Next, the heat absorption side heat medium circuit 60 will be described. The heat absorption side heat medium circuit 60 is a heat medium circulation circuit that circulates the heat absorption side heat medium. As the heat absorbing side heat medium, the same fluid as the high temperature side heat medium can be adopted. The heat absorption side heat medium circuit 60 includes a water passage of the second chiller 19 b, a heat absorption side heat medium pump 61, a cooling water passage formed in a vehicle-mounted device 82 that generates heat during operation, a heat absorption side three-way valve 63, a heat absorption side radiator 64, and the like. Is arranged.

  The heat absorption side heat medium pump 61 is a water pump that pumps the heat absorption side heat medium to the inlet side of the water passage of the second chiller 19b. The basic configuration of the temperature adjustment side heat medium pump 51 is the same as that of the high temperature side heat medium pump 41.

  The inlet side of the cooling water passage of the vehicle-mounted device 82 is connected to the outlet of the water passage of the second chiller 19b. The on-vehicle device 82 is a heat-absorbing target that causes the refrigerant of the refrigeration cycle device 10 to absorb heat generated during operation. As such an in-vehicle device, an electric motor that outputs driving force for traveling, an inverter that converts the frequency of electric power supplied to the electric motor, a charger that charges the battery 80 with electric power, and the like can be used. .

  The inlet of the heat-absorbing three-way valve 63 is connected to the inlet of the cooling water passage of the vehicle-mounted device 82. The basic configuration of the heat absorption side three-way valve 63 is the same as that of the high temperature side three-way valve 43.

  The heat medium inlet side of the heat absorbing radiator 64 is connected to one outlet of the heat absorbing side three-way valve 63. The other outlet of the three-way valve 63 on the heat absorption side is connected to the suction port side of the heat medium pump 61 on the heat absorption side. Accordingly, the heat-absorbing side three-way valve 63 supplies the heat-absorbing-side heat medium pump 61 to the heat-absorbing-side heat medium pump 61 by bypassing the heat-absorbing-side radiator 64 and the flow rate of the heat-absorbing-side heat medium flowing out of the cooling water passage of the vehicle-mounted device 82. It has the function of adjusting the flow ratio with the flow to be sucked.

  The heat-absorbing radiator 64 exchanges heat between the refrigerant flowing out of the cooling water passage of the on-vehicle equipment 82 and the outside air blown by an outside air fan (not shown), and radiates the heat of the temperature-adjusting heat medium to the outside air. It is.

  The heat-absorbing-side radiator 64 is disposed on the front side in the drive device chamber. Therefore, during traveling of the vehicle, traveling wind can be applied to the heat absorbing radiator 64. Therefore, the heat-absorbing radiator 64 may be formed integrally with the high-temperature radiator 44. The suction medium side of the heat absorption side heat medium pump 61 is connected to the heat medium outlet of the heat absorption side radiator 64.

  Therefore, in the heat absorbing side heat medium circuit 60, the control device 70 operates the heat absorbing side heat medium pump 61, so that the refrigerant flowing out of the second cooling expansion valve 14c and the heat absorbing side heat medium in the second chiller 19b. Heat is exchanged, and the refrigerant is evaporated to cool the heat absorbing side heat medium. Further, by flowing the cooled heat absorbing side heat medium through the cooling water passage of the vehicle-mounted device 82, the vehicle-mounted device 82 can be cooled.

  That is, in the present embodiment, each component of the second chiller 19b and the heat absorbing side heat medium circuit 60 constitutes a heat absorbing portion that evaporates the refrigerant flowing out of the second cooling expansion valve 14c and cools the vehicle-mounted device 82. ing.

  Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 blows out the blast air whose temperature has been adjusted by the refrigeration cycle device 10 into the vehicle interior. The indoor air-conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the forefront of the vehicle interior.

  As shown in FIG. 1, the indoor air-conditioning unit 30 accommodates a blower 32, an indoor evaporator 18, a heater core 42, and the like in an air passage formed in an air-conditioning case 31 forming an outer shell thereof.

  The air-conditioning case 31 forms an air passage for blowing air blown into the vehicle interior. The air-conditioning case 31 has a certain degree of elasticity and is formed of a resin (for example, polypropylene) having excellent strength. An inside / outside air switching device 33 is disposed on the most upstream side of the airflow of the air conditioning case 31. The inside / outside air switching device 33 switches between the inside air (vehicle interior air) and the outside air (vehicle outside air) into the air conditioning case 31.

  The inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port for introducing the inside air into the air conditioning case 31 and the outside air introduction port for introducing the outside air by the inside / outside air switching door, and the inside air introduction air volume and the outside air. Is to change the rate of introduction with the amount of air introduced. The inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door. The operation of the electric actuator is controlled by a control signal output from the control device 70.

  A blower 32 is arranged downstream of the inside / outside air switching device 33 with respect to the flow of the blown air. The blower 32 blows the air taken in through the inside / outside air switching device 33 toward the vehicle interior. The blower 32 is an electric blower that drives a centrifugal multi-blade fan with an electric motor. The rotation speed (that is, the blowing capacity) of the blower 32 is controlled by the control voltage output from the control device 70.

  On the downstream side of the blown air flow of the blower 32, the indoor evaporator 18 and the heater core 42 are arranged in this order with respect to the blown air flow. That is, the indoor evaporator 18 is arranged on the upstream side of the flow of the blown air from the heater core 42.

  In the air-conditioning case 31, a cool air bypass passage 35 is provided in which the air blown after passing through the indoor evaporator 18 bypasses the heater core 42. An air mix door 34 is arranged on the downstream side of the blown air flow of the indoor evaporator 18 in the air conditioning case 31 and on the upstream side of the blown air flow of the heater core 42.

  The air mix door 34 adjusts a flow rate ratio of a flow rate of the blown air passing through the heater core 42 and a flow rate of the blown air passing through the cool air bypass passage 35 among the blown air after passing through the indoor evaporator 18. Department. The air mix door 34 is driven by an electric actuator for the air mix door. The operation of the electric actuator is controlled by a control signal output from the control device 70.

  A mixing space is arranged in the air-conditioning case 31 on the downstream side of the air flow of the heater core 42 and the cool air bypass passage 35. The mixing space is a space for mixing the blast air heated by the heater core 42 and the blast air that has not passed through the cool air bypass passage 35 and is not heated.

  Further, an opening hole for blowing out the blast air mixed in the mixing space (that is, the conditioned air) into the vehicle interior, which is a space to be air-conditioned, is arranged downstream of the airflow of the air-conditioning case 31.

  As the opening, a face opening, a foot opening, and a defroster opening (all not shown) are provided. The face opening hole is an opening hole for blowing out conditioned air toward the upper body of the occupant in the passenger compartment. The foot opening hole is an opening hole for blowing out conditioned air toward the feet of the occupant. The defroster opening hole is an opening hole for blowing out conditioned air toward the inner surface of the vehicle front window glass.

  The face opening, the foot opening, and the defroster opening are respectively formed by a face opening, a foot opening, and a defroster opening provided in the vehicle cabin through ducts forming air passages. )It is connected to the.

  Therefore, the temperature of the conditioned air mixed in the mixing space is adjusted by adjusting the air flow ratio of the air flow passing through the heater core 42 and the air flow passing through the cool air bypass passage 35 by the air mix door 34. Then, the temperature of the blown air (conditioned air) blown out from each outlet into the vehicle interior is adjusted.

  Further, a face door, a foot door, and a defroster door (all not shown) are arranged on the upstream side of the blown air flow from the face opening hole, the foot opening hole, and the defroster opening hole. The face door adjusts the opening area of the face opening hole. The foot door adjusts the opening area of the foot opening hole. The defroster door is for adjusting the opening area of the froster opening hole.

  These face door, foot door, and defroster door constitute an outlet mode switching device that switches the outlet mode. These doors are connected to an electric actuator for driving the outlet mode door via a link mechanism or the like, and are rotated in conjunction therewith. The operation of this electric actuator is also controlled by a control signal output from the control device 70.

  Specific examples of the outlet mode switched by the outlet mode switching device include a face mode, a bi-level mode, and a foot mode.

  The face mode is an outlet mode in which the face outlet is fully opened and air is blown from the face outlet toward the upper body of the occupant in the vehicle. The bi-level mode is an air outlet mode in which both the face air outlet and the foot air outlet are opened to blow air toward the upper body and feet of the occupant in the vehicle. The foot mode is an outlet mode in which the foot outlet is fully opened, the defroster outlet is opened by a small opening, and air is mainly blown out from the foot outlet.

  Further, the occupant can switch to the defroster mode by manually operating the blowout mode changeover switch provided on the operation panel 701. The defroster mode is an outlet mode in which the defroster outlet is fully opened and air is blown from the defroster outlet to the inner surface of the windshield.

  Next, an outline of the electric control unit of the present embodiment will be described. The control device 70 includes a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and its peripheral circuits. Then, various calculations and processes are performed based on the air-conditioning control program stored in the ROM, and various control target devices 11, 14a to 14c, 32, 41, 43, 51, 61, 63 connected to the output side. And the like.

  On the input side of the control device 70, as shown in the block diagram of FIG. 2, an inside air temperature sensor 71, an outside air temperature sensor 72, a solar radiation sensor 73, first to third refrigerant temperature sensors 74a to 74c, an evaporator temperature. Sensor 74f, first and second refrigerant pressure sensors 75a and 75b, high-temperature side heat medium temperature sensor 76a, temperature adjustment side heat medium temperature sensor 76b, heat absorption side heat medium temperature sensor 76c, battery temperature sensor 78, air conditioning air temperature sensor 79 Etc. are connected. Then, the detection signals of these sensor groups are input to the control device 70.

  The internal air temperature sensor 71 is an internal air temperature detecting unit that detects a vehicle interior temperature (internal air temperature) Tr. The outside air temperature sensor 72 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam. The solar radiation sensor 73 is a solar radiation amount detecting unit that detects the amount of solar radiation Ts emitted to the vehicle interior.

  The first refrigerant temperature sensor 74a is a first refrigerant temperature detector that detects the temperature T1 of the refrigerant discharged from the compressor 11. The second refrigerant temperature sensor 74b is a second refrigerant temperature detecting unit that detects the temperature T2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12. The third refrigerant temperature sensor 74c is a third refrigerant temperature detector that detects the temperature T3 of the refrigerant flowing out of the refrigerant passage of the second chiller 19b.

  The evaporator temperature sensor 74f is an evaporator temperature detector that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18. Specifically, the evaporator temperature sensor 74f of the present embodiment detects the heat exchange fin temperature of the indoor evaporator 18.

  The first refrigerant pressure sensor 75a is a first refrigerant pressure detecting unit that detects the pressure P1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12. The second refrigerant pressure sensor 75b is a second refrigerant pressure detector that detects the pressure P2 of the refrigerant flowing out of the refrigerant passage of the second chiller 19b.

  The high-temperature heat medium temperature sensor 76a detects a high-temperature heat medium temperature TWH that is the temperature of the high-temperature heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 and flowing into the heater core 42. It is a detection unit.

  The temperature adjustment-side heat medium temperature sensor 76b detects the temperature adjustment-side heat medium temperature TWC1, which is the temperature of the temperature adjustment-side heat medium flowing out of the water passage of the first chiller 19a and flowing into the temperature adjustment heat exchange section 52. It is a temperature adjusting-side heat medium temperature detecting section.

  The heat absorption side heat medium temperature sensor 76c detects the heat absorption side heat medium temperature TWC2 which is the temperature of the heat absorption side heat medium flowing out of the water passage of the second chiller 19b and flowing into the cooling water passage of the vehicle-mounted device 82. It is a medium temperature detecting unit.

  The battery temperature sensor 78 is a battery temperature detection unit that detects a battery temperature TB that is the temperature of the battery 80. The battery temperature sensor 78 of the present embodiment has a plurality of temperature sensors and detects temperatures at a plurality of locations of the battery 80. Therefore, the control device 70 can also detect the temperature difference between the components of the battery 80. Further, as the battery temperature TB, an average value of detection values of a plurality of temperature sensors is employed.

  The air-conditioning air temperature sensor 79 is an air-conditioning air temperature detecting unit that detects the temperature of the air blown from the mixing space into the vehicle compartment TAV.

  Further, an input panel of the control device 70 is connected to an operation panel 701 disposed near the instrument panel in the front of the vehicle cabin, and receives input of operation signals from various operation switches provided on the operation panel 701. Various operation switches provided on the operation panel 701 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, a blowout mode switching switch, and the like.

  The auto switch is an operation unit for setting or canceling the automatic air-conditioning operation. The air conditioner switch is an operation unit for requesting that the blown air be cooled by the indoor evaporator 18. The air volume setting switch is an operation unit for manually setting the air volume of the blower 32. Temperature setting switch This is an operation unit for setting a target temperature Tset in the passenger compartment. This is an operation unit for manually setting the blowout mode.

  Note that the control device 70 of the present embodiment is configured such that a control unit that controls various control target devices connected to the output side thereof is integrally configured. However, the control device 70 controls the operation of each control target device. Hardware and software) constitute a control unit that controls the operation of each device to be controlled.

  For example, of the control device 70, a configuration that controls the refrigerant discharge capacity of the compressor 11 (specifically, the number of revolutions of the compressor 11) constitutes a compressor control unit 70a. The configuration for controlling the operations of the cooling expansion valve 14a, the first cooling expansion valve 14b, the second cooling expansion valve 14c, and the like constitutes a pressure reducing unit control unit 70b.

  Next, the operation of the present embodiment in the above configuration will be described. The vehicle air conditioner 1 according to the present embodiment has a function of performing air conditioning of the vehicle interior and a function of adjusting the temperature of the battery 80. Therefore, in the refrigeration cycle apparatus 10, the refrigerant circuit is switched to switch between operation modes such as a cooling temperature control mode, a heating temperature control mode, a single cooling mode, a single warming mode, a single cooling mode, and a single heating mode.

  The cooling temperature control mode is an operation mode for cooling the blast air and cooling the temperature of the battery 80 in order to perform cooling of the vehicle interior. The cooling temperature control mode includes a cooling cooling mode for cooling the blast air and cooling the battery 80, and a cooling warming mode for cooling the blast air and heating the battery 80 to warm it up.

  The heating temperature control mode is an operation mode in which the blast air is heated to heat the vehicle interior and the temperature of the battery 80 is adjusted. The heating temperature control mode includes a heating / cooling mode in which the blast air is heated and the battery 80 is cooled, and a heating and warming mode in which the blast air is heated and the battery 80 is heated to warm up.

  The single cooling mode is an operation mode in which the battery 80 is cooled without adjusting the temperature of the blown air. The single warm-up mode is an operation mode in which the battery 80 is heated and warmed up without adjusting the temperature of the blown air.

  The single cooling mode is an operation mode in which the blown air is cooled in order to perform cooling in the vehicle compartment without adjusting the temperature of the battery 80. The single heating mode is an operation mode in which the blast air is heated in order to heat the vehicle interior without adjusting the temperature of the battery 80.

  Switching between these operation modes is performed by executing a control program stored in the control device 70 in advance. In this control program, the detection signal of the above-described sensor group and the operation signal of the operation panel 701 are read every predetermined control cycle. Then, the target blowing temperature TAO of the blown air blown into the vehicle compartment is determined using the read detection signal and operation signal.

Specifically, the target outlet temperature TAO is calculated by the following equation F1.
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × Ts + C (F1)
Tset is a vehicle interior set temperature set by the temperature setting switch. Tr is a vehicle interior temperature detected by the inside air sensor. Tam is the vehicle outside temperature detected by the outside air sensor. Ts is the amount of solar radiation detected by the solar radiation sensor. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

  Further, in the control program, the operation mode is switched based on the target outlet temperature TAO, the battery temperature TB detected by the battery temperature sensor 78, the operation signal of the operation panel 701, and the like.

  Specifically, when the automatic air-conditioning operation is set by operating the auto switch and the air-conditioning switch is turned on and the outside temperature Tam is equal to or higher than the predetermined reference cooling temperature Kα, the cooling temperature Operate in tuning mode. In the cooling temperature control mode, when the battery temperature TB becomes equal to or higher than a predetermined reference upper limit temperature KTBH (40 ° C. in the present embodiment), the mode is switched to the cooling cooling mode. When the battery temperature TB becomes equal to or lower than a predetermined reference lower limit temperature KTBL (20 ° C. in the present embodiment), the mode is switched to the cooling / warm-up mode.

  If the air conditioner switch is not turned on and the outside temperature Tam is equal to or lower than the predetermined reference heating temperature Kβ in a state where the automatic air conditioning operation is set by operating the auto switch, the heating temperature control mode is set. Driving at. In the heating temperature control mode, when the battery temperature TB becomes equal to or higher than the reference upper limit temperature KTBH, the mode is switched to the heating / cooling mode. When the battery temperature TB falls below the reference lower limit temperature KTBL, the mode is switched to the heating warm-up mode.

  When the air conditioning in the vehicle compartment is not performed, such as when the automatic air-conditioning operation is canceled by the operation of the auto switch, the operation is performed in the single temperature control mode. In the single temperature control mode, when the battery temperature TB becomes equal to or higher than the reference upper limit temperature KTBH, the mode is switched to the single cooling mode. When the battery temperature TB becomes equal to or lower than the reference lower limit temperature KTBL, the mode is switched to the single warm-up mode.

  Here, it is desirable that the temperature of the battery 80 is always maintained within an appropriate temperature range when the vehicle system is activated, regardless of whether or not the vehicle compartment is air-conditioned. For this reason, when the vehicle system is activated, the refrigeration cycle device 10 operates in the operation mode in which the temperature of the battery 80 can be adjusted (in the present embodiment, the cooling temperature adjustment mode, the heating temperature adjustment mode, the individual cooling mode). Mode, or a single warm-up mode).

  Therefore, in the control program of the present embodiment, when the predetermined operation condition is satisfied, the operation is switched to the single cooling mode and the single warm-up mode. Hereinafter, the detailed operation of each operation mode will be described.

(1) Cooling Temperature Control Mode In the cooling temperature control mode, the control device 70 sets the cooling expansion valve 14a, the first cooling expansion valve 14b, and the second cooling expansion valve 14c to the throttle state in which the refrigerant depressurizes. I do. Further, the control device 70 operates the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping capacity for the cooling temperature control mode. Control.

  Further, the control device 70 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows out to the inlet side of the high-temperature side radiator 44.

  Further, the control device 70 controls the operation of the heat-absorbing three-way valve 63 so that the vehicle-mounted device 82 is cooled to an appropriate temperature. More specifically, the operation of the heat-absorbing three-way valve 63 is controlled such that the heat-absorbing-side heat medium temperature TWC2 detected by the heat-absorbing-side heat medium temperature sensor 76c approaches a predetermined reference heat-absorbing-side heat medium temperature KTWC2. .

  Thereby, in the refrigeration cycle apparatus 10 in the cooling temperature control mode, the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the first three-way joint 13a → the cooling expansion valve 14a → the indoor evaporator 18 → the second three-way joint 13b → evaporation pressure regulating valve 20 → accumulator 21 → refrigerant circulates in the order of compressor 11 suction port, compressor 11 discharge port → water-refrigerant heat exchanger 12 → first three-way joint 13a → first cooling Refrigeration in which the refrigerant circulates in the order of expansion valve 14b → first chiller 19a → second cooling expansion valve 14c → second chiller 19b → second three-way joint 13b → evaporation pressure regulating valve 20 → accumulator 21 → compressor 11 suction port. A cycle is configured.

  In other words, in the refrigeration cycle apparatus 10 in the cooling temperature control mode, the refrigerant flows in the order of the cooling expansion valve 14a → the indoor evaporator 18, and the first cooling expansion valve 14b → the first chiller 19a → the second cooling expansion. The path in which the refrigerant flows in the order of the valve 14c and the second chiller 19b is switched to a refrigerant circuit connected in parallel with the refrigerant flow.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device. For example, for the compressor 11, the rotation speed (that is, the refrigerant discharge capacity) is controlled such that the evaporator temperature Tefin detected by the evaporator temperature sensor 74f approaches the target evaporator temperature TEO.

  The target evaporator temperature TEO is determined based on the target outlet temperature TAO with reference to a control map stored in the control device 70 in advance. In this control map, the target evaporator temperature TEO is determined to decrease as the target outlet temperature TAO decreases.

  The throttle opening of the cooling expansion valve 14a is controlled such that the supercooling degree SC1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO1.

  The degree of supercooling SC1 is calculated from the temperature T2 detected by the second refrigerant temperature sensor 74b and the pressure P1 detected by the first refrigerant pressure sensor 75a. The target degree of subcooling SCO1 is determined based on the outside temperature Tam with reference to a control map stored in the control device 70 in advance. In this control map, the target degree of supercooling SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

  Further, the first cooling expansion valve 14b and the second cooling expansion valve 14c are set so that the superheat degree SHC2 of the refrigerant flowing out of the refrigerant passage of the second chiller 19b approaches the target superheat degree SHCO2. The throttle opening EX1 of the valve 14b and the throttle opening EX2 of the second cooling expansion valve 14c are controlled.

  The superheat degree SHC2 is calculated from the temperature T3 detected by the third refrigerant temperature sensor 74c and the pressure P2 detected by the second refrigerant pressure sensor 75b. As the target superheat degree SHCO2, a predetermined constant (5 ° C. in the present embodiment) can be adopted.

  Further, the control device 70 opens and closes the second cooling expansion valve 14c so that the temperature-adjustment-side heat medium temperature TWC1 detected by the temperature-adjustment-side heat medium temperature sensor 76b approaches the target temperature adjustment-side heat medium temperature TWCO1. The opening ratio EX1 / EX2 of the throttle opening EX1 of the first cooling expansion valve 14b to the degree EX2 is adjusted.

  The target temperature adjustment-side heat medium temperature TWCO1 is determined based on the battery temperature TB with reference to a control map stored in the control device 70 in advance. In this control map, the target temperature adjustment-side heat medium temperature TWCO1 is determined to decrease as the battery temperature TB increases. Therefore, control device 70 decreases opening degree ratio EX1 / EX2 as battery temperature TB increases.

  At this time, in the cooling / cooling mode, the target temperature adjustment-side heat medium temperature TWCO1 is determined to be lower than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a. Further, in the cooling / warm-up mode, the target temperature adjustment-side heat medium temperature TWCO1 is determined to be higher than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a.

In addition, the actuator for the air mix door is controlled so that the opening of the air mix door 34 is equal to the opening SW determined using the following equation F2.
SW = {TAO- (Tefin + C2)} / {TWH- (Tefin + C2)}
… (F2)
TWH is the high-temperature-side heat medium temperature detected by the high-temperature-side heat medium temperature sensor 76a. C2 is a control constant. As for the opening degree of the air mix door 34, the passage area of the passage on the heater core 42 side increases as the SW increases. On the other hand, as the SW becomes smaller, the passage area on the side of the cool air bypass passage 35 increases.

  Therefore, in the refrigeration cycle device 10 in the cooling cooling mode, the state of the refrigerant changes as shown in the Mollier diagram of FIG. That is, the refrigerant (point a3 in FIG. 3) discharged from the compressor 11 flows into the refrigerant passage of the water-refrigerant heat exchanger 12, and exchanges heat with the high-temperature side heat medium flowing through the water passage to radiate heat. (Point a3 → point b3 in FIG. 3). Thus, the high-temperature side heat medium flowing through the water passage of the water-refrigerant heat exchanger 12 is heated.

  In the high-temperature side heat medium circuit 40, the high-temperature side heat medium heated in the water passage of the water-refrigerant heat exchanger 12 flows into the heater core 42. The high-temperature side heat medium that has flowed into the heater core 42 exchanges heat with the blast air cooled by the indoor evaporator 18 and radiates heat. As a result, the air blown into the vehicle compartment is heated, and the temperature of the blown air approaches the target blowing temperature TAO.

  The high-temperature side heat medium flowing out of the heater core 42 flows into the high-temperature side radiator 44 via the high-temperature side three-way valve 43. The high-temperature side heat medium that has flowed into the high-temperature side radiator 44 exchanges heat with the outside air and radiates heat. The high-temperature-side heat medium radiated by the high-temperature-side radiator 44 is sucked into the high-temperature-side heat medium pump 41 and is again pressure-fed to the water passage of the water-refrigerant heat exchanger 12.

  The flow of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is branched at the first three-way joint 13a. One refrigerant branched at the first three-way joint 13a flows into the cooling expansion valve 14a and is decompressed (point b3 → point c3 in FIG. 3). The refrigerant decompressed by the cooling expansion valve 14a flows into the indoor evaporator 18 and evaporates by exchanging heat with the air blown from the blower 32 (point c3 → point d3 in FIG. 3). As a result, the blown air is cooled by the indoor evaporator 18.

  The refrigerant flowing out of the indoor evaporator 18 flows into the second three-way joint 13b and merges with the refrigerant flowing out of the refrigerant passage of the second chiller 19b (point d3 → point i3 in FIG. 3).

  On the other hand, the other refrigerant branched at the first three-way joint 13a flows into the first cooling expansion valve 14b and is decompressed (point b3 → point e3 in FIG. 3). In the cooling cooling mode, the saturation temperature of the refrigerant decompressed by the first cooling expansion valve 14b becomes lower than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a.

  For this reason, the refrigerant decompressed by the first cooling expansion valve 14b flows into the refrigerant passage of the first chiller 19a, exchanges heat with the temperature control side heat medium flowing through the water passage, and evaporates (FIG. 3). E3 point → f3 point). Thereby, the temperature control side heat medium flowing through the water passage of the first chiller 19a is cooled.

  In the temperature control side heat medium circuit 50, the temperature control side heat medium cooled in the water passage of the first chiller 19a flows into the temperature control heat exchange unit 52 and exchanges heat with the battery 80. Thereby, battery 80 is cooled, and the temperature of battery 80 is maintained within an appropriate temperature range. The temperature-adjustment-side heat medium that has flowed out of the temperature-adjustment heat exchange unit 52 is sucked into the temperature-adjustment-side heat medium pump 51, and is again pressure-fed to the water passage of the first chiller 19a.

  The refrigerant flowing out of the refrigerant passage of the first chiller 19a flows into the second cooling expansion valve 14c and is decompressed (point f3 → point g3 in FIG. 3). The refrigerant decompressed by the second cooling expansion valve 14c flows into the refrigerant passage of the second chiller 19b, and exchanges heat with the heat absorbing heat medium flowing through the water passage to evaporate (point g3 in FIG. 3 →). h3 point). Thereby, the heat absorbing heat medium flowing through the water passage of the second chiller 19b is cooled.

  In the heat absorbing side heat medium circuit 60, the heat absorbing side heat medium cooled in the water passage of the second chiller 19b flows through the cooling water passage of the vehicle mounted device 82, so that the vehicle mounted device 82 is cooled. Of the heat-absorbing heat medium that has flowed out of the cooling water passage of the vehicle-mounted device 82, the heat-absorbing heat medium that has flowed into the heat-absorbing radiator 64 via the heat-absorbing three-way valve 63 exchanges heat with the outside air. Thereby, the waste heat of the vehicle-mounted device 82 is radiated to the outside air.

  The refrigerant flowing out of the refrigerant passage of the second chiller 19b flows into the second three-way joint 13b and merges with the refrigerant flowing out of the indoor evaporator 18 (point d3 → point i3, point h3 → point i3 in FIG. 3). . The refrigerant flowing out of the second three-way joint 13b flows into the accumulator 21 via the evaporation pressure adjusting valve 20. The gas-phase refrigerant separated by the accumulator 21 is sucked into the compressor 11 and compressed again (point i3 → point a3 in FIG. 3).

  As described above, in the refrigeration cycle apparatus 10 in the cooling / cooling mode, the vapor compression in which the water-refrigerant heat exchanger 12 functions as a radiator and the indoor evaporator 18, the first chiller 19a, and the second chiller 19b function as evaporators. The refrigerating cycle of the formula is constituted.

  Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. In addition, the blown air can be cooled by the indoor evaporator 18. Further, the first chiller 19a can cool the heat medium on the temperature adjustment side. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  As a result, in the vehicle air conditioner 1 in the cooling cooling mode, a part of the air blown by the indoor evaporator 18 can be reheated by the heater core 42 by adjusting the opening of the air mix door 34. Then, the inside of the vehicle compartment can be cooled by blowing out the blast air whose temperature has been adjusted so as to approach the target outlet temperature TAO by the heater core 42 into the vehicle compartment.

  In addition, the heat absorbing side heat medium cooled by the second chiller 19b flows into the cooling water passage of the vehicle-mounted device 82, so that the vehicle-mounted device 82 can be cooled.

  Further, the battery 80 can be cooled by flowing the temperature-adjusting-side heat medium cooled by the first chiller 19a into the temperature-adjusting heat exchange unit 52. At this time, the control device 70 adjusts the opening ratio EX1 / EX2 according to the battery temperature TB. Therefore, the temperature of the refrigerant flowing into the first chiller 19a can be appropriately changed, and the temperature of the battery 80 can be maintained within an appropriate temperature range.

  That is, the control device 70 appropriately adjusts the cooling capacity exerted by the first chiller 19a and the cooling capacity exerted by the second chiller 19b by adjusting the opening degree ratio EX1 / EX2. Can be. In other words, the cooling capacity that can be exhibited by the refrigeration cycle device 10 can be appropriately distributed to the first chiller 19a and the second chiller 19b.

  Further, in the refrigeration cycle apparatus 10 in the cooling / warm-up mode, the saturation temperature of the refrigerant depressurized by the first cooling expansion valve 14b is higher than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a. Get higher. Accordingly, the refrigerant decompressed by the first cooling expansion valve 14b flows into the refrigerant passage of the first chiller 19a, and exchanges heat with the temperature control side heat medium flowing through the water passage to radiate heat. Thereby, the temperature adjustment-side heat medium flowing through the water passage of the first chiller 19a is heated.

  In the temperature-adjustment-side heat medium circuit 50, the temperature-adjustment-side heat medium heated in the water passage of the first chiller 19a flows into the temperature-adjusting heat exchange unit 52, and exchanges heat with the battery 80. Thereby, battery 80 is heated, and the temperature of battery 80 is maintained within an appropriate temperature range. Other operations are the same as those in the cooling / cooling mode.

  As described above, in the refrigeration cycle apparatus 10 in the cooling / warm-up mode, the refrigeration system in which the water-refrigerant heat exchanger 12 and the first chiller 19a function as a radiator and the indoor evaporator 18 and the second chiller 19b function as an evaporator. A cycle is configured.

  Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the first chiller 19a can heat the heat medium on the temperature adjustment side. In addition, the blown air can be cooled by the indoor evaporator 18. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  As a result, in the vehicle air conditioner 1 in the cooling / warm-up mode, it is possible to perform cooling of the vehicle interior similarly to the cooling / cooling mode. Further, similarly to the cooling mode, the on-vehicle device 82 can be cooled.

  Further, the battery 80 can be heated by causing the temperature-adjustment-side heat medium heated by the first chiller 19a to flow into the temperature-adjusting heat exchange unit 52. At this time, the control device 70 adjusts the opening ratio EX1 / EX2 according to the battery temperature TB. Therefore, the temperature of the refrigerant flowing into the first chiller 19a can be appropriately changed, and the temperature of the battery 80 can be maintained within an appropriate temperature range.

  Here, the cooling in the vehicle interior is performed when the outside temperature Tam is relatively high. For this reason, during execution of the cooling temperature adjustment mode, the battery temperature TB rarely falls below the reference lower limit temperature KTBL. For this reason, in the cooling temperature adjustment mode, the cooling cooling mode is often executed, and the opportunity to execute the cooling warm-up mode is small.

(2) Heating Temperature Control Mode In the heating temperature control mode, the control device 70 fully closes the cooling expansion valve 14a and sets the first cooling expansion valve 14b and the second cooling expansion valve 14c to the throttle state. Further, the control device 70 operates the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping capacity for the heating temperature adjustment mode. Control.

  The control device 70 controls the operation of the high-temperature side three-way valve 43 such that the high-temperature side heat medium flowing out of the heater core 42 flows out to the suction port side of the high-temperature side heat medium pump 41. Further, the control device 70 controls the operation of the heat-absorbing three-way valve 63 as in the cooling temperature control mode.

  Thereby, in the refrigeration cycle device 10 in the heating temperature control mode, the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the first three-way joint 13a → the first cooling expansion valve 14b → the first chiller 19a → the second. A refrigeration cycle is formed in which the refrigerant circulates in the order of the cooling expansion valve 14c, the second chiller 19b, the second three-way joint 13b, the evaporating pressure regulating valve 20, the accumulator 21, and the suction port of the compressor 11.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device. For example, the rotation speed of the compressor 11 is controlled such that the high-temperature-side heat medium temperature TWH approaches the target high-temperature-side heat medium temperature TWHO.

  The target high-temperature-side heat medium temperature TWHO is determined based on the target outlet temperature TAO with reference to a control map stored in the control device 70 in advance. In this control map, it is determined that the target high-temperature-side heat medium temperature TWHO is increased with the increase of the target outlet temperature TAO so that the temperature of the blown air blown into the vehicle compartment approaches the target outlet temperature TAO.

  Further, regarding the first cooling expansion valve 14b and the second cooling expansion valve 14c, the supercooling degree SC1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO1. The throttle opening EX1 of the first cooling expansion valve 14b and the throttle opening EX2 of the second cooling expansion valve 14c are controlled. The target degree of supercooling SCO1 is determined in the same manner as in the cooling temperature control mode.

  Further, control device 70 adjusts opening degree ratio EX1 / EX2 such that temperature adjustment-side heat medium temperature TWC1 approaches target temperature adjustment-side heat medium temperature TWCO1. The target temperature adjustment-side heat medium temperature TWCO1 is determined in the same manner as in the cooling temperature control mode. Therefore, control device 70 decreases opening degree ratio EX1 / EX2 as battery temperature TB increases.

  At this time, in the heating / cooling mode, the target temperature adjustment-side heat medium temperature TWCO1 is determined to be lower than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a. In the heating / warm-up mode, the target temperature adjustment-side heat medium temperature TWCO1 is determined to be higher than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a.

  The actuator for the air mix door is controlled in the same manner as in the cooling temperature control mode. Here, in the heating temperature control mode, since the target outlet temperature TAO is relatively high, the opening degree SW of the air mix door 34 approaches 100%. Therefore, in the heating temperature control mode, the air mix door 34 is displaced such that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.

  Therefore, in the refrigeration cycle apparatus 10 in the heating / cooling mode, the state of the refrigerant changes as shown in the Mollier diagram of FIG. In FIG. 4, the state of the refrigerant at a location equivalent to the cycle configuration with respect to the Mollier diagram of FIG. 3 described in the cooling temperature control mode is indicated by the same reference numeral (alphabet) as in FIG. Only the figure is changed to match the figure number. This is the same in the following Mollier diagram.

  In the heating / cooling mode, the refrigerant discharged from the compressor 11 (point a4 in FIG. 4) flows into the refrigerant passage of the water-refrigerant heat exchanger 12, and flows through the water passage, similarly to the cooling temperature control mode. Heat is exchanged with the high-temperature side heat medium and heat is released (point a4 → point b4 in FIG. 4). Thus, the high-temperature side heat medium flowing through the water passage of the water-refrigerant heat exchanger 12 is heated.

  In the high-temperature side heat medium circuit 40, similarly to the cooling temperature control mode, the high-temperature side heat medium heated in the water passage of the water-refrigerant heat exchanger 12 exchanges heat with the blown air in the heater core 42 and radiates heat. . Thereby, the temperature of the blown air blown into the vehicle compartment approaches the target blowout temperature TAO. The high-temperature-side heat medium flowing out of the heater core 42 is sucked into the high-temperature-side heat medium pump 41 via the high-temperature-side three-way valve 43 and is again pressure-fed to the water passage of the water-refrigerant heat exchanger 12.

  The refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 flows into the first cooling expansion valve 14b through the first three-way joint 13a and is decompressed (point b4 → point e4 in FIG. 4). In the heating / cooling mode, the saturation temperature of the refrigerant decompressed by the first cooling expansion valve 14b becomes lower than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a.

  Therefore, the refrigerant decompressed by the first cooling expansion valve 14b flows into the refrigerant passage of the first chiller 19a, and exchanges heat with the temperature control side heat medium flowing through the water passage to evaporate (see FIG. 4). e4 point → f4 point). Thereby, the temperature control side heat medium flowing through the water passage of the first chiller 19a is cooled. In the temperature adjustment-side heat medium circuit 50, the battery 80 is cooled in the same manner as in the cooling mode.

  The refrigerant flowing out of the refrigerant passage of the first chiller 19a flows into the second cooling expansion valve 14c and is decompressed (point f4 → point g4 in FIG. 4). The refrigerant decompressed by the second cooling expansion valve 14c flows into the refrigerant passage of the second chiller 19b, exchanges heat with the heat absorbing heat medium flowing through the water passage, and evaporates (point g4 in FIG. 4 →). i4 points). Thereby, the heat absorbing heat medium flowing through the water passage of the second chiller 19b is cooled. In the heat absorption side heat medium circuit 60, the on-vehicle device 82 is cooled in the same manner as in the cooling temperature control mode.

  The refrigerant flowing out of the refrigerant passage of the second chiller 19b flows into the accumulator 21 via the second three-way joint 13b. The gas-phase refrigerant separated by the accumulator 21 is drawn into the compressor 11 and compressed again (point i4 → point a4 in FIG. 4).

  As described above, in the refrigeration cycle apparatus 10 in the heating / cooling mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a radiator and the first chiller 19a and the second chiller 19b function as an evaporator is configured.

  Therefore, in the refrigeration cycle apparatus 10 in the heating / cooling mode, the water-refrigerant heat exchanger 12 can heat the high-temperature side heat medium. Further, the first chiller 19a can cool the heat medium on the temperature adjustment side. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  As a result, in the vehicle air conditioner 1 in the heating / cooling mode, the vehicle core can be heated by blowing the blast air heated by the heater core 42 so as to approach the target blowing temperature TAO into the vehicle interior. In addition, the heat absorbing side heat medium cooled by the second chiller 19b flows into the cooling water passage of the vehicle-mounted device 82, so that the vehicle-mounted device 82 can be cooled.

  Further, the battery 80 can be cooled by flowing the temperature-adjusting-side heat medium cooled by the first chiller 19a into the temperature-adjusting heat exchange unit 52. At this time, the control device 70 adjusts the opening ratio EX1 / EX2 according to the battery temperature TB. Therefore, the temperature of the refrigerant flowing into the first chiller 19a can be appropriately changed, and the temperature of the battery 80 can be maintained within an appropriate temperature range.

  Further, in the refrigeration cycle apparatus 10 in the heating / warm-up mode, the refrigerant discharged from the compressor 11 (point a5 in FIG. 5) is the refrigerant of the water-refrigerant heat exchanger 12, as shown in the Mollier diagram of FIG. It flows into the passage and exchanges heat with the high-temperature side heat medium flowing through the water passage and radiates heat (point a5 → point b5 in FIG. 5) as in the heating / cooling mode. In the heating / warm-up mode, since the refrigerant also radiates heat in the first chiller 19a, the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 is smaller than in the heating / cooling mode.

  In the high-temperature side heat medium circuit 40, the blown air is heated by the heater core 42 as in the heating / cooling mode. Thereby, the temperature of the blown air blown into the vehicle compartment approaches the target blowout temperature TAO.

  The refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 flows into the first cooling expansion valve 14b via the first three-way joint 13a and is decompressed (point b5 → point e5 in FIG. 5). In the heating / warm-up mode, the saturation temperature of the refrigerant depressurized by the first cooling expansion valve 14b becomes higher than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a.

  Therefore, the refrigerant decompressed by the first cooling expansion valve 14b flows into the refrigerant passage of the first chiller 19a, and exchanges heat with the temperature control side heat medium flowing through the water passage to radiate heat (see FIG. 4). e5 point → f5 point). Thereby, the temperature adjustment-side heat medium flowing through the water passage of the first chiller 19a is heated. In the temperature adjustment-side heat medium circuit 50, the battery 80 is heated in the same manner as in the cooling / warm-up mode.

  The refrigerant flowing out of the refrigerant passage of the first chiller 19a flows into the second cooling expansion valve 14c and is decompressed (point f5 → point g5 in FIG. 5). The refrigerant decompressed by the second cooling expansion valve 14c flows into the refrigerant passage of the second chiller 19b, absorbs heat from the heat absorbing heat medium flowing through the water passage, and evaporates (point g5 → i5 in FIG. 5). point). Thereby, the heat absorbing heat medium flowing through the water passage of the second chiller 19b is cooled. In the heat absorption side heat medium circuit 60, the on-vehicle device 82 is cooled in the same manner as in the cooling temperature control mode.

  The refrigerant flowing out of the refrigerant passage of the second chiller 19b flows into the accumulator 21 via the second three-way joint 13b. The gas-phase refrigerant separated by the accumulator 21 is drawn into the compressor 11 and compressed again (point i5 → point a5 in FIG. 5).

  As described above, in the refrigeration cycle apparatus 10 in the heating / warm-up mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 and the first chiller 19a function as a radiator and the second chiller 19b functions as an evaporator is configured. .

  Therefore, in the refrigeration cycle device 10 in the heating / warm-up mode, the water-refrigerant heat exchanger 12 can heat the high-temperature side heat medium. Further, the first chiller 19a can heat the heat medium on the temperature adjustment side. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  As a result, the vehicle air conditioner 1 in the heating warm-up mode can heat the vehicle interior similarly to the heating cooling mode. Further, similarly to the heating / cooling mode, the in-vehicle device 82 can be cooled.

  Further, the battery 80 can be heated by causing the temperature-adjustment-side heat medium heated by the first chiller 19a to flow into the temperature-adjusting heat exchange unit 52. At this time, the control device 70 adjusts the opening ratio EX1 / EX2 according to the battery temperature TB. Therefore, similarly to the heating / cooling mode, the temperature of the refrigerant flowing into the first chiller 19a can be appropriately changed, and the temperature of the battery 80 can be maintained within an appropriate temperature range.

  Here, the heating of the vehicle interior is performed when the outside temperature Tam is relatively low. Therefore, during execution of the heating temperature control mode, the battery temperature TB may become lower than or equal to the reference lower limit temperature KTBL. In addition, since the battery 80 generates its own heat during charging and discharging, the battery temperature TB may become higher than or equal to the reference upper limit temperature KTBH during the execution of the heating temperature adjustment mode. Therefore, in the heating temperature control mode, the heating / cooling mode and the heating / warm-up mode may be alternately switched.

(3) Single Cooling Mode In the single cooling mode, the control device 70 fully closes the cooling expansion valve 14a, closes the first cooling expansion valve 14b, and fully opens the second cooling expansion valve 14c. Further, the control device 70 controls the operation of the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping ability for the single cooling mode. Control.

  The control device 70 controls the operation of the high-temperature three-way valve 43 so that the high-temperature heat medium flowing out of the heater core 42 flows into the high-temperature radiator 44. Further, the control device 70 controls the operation of the heat-absorbing three-way valve 63 as in the cooling temperature control mode.

  Thereby, in the refrigeration cycle apparatus 10 in the single cooling mode, the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the first three-way joint 13a → the first cooling expansion valve 14b → the first chiller 19a → (second A refrigeration cycle in which the refrigerant circulates in the order of the cooling expansion valve 14c →) the second chiller 19b → the second three-way joint 13b → the evaporating pressure regulating valve 20 → the accumulator 21 → the suction port of the compressor 11 is constructed.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device. For example, the rotation speed of the compressor 11 is controlled so that the temperature adjustment-side heat medium temperature TWC1 approaches the target temperature adjustment-side heat medium temperature TWCO1.

  The target temperature adjustment-side heat medium temperature TWCO1 is determined based on the battery temperature TB with reference to a control map for the single cooling mode stored in the control device 70 in advance. In this control map, the target temperature adjustment-side heat medium temperature TWCO1 is determined to decrease as the battery temperature TB increases. In the single cooling mode, the target temperature adjustment-side heat medium temperature TWCO1 is determined to be lower than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a.

  The throttle opening of the first cooling expansion valve 14b is controlled such that the supercooling degree SC1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO1. The target degree of supercooling SCO1 is determined based on the outside temperature Tam with reference to a control map for the single cooling mode stored in the control device 70 in advance. In this control map, the target degree of supercooling SCO1 is determined so that the COP of the cycle approaches the maximum value.

  Further, the actuator for the air mixing door is controlled so that the opening degree SW becomes 0%. That is, control is performed such that the cool air bypass passage 35 is fully opened and the air passage on the heater core 42 side is completely closed.

  For this reason, in the refrigeration cycle apparatus 10 in the single cooling mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a radiator and the first chiller 19a and the second chiller 19b function as an evaporator is configured.

  Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the first chiller 19a can cool the heat medium on the temperature adjustment side. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  In the single cooling mode, the air mixing door 34 completely closes the air passage on the heater core 42 side. For this reason, the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 radiates heat to the outside air by the high-temperature side radiator 44 while hardly radiating heat to the blown air by the heater core 42. Therefore, the blown air is not heated by the heater core 42.

  As a result, the vehicle air conditioner 1 in the single cooling mode allows the temperature-adjusting-side heat medium cooled by the first chiller 19a to flow into the temperature-adjusting heat exchange unit 52 without performing air conditioning in the vehicle interior. Thus, the battery 80 can be cooled. Further, the heat absorbing side heat medium cooled by the second chiller 19b flows into the cooling water passage of the vehicle-mounted device 82, so that the vehicle-mounted device 82 can be cooled.

(4) Independent warm-up mode In the independent warm-up mode, the control device 70 fully closes the cooling expansion valve 14a, fully opens the first cooling expansion valve 14b, and closes the second cooling expansion valve 14c. I do. In addition, the control device 70 stops the high-temperature side heat medium pump 41 and performs the temperature adjustment side heat medium pump 51 and the heat absorption side heat medium pump so as to exhibit a predetermined heat medium pumping ability for the single warm-up mode. The operation of 61 is controlled. Further, the control device 70 controls the operation of the heat-absorbing three-way valve 63 as in the cooling temperature control mode.

  Thereby, in the refrigeration cycle apparatus 10 in the single warm-up mode, the discharge port of the compressor 11 → (water-refrigerant heat exchanger 12 → first three-way joint 13a → first cooling expansion valve 14b →) first chiller 19a → A refrigeration cycle is formed in which the refrigerant circulates in the order of the second cooling expansion valve 14c, the second chiller 19b, the second three-way joint 13b, the evaporating pressure regulating valve 20, the accumulator 21, and the suction port of the compressor 11.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device. For example, the rotation speed of the compressor 11 is controlled so that the temperature adjustment-side heat medium temperature TWC1 approaches the target temperature adjustment-side heat medium temperature TWCO1.

  The target temperature adjustment-side heat medium temperature TWCO1 is determined based on the battery temperature TB with reference to a control map for the single warm-up mode stored in the control device 70 in advance. In this control map, the target temperature adjustment-side heat medium temperature TWCO1 is determined to decrease as the battery temperature TB increases. In the single warm-up mode, the target temperature adjustment-side heat medium temperature TWCO1 is determined to be higher than the temperature of the temperature adjustment-side heat medium flowing into the water passage of the first chiller 19a.

  The throttle opening of the second cooling expansion valve 14c is controlled such that the supercooling degree SC1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO1. The target degree of supercooling SCO1 is determined based on the outside temperature Tam with reference to a control map for the single cooling mode stored in the control device 70 in advance. In this control map, the target degree of supercooling SCO1 is determined so that the COP of the cycle approaches the maximum value.

  The actuator for the air mix door is controlled so that the opening degree SW becomes 0% as in the single cooling mode.

  Therefore, in the refrigeration cycle apparatus 10 in the single warm-up mode, a refrigeration cycle in which the first chiller 19a functions as a radiator and the second chiller 19b functions as an evaporator is configured. Therefore, the first chiller 19a can heat the temperature adjustment-side heat medium. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  In the single warm-up mode, since the high-temperature side heat medium pump 41 is stopped, the refrigerant flowing into the refrigerant passage of the water-refrigerant heat exchanger 12 flows out of the water-refrigerant heat exchanger 12 with almost no heat radiation. . Therefore, the blown air is not heated by the heater core 42.

  As a result, in the vehicle air conditioner 1 in the single warm-up mode, the temperature-adjustment-side heat medium heated by the first chiller 19a flows into the temperature-adjustment heat exchange unit 52 without performing air conditioning in the vehicle interior. Thereby, the battery 80 can be heated. Further, the heat absorbing side heat medium cooled by the second chiller 19b flows into the cooling water passage of the vehicle-mounted device 82, so that the vehicle-mounted device 82 can be cooled.

  Here, the refrigeration cycle device 10 of the present embodiment can perform pre-air conditioning. The pre-air-conditioning is executed by the occupant having the control device 70 store the target temperature Tset in the vehicle compartment, the pre-air-conditioning start time, and the like using the operation panel 701 or a remote control terminal. The pre-air-conditioning start time is a time at which the time when the occupant gets on board is approaching, and there is a high possibility that the vehicle will travel in the relatively near future.

  Therefore, in the refrigeration cycle apparatus 10 of the present embodiment, when the pre-air conditioning is set, the battery temperature TB at a time that is a predetermined time before (for example, 10 minutes before) the pre-air conditioning start time is equal to the reference lower limit temperature. If it is lower than KTBL, the operation is performed in the single warm-up mode.

  Thereafter, when the pre-air conditioning start time comes, the mode is switched from the single warm-up mode to the heating temperature control mode. Further, before switching from the single warm-up mode to the heating temperature control mode (for example, one minute before), the target temperature adjustment-side heat medium temperature TWCO1 is increased.

  That is, in the refrigeration cycle apparatus 10 of the present embodiment, when the pre-air conditioning is set and the operation in the single warm-up mode is performed, it is determined that the predetermined warm-up switching condition is satisfied. Then, when the warm-up switching condition is satisfied, before switching from the single warm-up mode to the heating temperature adjustment mode, the target temperature adjustment-side heat medium temperature TWCO1 is increased to increase the temperature of the temperature adjustment-side heat medium. It has become.

(5) Single Cooling Mode In the single cooling mode, the control device 70 closes the cooling expansion valve 14a and fully closes the first cooling expansion valve 14b. In addition, the control device 70 controls the operation of the high-temperature side heat medium pump 41 and the temperature adjustment side heat medium pump 51 and the heat absorption side heat medium pump so as to exhibit a predetermined heat medium pumping capacity for the single cooling mode. 61 is stopped.

  The control device 70 controls the operation of the high-temperature three-way valve 43 so that the high-temperature heat medium flowing out of the heater core 42 flows into the high-temperature radiator 44.

  Thereby, in the refrigeration cycle apparatus 10 in the single cooling mode, the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the first three-way joint 13a → the cooling expansion valve 14a → the indoor evaporator 18 → the second three-way joint 13b A refrigeration cycle is formed in which the refrigerant circulates in the order of the evaporating pressure regulating valve 20, the accumulator 21, and the suction port of the compressor 11.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device, similarly to the cooling temperature control mode.

  Therefore, in the refrigeration cycle apparatus 10a in the single cooling mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a radiator and the indoor evaporator 18 functions as an evaporator is configured. Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the blown air can be cooled by the indoor evaporator 18.

  As a result, in the vehicle air conditioner 1 in the single cooling mode, the inside of the vehicle compartment can be cooled in the same manner as in the cooling temperature control mode without adjusting the temperature of the battery 80.

(6) Single Heating Mode In the single cooling mode, the control device 70 fully closes the cooling expansion valve 14a, fully opens the first cooling expansion valve 14b, and throttles the second cooling expansion valve 14c. Further, the control device 70 controls the operation of the high-temperature side heat medium pump 41 and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping capacity for the single heating mode, and controls the temperature adjustment side heat medium pump. The pump 51 is stopped.

  Further, the control device 70 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows out to the suction port side of the high-temperature side heat medium pump 41, similarly to the heating temperature control mode. I do. Further, the control device 70 controls the operation of the heat-absorbing three-way valve 63 as in the cooling temperature control mode.

  Thereby, in the refrigeration cycle apparatus 10 in the single heating mode, the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the first three-way joint 13a → (the first cooling expansion valve 14b → the first chiller 19a →) A refrigeration cycle in which the refrigerant circulates in the order of 2 cooling expansion valve 14c → second chiller 19b → second three-way joint 13b → evaporation pressure adjusting valve 20 → accumulator 21 → compressor 11 suction port.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device, similarly to the heating temperature control mode.

  Therefore, in the refrigeration cycle apparatus 10a in the single cooling mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a radiator and the second chiller 19b functions as an evaporator is configured. Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  In the single cooling mode, since the temperature adjustment-side heat medium pump 51 is stopped, the refrigerant flowing into the refrigerant passage of the first chiller 19a flows out of the first chiller 19a with almost no heat radiation. Therefore, the heat medium on the temperature adjustment side is hardly heated by the first chiller 19a.

  As a result, the vehicle air conditioner 1 in the single heating mode can heat the vehicle interior similarly to the heating temperature adjustment mode without adjusting the temperature of the battery 80.

  Here, as a condition that the heating of the vehicle interior is required without performing the temperature adjustment of the battery 80, it is conceivable that the battery 80 is rapidly charged in a state where the occupant gets on the vehicle at an extremely low outside temperature. During rapid charging of the battery 80, the amount of self-generated heat of the battery 80 increases, so that it is not necessary to warm up the battery 80 even at a low outside temperature. However, when driving the vehicle after the completion of the quick charge, the battery 80 needs to be warmed up.

  Therefore, in the refrigeration cycle apparatus 10 of the present embodiment, when the rapid charging of the battery 80 is started in a state where the heating of the vehicle interior is requested, the operation in the single heating mode is performed. Thereafter, when the quick charge is completed, the mode is switched from the single heating mode to the heating temperature control mode. Further, when the remaining charge amount of the battery 80 becomes larger than a predetermined reference remaining charge amount, that is, immediately before the completion of the quick charge, the temperature adjusting-side heat medium pump 51 is operated.

  That is, in the refrigeration cycle device 10 of the present embodiment, when the rapid charging of the battery 80 is started in a state where the heating of the vehicle interior is requested, it is determined that the predetermined heating switching condition is satisfied. Then, when the heating switching condition is satisfied, before switching from the single heating mode to the heating temperature adjustment mode, the target high-temperature-side heat medium temperature TWHO is increased to increase the temperature of the high-temperature side heat medium. I have.

  As described above, the refrigeration cycle apparatus 10 of the present embodiment switches operation modes such as a cooling temperature control mode, a heating temperature control mode, a single cooling mode, a single warm-up mode, a single cooling mode, and a single heating mode to switch the inside of the vehicle compartment. Air conditioning and temperature adjustment of the battery 80 can be performed.

  In the cooling temperature control mode and the heating temperature control mode, the appropriate temperature adjustment of the blast air blown into the cabin, which is the air-conditioned space, and the appropriate temperature adjustment of the battery 80, which is a temperature adjustment target different from the blast air, Adjustment can be compatible.

  More specifically, in the refrigerating cycle device 10 in the cooling temperature control mode, the water-refrigerant heat exchanger 12 constituting the heating unit functions as a radiator, and the indoor evaporator 18 and the second chiller 19b constituting the heat absorbing unit are provided. A vapor compression refrigeration cycle that functions as an evaporator can be configured. Therefore, in the indoor evaporator 18, the low-pressure refrigerant can be evaporated to cool the blown air. That is, cooling of the vehicle interior can be performed.

  In the refrigeration cycle apparatus 10 in the heating temperature control mode, the refrigeration cycle in which the water-refrigerant heat exchanger 12 forming the heating unit functions as a radiator and the second chiller 19b forming the heat absorption unit functions as an evaporator is used. Be composed. Therefore, the blower air can be heated by the heater core 42 using the high-temperature side heat medium heated by the high-pressure refrigerant as a heat source. That is, heating of the vehicle interior can be performed.

  Further, in the cooling temperature adjustment mode and the heating temperature adjustment mode, the temperature of the refrigerant flowing into the first chiller 19a constituting the temperature adjustment unit can be changed by changing the opening degree ratio EX1 / EX2. This allows the first chiller 19a to cool or heat the battery 80 by changing the temperature of the temperature-adjusting heat medium that exchanges heat with the refrigerant. That is, appropriate temperature adjustment of the battery 80 can be performed.

  As a result, according to the refrigeration cycle device 10 of the present embodiment, it is possible to achieve both appropriate temperature adjustment of the blown air and appropriate temperature adjustment of the battery 80.

  In addition, in the cooling temperature adjustment mode and the heating temperature adjustment mode, the temperature of the battery 80 is adjusted by changing the opening ratio EX1 / EX2.

  According to this, it is not necessary to reverse the flow direction of the refrigerant flowing into the indoor evaporator 18 or to stop the compressor 11 in order to adjust the temperature of the battery 80 in the cooling temperature control mode. Similarly, in the heating temperature adjustment mode, it is not necessary to reverse the flow direction of the refrigerant flowing into the water-refrigerant heat exchanger 12 or to stop the compressor 11 in order to adjust the temperature of the battery 80. Therefore, it is possible to suppress the temperature fluctuation of the blown air.

  As a result, according to the refrigeration cycle device 10 of the present embodiment, it is possible to achieve both the appropriate temperature adjustment of the battery 80 and the suppression of the temperature fluctuation of the blown air due to the temperature adjustment of the battery 80.

  This will be described in more detail with reference to the time chart of FIG. The time chart of FIG. 6 shows changes in the blast air temperature TAV and the battery temperature TB in the heating temperature control mode. The blast air temperature TAV is the temperature of the blast air detected by the conditioned air temperature sensor 79. In the example of FIG. 6, the battery temperature TB is lower than or equal to the reference lower limit temperature KTBL at the time of starting the heating of the vehicle interior. Therefore, in this example, the operation is started from the heating warm-up mode.

  In the heating / warm-up mode, the opening degree ratio EX1 / EX2 is reduced as the battery temperature TB increases. Further, in the control map of the present embodiment, as shown in FIG. 6, the degree of decrease in the opening degree ratio EX1 / EX2 is changed according to the battery temperature TB, thereby suppressing a sharp rise in the battery temperature TB. When the battery temperature TB becomes equal to or higher than the reference upper limit temperature KTBH, the mode is switched to the heating / cooling mode.

  In the heating / cooling mode, the opening ratio EX1 / EX2 is increased as the battery temperature TB decreases. Further, in the control map of the present embodiment, as shown in FIG. 6, the degree of increase of the opening ratio EX1 / EX2 is changed in accordance with the battery temperature TB to suppress a sharp drop in the battery temperature TB. When the battery temperature TB becomes equal to or lower than the reference lower limit temperature KTBL, the mode is switched to the heating warm-up mode.

  By switching between the heating warm-up mode and the heating / cooling mode, the battery temperature TB can be maintained within an appropriate temperature range.

  In FIG. 6, the reason that the battery temperature TB slightly rises immediately after switching from the heating warm-up mode to the heating cooling mode is because the heat capacity of the temperature adjustment side heat medium circulating in the temperature adjustment side heat medium circuit 50 is different. This is because a response delay occurs when the temperature of the heat medium on the temperature adjustment side decreases. The same holds for the reason that the battery temperature TB slightly decreases immediately after switching from the heating / cooling mode to the heating / warm-up mode.

  Further, in the refrigeration cycle apparatus 10 of the present embodiment, in the heating temperature control mode, the high-temperature heat medium temperature TWH approaches the target high-temperature heat medium temperature TWHO independently of the control of increasing or decreasing the opening ratio EX1 / EX2. Thus, the rotation speed of the compressor 11 is controlled.

  Here, the high-temperature side heat medium is used as a heat source when heating the blown air by the heater core 42. Further, in the heating temperature control mode, the opening degree SW of the air mix door 34 approaches 100%. For this reason, controlling the rotation speed of the compressor 11 so that the high-temperature-side heat medium temperature TWH approaches the target high-temperature-side heat medium temperature TWHO requires that the blower air temperature TAV approach the target outlet temperature TAO. This means controlling the refrigerant discharge capacity.

  Therefore, in the refrigeration cycle apparatus 10 of the present embodiment, as shown in FIG. 6, even when the temperature of the battery 80 is adjusted by switching between the heating warm-up mode and the heating / cooling mode, the fluctuation of the blast air temperature TAV is suppressed. be able to.

  In addition, the refrigeration cycle apparatus 10 of the present embodiment can perform the single cooling mode and the single warm-up mode. According to this, even when it is not necessary to perform air conditioning in the vehicle compartment, the temperature of the battery 80 can be appropriately adjusted by cooling or heating the battery 80.

  At this time, in the single cooling mode, the cooling expansion valve 14a is fully closed, the first cooling expansion valve 14b is in a throttled state, and the second cooling expansion valve 14c is fully open. That is, in the single cooling mode, it is possible to perform appropriate cooling of the battery 80 in a simple control mode in which the throttle opening of the first cooling expansion valve 14b is substantially controlled.

  On the other hand, in the single heating mode, the cooling expansion valve 14a is fully closed, the first cooling expansion valve 14b is fully opened, and the second cooling expansion valve 14c is in a throttled state. That is, in the single heating mode, the battery 80 can be appropriately warmed up in a simple control mode in which the throttle opening of the second cooling expansion valve 14c is substantially controlled.

  Further, in the refrigeration cycle device 10 of the present embodiment, when the warm-up switching condition is satisfied, the temperature of the temperature adjustment-side heat medium is increased before switching from the single warm-up mode to the heating temperature control mode. According to this, it is possible to increase the temperature of the temperature adjustment-side heat medium circulating in the temperature adjustment-side heat medium circuit 50 before switching to the heating temperature adjustment mode.

  According to this, when the mode is switched from the single warm-up mode to the heating temperature control mode, the heating capacity of the battery 80 is utilized by utilizing the heat stored in the temperature control side heat medium circulating in the temperature control side heat medium circuit 50. Can be suppressed. That is, when switching from the single warm-up mode to the heating temperature control mode, even if the heating capacity of the refrigeration cycle device 10 is used to heat the blown air, the heat stored in the temperature adjustment-side heat medium is The battery 80 can be warmed up by utilizing this.

  Further, in the refrigeration cycle apparatus 10 of the present embodiment, a single cooling mode and a single heating mode can be performed. According to this, even when it is not necessary to adjust the temperature of the battery 80, it is possible to perform air conditioning in the vehicle compartment.

  Further, in the refrigeration cycle device 10 of the present embodiment, when the heating switching condition is satisfied, the temperature of the high-temperature side heat medium is increased before switching from the single heating mode to the heating temperature adjustment mode.

  According to this, when switching from the independent heating mode to the heating temperature control mode, the heat stored in the high-temperature side heat medium circulating through the high-temperature side heat medium circuit 40 is used to reduce the heating capacity of the blown air. Can be suppressed. That is, even when the heating capacity of the refrigeration cycle device 10 is used to heat the battery 80 when the mode is switched from the single heating mode to the heating temperature control mode, the heat stored in the high-temperature side heat medium is used. To warm up the blast air.

(2nd Embodiment)
In the present embodiment, an example in which a refrigeration cycle device 10a is employed as shown in FIG. 7 will be described. In the refrigeration cycle apparatus 10a, the third to sixth three-way joints 13c to 13f, the heating expansion valve 14d, the dehumidifying on-off valve 15a, the heating on-off valve 15b, and the refrigeration cycle apparatus 10 described in the first embodiment are provided. An outdoor heat exchanger 16, a bypass passage 22a, a heating passage 22b, and the like are added.

  In the refrigeration cycle apparatus 10a, the inlet side of the third three-way joint 13c is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12. The basic configuration of the third to sixth three-way joints 13c to 13f is the same as that of the first three-way joint 13a.

  One inlet of the third three-way joint 13c is connected to the inlet of a heating expansion valve 14d. One inflow side of the fourth three-way joint 13d is connected to the other outlet of the third three-way joint 13c via a bypass passage 22a. An on-off valve 15a for dehumidification is arranged in the bypass passage 22a.

  The dehumidifying on-off valve 15a is an electromagnetic valve that opens and closes a refrigerant passage connecting the other outflow side of the third three-way joint 13c and one inflow side of the fourth three-way joint 13d. Further, the refrigeration cycle device 10a includes a heating on-off valve 15b, as described later. The basic configuration of the heating on-off valve 15b is the same as that of the dehumidifying on-off valve 15a.

  The on-off valve 15a for dehumidification and the on-off valve 15b for heating can switch the refrigerant circuit in each operation mode by opening and closing the refrigerant passage. Therefore, the on-off valve 15a for dehumidification and the on-off valve 15b for heating, together with the expansion valve 14a for cooling, etc., are refrigerant circuit switching units that switch the refrigerant circuit of the cycle. The operations of the dehumidifying on-off valve 15a and the heating on-off valve 15b are controlled by a control voltage output from the control device 70.

  The heating expansion valve 14d is a heating pressure reducing unit that reduces the pressure of the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 and adjusts the flow rate of the refrigerant that flows out downstream. The basic configuration of the heating expansion valve 14d is the same as that of the cooling expansion valve 14a and the like.

  The refrigerant inlet side of the outdoor heat exchanger 16 is connected to the outlet of the heating expansion valve 14d. The outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out of the heating expansion valve 14d and the outside air blown by an outside air fan (not shown).

  The outdoor heat exchanger 16 is arranged on the front side in the drive device room. For this reason, when the vehicle is traveling, traveling wind can be applied to the outdoor heat exchanger 16. Therefore, the outdoor heat exchanger 16 may be formed integrally with the high-temperature-side radiator 44, the heat-absorbing-side radiator 64, and the like.

  The refrigerant outlet of the outdoor heat exchanger 16 is connected to the inflow side of the fifth three-way joint 13e. One outlet of the sixth three-way joint 13f is connected to one outlet of the third three-way joint 13c via a heating passage 22b. A heating opening / closing valve 15b that opens and closes the refrigerant passage is arranged in the heating passage 22b.

  The other outlet of the fifth three-way joint 13e is connected to the other inlet of the fourth three-way joint 13d. A check valve 17 is disposed in the refrigerant passage connecting the other outflow side of the fifth three-way joint 13e and the other inflow side of the fourth three-way joint 13d. The check valve 17 allows the refrigerant to flow from the fifth three-way joint 13e to the fourth three-way joint 13d, and inhibits the refrigerant from flowing from the fourth three-way joint 13d to the fifth three-way joint 13e. Fulfill.

  The inflow side of the first three-way joint 13a is connected to the outflow port of the fourth three-way joint 13d. The other inlet side of the sixth three-way joint 13f is connected to the outlet of the evaporation pressure regulating valve 20. The inlet of the accumulator 21 is connected to the outlet of the sixth three-way joint 13f.

  Therefore, in the refrigeration cycle apparatus 10a, the bypass passage 22a allows the refrigerant flowing out of the water-refrigerant heat exchanger 12 constituting the heating section to bypass the outdoor heat exchanger 16 and to be the first three-way joint 13a serving as the branch section. This is a refrigerant passage that leads to the upstream side of.

  In addition, the heating passage 22b bypasses the refrigerant flowing out of the outdoor heat exchanger 16 to the indoor evaporator 18, the first chiller 19a forming the temperature adjustment unit, and the second chiller 19b forming the heat absorption unit. A refrigerant passage that leads to the suction port side of the compressor 11.

  As shown in the block diagram of FIG. 8, a fourth refrigerant temperature sensor 74d and a third refrigerant pressure sensor 75c are connected to the input side of the control device 70 of the present embodiment. The fourth refrigerant temperature sensor 74d is a fourth refrigerant temperature detection unit that detects the temperature T4 of the refrigerant flowing out of the outdoor heat exchanger 16. The third refrigerant pressure sensor 75c is a third pressure detector that detects the pressure P3 of the refrigerant flowing out of the outdoor heat exchanger 16. Other configurations are the same as those of the refrigeration cycle device 10 described in the first embodiment.

  Next, the operation of the present embodiment in the above configuration will be described. In the refrigeration cycle apparatus 10a of this embodiment, in addition to the cooling temperature control mode, the heating temperature control mode, the single cooling mode, the single warming mode, the single cooling mode, and the single heating mode, the operation is performed in the dehumidifying heating temperature control mode. be able to.

  The dehumidifying and heating temperature control mode is an operation mode in which cooling and reheating of the blown air for performing dehumidifying and heating in the vehicle compartment and temperature adjustment of the battery 80 are performed. The dehumidification and heating temperature control mode includes a dehumidification and heating cooling mode for dehumidifying the blast air and adjusting the temperature, and cooling the battery 80, and a dehumidification and temperature adjustment for the blast air and heating and warming the battery 80. There is a dehumidifying heating warm-up mode. Hereinafter, the detailed operation of each operation mode will be described.

(1) Cooling Temperature Control Mode In the cooling temperature control mode, the control device 70 sets the cooling expansion valve 14a, the first cooling expansion valve 14b, and the second cooling expansion valve 14c to the throttle state, and the heating expansion valve 14d. Is fully opened. In addition, the control device 70 stops the high-temperature side heat medium pump 41 and performs the temperature adjustment side heat medium pump 51 and the heat absorption side heat medium pump so as to exhibit a predetermined heat medium pumping capacity for the cooling temperature control mode. The operation of 61 is controlled.

  Further, the control device 70 closes the on-off valve 15a for dehumidification and the on-off valve 15b for heating. Further, the control device 70 controls the operation of the heat-absorbing three-way valve 63 in the same manner as in the cooling temperature control mode of the first embodiment.

  Thereby, in the refrigeration cycle device 10a in the cooling temperature control mode, the discharge port of the compressor 11 (→ water-refrigerant heat exchanger 12 → third three-way joint 13c → heating expansion valve 14d) → outdoor heat exchanger 16 (→ Fifth three-way joint 13e → check valve 17 → fourth three-way joint 13d) → first three-way joint 13a → cooling expansion valve 14a → indoor evaporator 18 → second three-way joint 13b → evaporating pressure regulating valve 20 → accumulator 21 → The refrigerant circulates in the order of the suction port of the compressor 11 and the discharge port of the compressor 11 → water-refrigerant heat exchanger 12 → third three-way joint 13c → heating expansion valve 14d) → outdoor heat exchanger 16 (→ 5 Three-way joint 13e → check valve 17 → fourth three-way joint 13d) → first three-way joint 13a → first cooling expansion valve 14b → first chiller 19a → second cooling expansion valve 14c → second chiller 19b → second 2 Three-way joint 13b → evaporation Refrigeration cycle in which the refrigerant is circulated in the order of the suction port of force adjusting valve 20 → accumulator 21 → compressor 11 is constructed.

  That is, in the refrigeration cycle apparatus 10a in the cooling temperature control mode, similarly to the refrigeration cycle apparatus 10 of the first embodiment, a path through which the refrigerant flows in the order of the cooling expansion valve 14a → the indoor evaporator 18, and the first cooling expansion path. The path in which the refrigerant flows in the order of the valve 14b, the first chiller 19a, the second cooling expansion valve 14c, and the second chiller 19b is switched to a refrigerant circuit connected in parallel to the refrigerant flow.

  With this circuit configuration, the control device 70 appropriately controls the operation of various control target devices, similarly to the cooling temperature control mode of the first embodiment. The throttle opening of the cooling expansion valve 14a is controlled such that the supercooling degree SC3 of the refrigerant flowing out of the outdoor heat exchanger 16 approaches the target supercooling degree SCO3.

  The degree of supercooling SC3 is calculated from the temperature T4 detected by the fourth refrigerant temperature sensor 74d and the pressure P3 detected by the third refrigerant pressure sensor 75c. The target degree of subcooling SCO3 is determined based on the outside temperature Tam with reference to a control map stored in the control device 70 in advance. In this control map, the target degree of supercooling SCO3 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

  Therefore, in the refrigeration cycle apparatus 10a in the cooling / cooling mode, a refrigeration cycle in which the outdoor heat exchanger 16 functions as a radiator and the indoor evaporator 18, the first chiller 19a, and the second chiller 19b function as an evaporator is configured. You. Therefore, the air blown by the indoor evaporator 18 can be cooled. Further, the first chiller 19a can cool the heat medium on the temperature adjustment side. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  In the refrigeration cycle apparatus 10a in the cooling / warm-up mode, a refrigeration cycle is configured in which the outdoor heat exchanger 16 and the first chiller 19a function as a radiator, and the indoor evaporator 18 and the second chiller 19b function as an evaporator. You. Therefore, the first chiller 19a can heat the temperature adjustment-side heat medium. In addition, the blown air can be cooled by the indoor evaporator 18. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  Further, in the cooling temperature control mode, since the high-temperature side heat transfer medium pump 41 is stopped, the refrigerant flowing into the refrigerant passage of the water-refrigerant heat exchanger 12 hardly releases heat from the water-refrigerant heat exchanger 12. leak. Therefore, the blown air is not heated by the heater core 42.

  As a result, in the vehicle air conditioner 1 in the cooling temperature control mode, the air in the vehicle cabin can be cooled by blowing the blast air cooled by the indoor evaporator 18 into the vehicle cabin. Further, similarly to the first embodiment, the in-vehicle device 82 can be cooled. Further, control device 70 can maintain the temperature of battery 80 within an appropriate temperature range by adjusting opening ratio EX1 / EX2 according to battery temperature TB.

(2) Dehumidifying / heating temperature control mode In the dehumidifying / heating temperature control mode, the control device 70 restricts the cooling expansion valve 14a, the first cooling expansion valve 14b, the second cooling expansion valve 14c, and the heating expansion valve 14d. State. In addition, the control device 70 controls the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping capacity for the dehumidifying and heating temperature control mode. Control the operation.

  Further, the control device 70 opens the on-off valve 15a for dehumidification and the on-off valve 15b for heating. The control device 70 controls the operation of the high-temperature three-way valve 43 and the heat-absorbing three-way valve 63 as in the heating temperature control mode of the first embodiment.

  Thus, in the refrigeration cycle apparatus 10a in the cooling temperature control mode, the discharge port of the compressor 11, the water-refrigerant heat exchanger 12, the third three-way joint 13c, the heating expansion valve 14d, the outdoor heat exchanger 16, and the fifth three-way. The refrigerant circulates in the order of the joint 13e → the heating passage 22b → the accumulator 21 → the suction port of the compressor 11.

  Further, the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the third three-way joint 13c → the bypass passage 22a → the fourth three-way joint 13d → the first three-way joint 13a → the cooling expansion valve 14a → the indoor evaporator 18 → The refrigerant circulates in the order of the second three-way joint 13b → the evaporating pressure regulating valve 20 → the accumulator 21 → the inlet of the compressor 11 and the outlet of the compressor 11 → the water-refrigerant heat exchanger 12 → the third three-way joint 13c → Bypass passage 22a → fourth three-way joint 13d → first three-way joint 13a → first cooling expansion valve 14b → first chiller 19a → second cooling expansion valve 14c → second chiller 19b → second three-way joint 13b → evaporation pressure A refrigeration cycle in which the refrigerant circulates in the order of the regulating valve 20, the accumulator 21, and the suction port of the compressor 11 is configured.

  That is, in the refrigeration cycle apparatus 10a in the dehumidifying and heating temperature control mode, a path in which the refrigerant flows in the order of the heating expansion valve 14d → the outdoor heat exchanger 16, a path in which the refrigerant flows in the order of the cooling expansion valve 14a → the indoor evaporator 18, and The path through which the refrigerant flows in the order of the first cooling expansion valve 14b → the first chiller 19a → the second cooling expansion valve 14c → the second chiller 19b is switched to a refrigerant circuit connected in parallel to the refrigerant flow. .

  With this circuit configuration, the control device 70 appropriately controls the operation of various control target devices, similarly to the cooling temperature control mode of the first embodiment. The compressor 11 is controlled in the same manner as in the heating temperature control mode of the first embodiment.

  The cooling expansion valve 14a and the heating expansion valve 14d have their throttle openings set so that the supercooling degree SC1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO1. Control. Further, the control device 70 increases the opening ratio EX3 / EX4 of the throttle opening EX3 of the cooling expansion valve 14a to the throttle opening EX4 of the heating expansion valve 14d as the target outlet temperature TAO increases.

  Further, the first cooling expansion valve 14b and the second cooling expansion valve 14c are controlled in the same manner as in the heating temperature control mode of the first embodiment. The actuator for the air mix door is controlled in the same manner as in the cooling temperature control mode of the first embodiment.

  For this reason, in the refrigeration cycle apparatus 10a in the dehumidifying heating / cooling mode, the water-refrigerant heat exchanger 12 functions as a radiator, and the outdoor heat exchanger 16, the indoor evaporator 18, the first chiller 19a, and the second chiller 19b are used. A refrigeration cycle that functions as an evaporator is configured.

  Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. In the indoor evaporator 18, the blown air can be cooled. In the first chiller 19a, the heat medium on the temperature adjustment side can be cooled. The heat absorption side heat medium can be cooled by the second chiller 19b.

  In the refrigeration cycle apparatus 10a in the dehumidifying heating / warm-up mode, the water-refrigerant heat exchanger 12 and the first chiller 19a function as a radiator, and the outdoor heat exchanger 16, the indoor evaporator 18, and the second chiller 19b Is configured as a refrigeration cycle that functions as an evaporator.

  Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. In the indoor evaporator 18, the blown air can be cooled. The first chiller 19a can heat the heat medium on the temperature adjustment side. The heat absorption side heat medium can be cooled by the second chiller 19b.

  As a result, in the vehicle air conditioner 1 in the dehumidifying and heating temperature control mode, the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the vehicle cabin, whereby Dehumidification heating can be performed.

  At this time, as the target outlet temperature TAO increases, the opening degree ratio EX3 / EX4 can be increased, and the refrigerant evaporation pressure in the outdoor heat exchanger 16 can be reduced. Therefore, the amount of heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 16 can be increased, and the amount of heat released by the refrigerant to the high-temperature heat medium in the water-refrigerant heat exchanger 12 can be increased. And the heating capability of the blower air in the heater core 42 can be improved.

  Further, since the opening ratio EX1 / EX2 is adjusted according to the battery temperature TB, the temperature of the battery 80 can be maintained within an appropriate temperature range as in the cooling temperature adjustment mode.

(3) Heating Temperature Control Mode In the heating temperature control mode, the control device 70 fully closes the cooling expansion valve 14a and the heating expansion valve 14d, and closes the first cooling expansion valve 14b and the second cooling expansion valve 14c. The aperture state is set. Further, the control device 70 operates the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping capacity for the heating temperature adjustment mode. Control.

  Further, the control device 70 opens the dehumidifying on-off valve 15a and closes the heating on-off valve 15b. The control device 70 controls the operation of the high-temperature three-way valve 43 and the heat-absorbing three-way valve 63 as in the heating temperature control mode of the first embodiment.

  Thereby, in the refrigeration cycle apparatus 10a in the heating temperature control mode, the discharge port of the compressor 11, the water-refrigerant heat exchanger 12, the bypass passage 22a, the first three-way joint 13a, the first cooling expansion valve 14b, and the first chiller. A refrigeration cycle in which the refrigerant circulates in the order of 19a → second cooling expansion valve 14c → second chiller 19b → second three-way joint 13b → evaporation pressure regulating valve 20 → accumulator 21 → suction port of compressor 11 is formed.

  That is, in the refrigeration cycle device 10a in the heating temperature control mode, a refrigeration cycle similar to that in the heating temperature control mode in the first embodiment is configured. Other operations are the same as in the heating temperature control mode of the first embodiment. Therefore, in the vehicle air conditioner 1 of the present embodiment, similarly to the heating temperature control mode of the first embodiment, heating of the vehicle interior, cooling of the in-vehicle device 82, and further, temperature adjustment of the battery 80 can be performed.

(4) Single Cooling Mode In the single cooling mode, the controller 70 fully closes the cooling expansion valve 14a, closes the first cooling expansion valve 14b, fully opens the second cooling expansion valve 14c, and performs heating. The expansion valve 14d is fully opened. Further, the control device 70 stops the high-temperature side heat medium pump 41 and controls the temperature adjustment side heat medium pump 51 and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping ability for the single cooling mode. Control the operation.

  Further, the control device 70 closes the on-off valve 15a for dehumidification and the on-off valve 15b for heating. The control device 70 controls the operation of the heat-absorbing three-way valve 63 as in the single cooling mode of the first embodiment.

  Accordingly, in the refrigeration cycle apparatus 10a in the single cooling mode, the discharge port of the compressor 11 → (water-refrigerant heat exchanger 12 → third three-way joint 13c → heating expansion valve 14d →) outdoor heat exchanger 16) → second. 5 Three-way joint 15e → first three-way joint 13a → first cooling expansion valve 14b → first chiller 19a → (second cooling expansion valve 14c →) second chiller 19b → second three-way joint 13b → evaporation pressure regulating valve 20 A refrigeration cycle in which the refrigerant circulates in the order of the accumulator 21 and the suction port of the compressor 11 is configured.

  With this circuit configuration, the control device 70 appropriately controls the operation of various control target devices, similarly to the single cooling mode of the first embodiment. The throttle opening of the first cooling expansion valve 14b is controlled such that the supercooling degree SC3 of the refrigerant flowing out of the outdoor heat exchanger 16 approaches the target supercooling degree SCO3.

  Therefore, in the refrigeration cycle apparatus 10a in the single cooling mode, a refrigeration cycle in which the outdoor heat exchanger 16 functions as a radiator and the first chiller 19a and the second chiller 19b function as an evaporator is configured. Therefore, the first chiller 19a can cool the heat medium on the temperature adjustment side. Further, the heat absorption side heat medium can be cooled by the second chiller 19b.

  As a result, in the vehicle air conditioner 1 in the single cooling mode, the battery 80 can be cooled without performing air conditioning in the vehicle compartment, as in the single cooling mode of the first embodiment.

  Further, in the refrigeration cycle apparatus 10a in the single cooling mode, the heat of the refrigerant discharged from the compressor 11 can be directly radiated to the outside air by the outdoor heat exchanger 16. Therefore, the heat exchange efficiency and the responsiveness are improved when the heat of the refrigerant discharged from the compressor 11 is indirectly radiated to the outside air by the high-temperature radiator 44 via the high-temperature heat medium. Can be.

(5) Single warm-up mode In the single warm-up mode, the control device 70 fully closes the cooling expansion valve 14a and the heating expansion valve 14d, fully opens the first cooling expansion valve 14b, and expands the second cooling expansion. The valve 14c is set in the throttled state. Further, the control device 70 stops the high-temperature side heat medium pump 41, and controls the temperature adjustment side heat medium pump 51 and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping ability for the single warm-up mode. Controls the operation of.

  Further, the control device 70 opens the dehumidifying on-off valve 15a and closes the heating on-off valve 15b. Further, the control device 70 controls the operation of the heat-absorbing three-way valve 63 as in the single warm-up mode of the first embodiment.

  Accordingly, in the refrigeration cycle apparatus 10a in the single warm-up mode, the discharge port of the compressor 11 → (water-refrigerant heat exchanger 12 → bypass passage 22a → first three-way joint 13a → first cooling expansion valve 14b →) A refrigeration cycle in which the refrigerant circulates in the order of 1 chiller 19a → second cooling expansion valve 14c → second chiller 19b → second three-way joint 13b → evaporation pressure adjusting valve 20 → accumulator 21 → suction port of compressor 11 is configured. .

  That is, in the refrigeration cycle device 10a in the single warm-up mode, a refrigeration cycle similar to that in the single warm-up mode in the first embodiment is configured. Other operations are the same as in the single warm-up mode of the first embodiment. Therefore, in the vehicle air conditioner 1 of the present embodiment, similarly to the single warm-up mode of the first embodiment, it is possible to maintain the temperature of the battery 80 within an appropriate temperature range without performing air conditioning of the vehicle interior. it can. Further, the in-vehicle device 82 can be cooled.

(6) Single Cooling Mode In the single cooling mode, the control device 70 closes the cooling expansion valve 14a, fully closes the first cooling expansion valve 14b, and fully opens the heating expansion valve 14d. Further, the control device 70 stops the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61. Further, the control device 70 closes the on-off valve 15a for dehumidification and the on-off valve 15b for heating.

  Thus, in the refrigeration cycle apparatus 10a in the single warm-up mode, the discharge port of the compressor 11 → (water-refrigerant heat exchanger 12 → heating expansion valve 14d →) outdoor heat exchanger 16 → fifth three-way joint 15e → 1 A three-way joint 13a → the cooling expansion valve 14a → the indoor evaporator 18 → the evaporation pressure regulating valve 20 → the accumulator 21 → the suction port of the compressor 11 constitutes a refrigeration cycle in which the refrigerant circulates in this order.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device, similarly to the cooling temperature control mode.

  Therefore, in the refrigeration cycle apparatus 10a in the single cooling mode, a refrigeration cycle in which the outdoor heat exchanger 16 functions as a radiator and the indoor evaporator 18 functions as an evaporator is configured. Therefore, the air blown by the indoor evaporator 18 can be cooled. As a result, in the vehicle air conditioner 1 in the single cooling mode, the inside of the vehicle compartment can be cooled in the same manner as in the cooling temperature control mode without adjusting the temperature of the battery 80.

  Further, in the refrigeration cycle apparatus 10a in the single cooling mode, the heat of the refrigerant discharged from the compressor 11 can be directly radiated to the outside air by the outdoor heat exchanger 16 as in the single cooling mode.

(7) Single Heating Mode In the single heating mode, in the single cooling mode, the control device 70 fully closes the cooling expansion valve 14a and the first cooling expansion valve 14b, and sets the heating expansion valve 14d to the throttled state. Further, the control device 70 controls the operation of the high-temperature side heat medium pump 41 and the temperature adjustment side heat medium pump 51 and the heat absorption side heat medium so as to exhibit a predetermined heat medium pumping ability for the single heating mode. The pump 61 is stopped.

  Further, the control device 70 closes the dehumidifying on-off valve 15a and opens the heating on-off valve 15b. Further, the control device 70 controls the operation of the high-temperature side three-way valve 43 so that the high-temperature side heat medium flowing out of the heater core 42 flows out to the suction port side of the high-temperature side heat medium pump 41, similarly to the heating temperature control mode. I do.

  Thereby, in the refrigeration cycle apparatus 10a in the single heating mode, the discharge port of the compressor 11, the water-refrigerant heat exchanger 12, the third three-way joint 13c, the heating expansion valve 14d, the outdoor heat exchanger 16, and the fifth three-way joint. 15e → the heating passage 22b → the accumulator 21 → the suction port of the compressor 11 constitutes a refrigeration cycle in which the refrigerant circulates in this order.

  With this circuit configuration, the control device 70 appropriately controls the operation of each control target device, similarly to the heating temperature control mode. The throttle opening of the heating expansion valve 14d is controlled such that the supercooling degree SC1 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 approaches the target supercooling degree SCO1.

  Therefore, in the refrigeration cycle apparatus 10a in the single heating mode, a refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a radiator and the outdoor heat exchanger 16 functions as an evaporator is configured. Therefore, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. As a result, in the vehicle air conditioner 1 in the single heating mode, the vehicle interior can be heated as in the cooling temperature adjustment mode without adjusting the temperature of the battery 80.

  As described above, the refrigeration cycle apparatus 10a according to the present embodiment performs operation modes such as a cooling temperature control mode, a dehumidifying heating temperature control mode, a heating temperature control mode, a single cooling mode, a single warming mode, a single cooling mode, and a single heating mode. By switching, air conditioning in the vehicle compartment and temperature adjustment of the battery 80 can be performed.

  Further, in the refrigeration cycle device 10a of the present embodiment, as in the first embodiment, the air blown into the vehicle interior, which is the space to be air-conditioned, in the cooling temperature adjustment mode, the dehumidification heating temperature adjustment mode, and the heating temperature adjustment mode. Appropriate temperature adjustment of the air and appropriate temperature adjustment of the battery 80, which is a temperature adjustment target different from the blast air, can be compatible.

  Further, in the refrigeration cycle device 10a of the present embodiment, in the cooling temperature control mode, the dehumidification heating temperature control mode, and the heating temperature control mode, the temperature of the battery 80 is adjusted by changing the opening degree ratio EX1 / EX2. I have. Therefore, similarly to the first embodiment, it is possible to achieve both the appropriate temperature adjustment of the battery 80 and the suppression of the temperature fluctuation of the blown air due to the temperature adjustment of the battery 80.

  In the refrigeration cycle device 10a of the present embodiment, the operation in the dehumidifying and heating temperature control mode can be performed. Therefore, in the vehicle air conditioner 1 of the present embodiment, more comfortable air conditioning in the vehicle interior can be realized.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, an example is described in which the refrigeration cycle devices 10 and 10a according to the present invention are applied to the vehicle air conditioner 1 mounted on an electric vehicle, and the temperature adjustment target is the battery 80. The application of the present invention is not limited to this.

  For example, the present invention may be applied to a vehicle air conditioner mounted on a hybrid vehicle that obtains driving power for vehicle running from both an engine and an electric motor. Furthermore, the temperature adjustment target is not limited to the battery 80, but may be an in-vehicle device 82. Further, the application of the present invention is not limited to a vehicle, but may be applied to an air conditioner having a server temperature adjusting function for performing indoor air conditioning while appropriately adjusting the temperature of a computer server.

  (2) In the above-described embodiment, the refrigeration cycle apparatuses 10 and 10a that can be switched to a plurality of operation modes have been described. However, the switching of the operation mode is not limited to the one disclosed in the above-described embodiment.

  At least, if the operation of the cooling temperature adjustment mode and the heating temperature adjustment mode is executable, the effect of achieving both the appropriate temperature adjustment of the blown air and the appropriate temperature adjustment of the temperature adjustment target can be achieved. Obtainable. Further, at least, if the operation in the heating temperature adjustment mode can be performed, realization of appropriate temperature adjustment of the temperature adjustment target and suppression of temperature fluctuation of the blown air due to performing the temperature adjustment of the temperature adjustment target. Can be obtained.

  Furthermore, in the cooling temperature adjustment mode and the heating temperature adjustment mode of the above-described embodiment, an example has been described in which the control device 70 decreases the opening degree ratio EX1 / EX2 with an increase in the battery temperature TB, but is not limited thereto. . If the opening ratio EX1 / EX2 can be reduced with the rise in the temperature of the temperature adjustment target, the control device 70 sets the opening ratio EX1 / EX2 based on another parameter correlated with the temperature of the temperature adjustment target. EX2 may be changed.

  For example, the opening degree ratio EX1 / EX2 may be decreased with an increase in the temperature adjustment-side heat medium temperature TWC1. Further, a detector is provided for detecting the temperature of the temperature-adjusting-side heat medium immediately after flowing out of the temperature-adjusting heat exchanging unit 52. With the rise in the temperature detected by this detector, the opening ratio EX1 / EX2 is determined. You may make it decrease.

  In addition, as the operation mode of the refrigeration cycle apparatus 10a described in the second embodiment, a heating temperature control mode using the outdoor heat exchanger 16 may be performed. For example, as the heating temperature control mode using the outdoor heat exchanger 16, a series heating temperature control mode and a parallel heating temperature control mode may be performed.

  In the series heating temperature control mode, the control device 70 fully closes the cooling expansion valve 14a, and sets the first cooling expansion valve 14b, the second cooling expansion valve 14c, and the heating expansion valve 14d to a throttled state. Further, the control device 70 controls the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping ability for the series heating temperature control mode. Control the operation.

  Further, the control device 70 closes the dehumidifying on-off valve 15a and closes the heating on-off valve 15b. The control device 70 controls the operation of the high-temperature three-way valve 43 and the heat-absorbing three-way valve 63 as in the heating temperature control mode of the first embodiment.

  Thereby, in the refrigerating cycle device 10a in the series heating temperature control mode, the discharge port of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14d, the outdoor heat exchanger 16, the fifth three-way joint 13e, and the fourth. Three-way joint 13d → first three-way joint 13a → first cooling expansion valve 14b → first chiller 19a → second cooling expansion valve 14c → second chiller 19b → second three-way joint 13b → evaporation pressure regulating valve 20 → accumulator 21 → A refrigeration cycle in which the refrigerant circulates in the order of the suction port of the compressor 11 is configured. That is, a refrigeration cycle in which the outdoor heat exchanger 16, the first chiller 19a, and the second chiller 19b are connected in series is configured.

  According to this, since the refrigerant and the outside air can be heat-exchanged in the outdoor heat exchanger 16, the cycle can be easily balanced with the cycle in the heating temperature control mode described in the second embodiment.

  That is, by increasing the throttle opening of the heating expansion valve 14d and raising the temperature of the refrigerant flowing into the outdoor heat exchanger 16 above the outdoor temperature Tam, the outdoor heat exchanger 16 can function as a radiator. it can. Further, by reducing the throttle opening of the heating expansion valve 14d and lowering the temperature of the refrigerant flowing into the outdoor heat exchanger 16 below the outside air temperature Tam, the outdoor heat exchanger 16 can function as an evaporator. it can.

  In the parallel heating temperature control mode, the control device 70 fully closes the cooling expansion valve 14a, and sets the first cooling expansion valve 14b, the second cooling expansion valve 14c, and the heating expansion valve 14d to a throttled state. Further, the control device 70 controls the high-temperature side heat medium pump 41, the temperature adjustment side heat medium pump 51, and the heat absorption side heat medium pump 61 so as to exhibit a predetermined heat medium pumping ability for the series heating temperature control mode. Control the operation.

  Further, the control device 70 opens the dehumidifying on-off valve 15a and opens the heating on-off valve 15b. The control device 70 controls the operation of the high-temperature three-way valve 43 and the heat-absorbing three-way valve 63 as in the heating temperature control mode of the first embodiment.

  Thereby, in the refrigerating cycle device 10a in the parallel heating temperature control mode, the discharge port of the compressor 11, the water-refrigerant heat exchanger 12, the third three-way joint 13c, the heating expansion valve 14d, the outdoor heat exchanger 16, and the fifth heat exchanger. The refrigerant circulates in the order of the three-way joint 13e → the heating passage 22b → the accumulator 21 → the suction port of the compressor 11.

  Further, the discharge port of the compressor 11 → the water-refrigerant heat exchanger 12 → the third three-way joint 13c → the bypass passage 22a → the fourth three-way joint 13d → the first three-way joint 13a → the first cooling expansion valve 14b → the first chiller. A refrigeration cycle in which the refrigerant circulates in the order of 19a → second cooling expansion valve 14c → second chiller 19b → second three-way joint 13b → evaporation pressure regulating valve 20 → accumulator 21 → suction port of compressor 11 is formed.

  That is, in the refrigerating cycle device 10a in the parallel heating temperature control mode, the path through which the refrigerant flows in the order of the heating expansion valve 14d → the outdoor heat exchanger 16, the first cooling expansion valve 14b → the first chiller 19a → the second cooling expansion. The path in which the refrigerant flows in the order of the valve 14c and the second chiller 19b is switched to a refrigerant circuit connected in parallel with the refrigerant flow.

  In this cycle configuration, the control device 70 controls the operation of the heating expansion valve 14d so that the temperature of the refrigerant flowing into the outdoor heat exchanger 16 becomes lower than the outside air temperature Tam.

  According to this, regardless of the refrigerant evaporation temperature in the first chiller 19a and the refrigerant evaporation temperature in the second chiller 19b, the outdoor heat exchanger 16 allows the refrigerant to absorb heat from the outside air. Further, by reducing the throttle opening of the heating expansion valve 14d, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 from the outside air can be increased.

  Therefore, the heating capacity of the high-temperature side heat medium in the water-refrigerant heat exchanger 12 can be improved as compared with the serial heating temperature control mode. As a result, it is possible to improve the possible capacity of the blown air as compared with the series heating temperature control mode.

  Further, switching of each operation mode is not limited to the mode disclosed in each of the above embodiments. For example, a switch for switching may be provided on the operation panel 701, and each operation mode may be switched by the operation of the occupant.

  (3) The configurations of the refrigeration cycle devices 10 and 10a are not limited to those disclosed in the above-described embodiment. For example, as the cooling expansion valve 14a, the first cooling expansion valve 14b, or the like, a valve in which an electric expansion valve having no fully closed function and an on-off valve may be directly connected may be employed. Further, a plurality of cycle components may be integrated.

  Further, in the above-described embodiment, the example in which the electric variable throttle mechanism is employed as the first cooling expansion valve 14b and the second cooling expansion valve 14c has been described, but the present invention is not limited to this. If the opening ratio EX1 / EX2 can be appropriately changed, for example, an electric variable throttle mechanism is adopted for one of the first cooling expansion valve 14b and the second cooling expansion valve 14c, and the other is used for the other. Alternatively, a fixed throttle or a thermal expansion valve may be employed.

  As such a temperature-type expansion valve, a temperature-sensitive portion having a deformable member (specifically, a diaphragm) that deforms according to the temperature and pressure of the refrigerant flowing out of the refrigerant passage of the second chiller 19b, It is possible to employ a mechanical mechanism including a valve body that changes in accordance with the deformation and changes the opening degree of the throttle. Then, the throttle opening may be changed so that the superheat degree SHC2 of the refrigerant flowing out of the refrigerant passage of the second chiller 19b approaches the target superheat degree SHCO2.

  Further, in the above-described embodiment, an example has been described in which the accumulator 21 is employed as the surplus refrigerant storage unit that stores the surplus refrigerant of the cycle as a low-pressure liquid-phase refrigerant, but the surplus refrigerant storage unit is not limited to this. For example, a receiver that separates gas-liquid of the high-pressure refrigerant flowing into the inside and stores the excess refrigerant in the cycle as a high-pressure liquid-phase refrigerant may be adopted. For example, in the refrigeration cycle apparatus 10, a receiver may be arranged on the outlet side of the refrigerant passage of the water-refrigerant heat exchanger 12. Further, both the accumulator 21 and the receiver may be employed.

  Further, in the above-described embodiment, an example in which R1234yf is employed as the refrigerant has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be adopted. Alternatively, a mixed refrigerant obtained by mixing a plurality of types of these refrigerants may be employed. Further, a supercritical refrigeration cycle in which carbon dioxide is used as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.

  In addition, the control mode of the refrigeration cycle devices 10 and 10a is not limited to those disclosed in the above embodiments. For example, the operation of the actuator for the air mix door may be controlled such that the blast air temperature TAV detected by the conditioned air temperature sensor 79 approaches the target outlet temperature TAO.

  Further, in the above-described embodiment, an example in which the opening ratio EX1 / EX2 is decreased with an increase in the battery temperature TB, but the opening ratio EX1 / EX2 is decreased with an increase in the amount of heat generated by the battery 80. May be. The heat value of the battery 80 may be detected from the internal current flowing through the battery 80 and the like.

  (4) In the above-described embodiment, the heating unit configured by the respective components of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 is employed, but the heating unit is not limited to this. For example, an indoor condenser that directly exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and the blown air may be adopted, and the indoor condenser may be arranged in the air-conditioning case 31 like the heater core 42.

  Further, when the refrigeration cycle devices 10 and 10a are applied to a vehicle air conditioner mounted on a hybrid vehicle or the like, the engine cooling water may flow into the high-temperature side heat medium circuit 40 and circulate. Good. According to this, the blower air can be heated by the heater core 42 using the waste heat of the engine as a heat source.

  Further, in the above-described embodiment, the temperature adjustment unit configured by the respective components of the first chiller 19a and the temperature adjustment-side heat medium circuit 50 is employed, but the temperature adjustment unit is not limited to this. As the temperature adjustment unit, a temperature adjustment heat exchange unit that directly exchanges heat between the battery 80 and the refrigerant flowing out of the first cooling expansion valve 14b may be employed.

  Further, as a temperature adjusting section, a heat exchanger for exchanging heat between the refrigerant flowing out of the first cooling expansion valve 14b and the blast air for temperature adjustment, and the blast air for temperature adjustment whose temperature is adjusted by the heat exchanger. A temperature adjusting blower that blows to the battery 80 may be employed.

  Further, in the above-described embodiment, the heat absorbing portion constituted by the respective components of the second chiller 19b and the heat absorbing side heat medium circuit 60 is employed, but the heat absorbing portion is not limited to this. A refrigerant passage formed in the vehicle-mounted device 82 may be adopted as the heat absorbing unit, and the refrigerant flowing out of the second cooling expansion valve 14c may be allowed to flow through this refrigerant passage.

  In addition, the high-temperature side heat medium circuit 40, the temperature adjustment side heat medium circuit 50, and the heat absorption side heat medium circuit 60 described in the above-described embodiment are connected to each other via an on-off valve or the like, and the high-temperature side heat medium, the temperature adjustment side The heat medium and the heat absorption side heat medium may be mixed.

  Then, for example, the high-temperature-side heat medium circuit 40 and the temperature-adjustment-side heat medium circuit 50 are connected, and the heat-absorbing-side heat medium that has absorbed the waste heat of the vehicle-mounted device 82 flows into the high-temperature-side heat medium circuit 40 and is circulated. You may do so. According to this, the blown air can be heated by the heater core 42 using the waste heat of the vehicle-mounted device 82 as a heat source.

  Further, the control mode of the high-temperature side three-way valve 43 of the high-temperature side heat medium circuit 40 and the heat absorption side three-way valve 63 of the heat absorption side heat medium circuit 60 are not limited to those disclosed in the above-described embodiments.

  For example, in the cooling temperature control mode, the heat absorbing side three-way valve 63 may be operated so that the heat absorbing side heat medium flowing out of the cooling water passage of the vehicle-mounted device 82 flows into the heat absorbing side radiator 64. In the heating temperature control mode, the heat absorption side three-way valve 63 is configured to guide the heat absorption side heat medium flowing out of the cooling water passage of the vehicle-mounted device 82 to the suction side of the heat absorption side heat medium pump 61 by bypassing the heat absorption side radiator 64. May be activated.

  (5) In the above-described embodiment, an example has been described in which the temperature adjustment target whose temperature is adjusted by the degree adjustment unit is the battery 80 and the heat absorption target that is cooled by the heat absorption unit is the vehicle-mounted device 82. The temperature adjustment target and the heat absorption target are not limited to these. For example, when the refrigeration cycle devices 10 and 10a are applied to an air conditioner for a vehicle that does not require warming up of the battery 80, the temperature adjustment target may be the vehicle-mounted device 82 and the heat absorption target may be the battery 80.

  According to this, it is possible to achieve both the appropriate temperature adjustment of the vehicle-mounted device 82 as the temperature adjustment target and the suppression of the temperature fluctuation of the blast air due to the temperature adjustment of the vehicle-mounted device 82.

  Further, under the operating condition in which the temperature of the refrigerant flowing into the first chiller 19a is lower than the temperature of the heat medium on the adjustment side every time the refrigerant flows into the first chiller 19a, the second cooling expansion valve 14c has a second opening degree EX2 relative to the throttle opening degree EX2. By adjusting the opening ratio EX1 / EX2 of the throttle opening EX1 of the first cooling expansion valve 14b, the cooling capacity exerted by the first chiller 19a and the cooling capacity exerted by the second chiller 19b are adjusted. Can be adjusted appropriately.

  In other words, by adjusting the opening degree ratio EX1 / EX2, the cooling capacity that can be exhibited by the refrigeration cycle device 10 can be appropriately distributed to the first chiller 19a and the second chiller 19b.

10, 10a Refrigeration cycle device 11 Compressor 12 Water-refrigerant heat exchanger (heating unit)
13a, 13b First three-way joint (branch), second three-way joint (merge)
14a Decompression unit for cooling (decompression unit for cooling)
14b first cooling expansion valve (first cooling pressure reducing unit)
14c Second cooling expansion valve (second cooling decompression unit)
19a, 19b 1st chiller (temperature adjustment part), 2nd chiller (heat absorption part)
40 High-temperature side heating medium circuit (heating section)
50 Temperature control side heat medium circuit (temperature control section)
60 Heat absorption side heat transfer circuit (heat absorption section)
80, 82 Battery (object of temperature adjustment), In-vehicle equipment (object of heat absorption)

Claims (6)

A refrigeration cycle device applied to an air conditioner,
A compressor (11) for compressing and discharging the refrigerant;
A heating unit (12, 40) for heating blast air blown to the air-conditioned space using the refrigerant discharged from the compressor as a heat source;
A first cooling decompression unit (14b) for decompressing the refrigerant flowing out of the heating unit;
A temperature adjustment unit (19a, 50) for adjusting the temperature of the temperature adjustment target (80) by the refrigerant flowing out of the first cooling decompression unit;
A second cooling decompression unit (14c) for decompressing the refrigerant flowing out of the temperature adjustment unit,
A heat absorbing section (19b, 60) for cooling the heat absorbing object (82) by the refrigerant flowing out of the cooling pressure reducing section;
In a heating temperature control mode in which the blast air is heated by the heating unit and the temperature of the temperature adjustment target is adjusted by the temperature adjustment unit, the temperature of the second cooling decompression unit with respect to the throttle opening (EX2) is reduced. A refrigeration cycle apparatus that adjusts the temperature of the temperature adjustment target by changing the opening ratio (EX1 / EX2) of the throttle opening (EX1) of the first cooling decompression unit. A decompression unit control unit (70b) for controlling at least one of the first cooling decompression unit and the second cooling decompression unit;
2. The refrigeration cycle according to claim 1, wherein the pressure reducing unit control unit reduces the opening degree ratio (EX1 / EX2) with an increase in the temperature of the temperature adjustment target in the heating temperature control mode. 3. apparatus. Furthermore, a compressor control unit (70a) for controlling the operation of the compressor is provided,
The compressor control unit controls the operation of the compressor such that the temperature of the blown air heated by the heating unit approaches the target temperature (TAO) of the blown air in the heating temperature control mode. The refrigeration cycle apparatus according to claim 1 or 2, wherein A heating decompression unit (14d) for decompressing the refrigerant flowing out of the heating unit;
An outdoor heat exchanger (16) for exchanging heat between the refrigerant flowing out of the heating decompression unit and the outside air to flow out to the upstream side of the branch unit;
A bypass passage (22a) that guides the refrigerant flowing out of the heating unit to the upstream side of the branch unit by bypassing the outdoor heat exchanger;
The refrigeration cycle apparatus according to any one of claims 1 to 3, further comprising a heating passage (22b) for guiding the refrigerant flowing out of the outdoor heat exchanger to a suction port side of the compressor. The heating section includes a water-refrigerant heat exchanger (12) for exchanging heat between the refrigerant discharged from the compressor and the high-temperature side heat medium, and a heater core for exchanging heat between the high-temperature side heat medium and the blown air. 42)
When the heating switching condition for switching from the single heating mode for heating the blast air at the heating unit to the heating temperature control mode without adjusting the temperature of the temperature adjustment target is satisfied, the single heating mode is switched to the single heating mode. The refrigeration cycle apparatus according to any one of claims 1 to 4, wherein the temperature of the high-temperature side heat medium is increased before switching to the heating temperature control mode. A heat exchange unit configured to exchange heat between the refrigerant flowing out of the first cooling decompression unit and the heat medium on the temperature adjustment side, and the temperature adjustment unit temperature-controlled by the heat exchange unit. A temperature control heat exchange unit (52) for exchanging heat between the heat medium and the temperature control target;
When the warm-up switching condition for switching from the single warm-up mode in which the temperature adjustment target is heated by the temperature adjusting unit to the heating temperature control mode without adjusting the temperature of the blast air is satisfied, the single warm-up is performed. The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the temperature of the temperature adjustment-side heat medium is increased before switching from the heating mode to the heating temperature adjustment mode.

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