JP2019219121A - Refrigeration cycle device - Google Patents

Abstract

To provide a refrigeration cycle device capable of sufficiently cooling blown air to be distributed to an air conditioned-space and a cooling object without exhibiting excessive cooling capacity and heating capacity.SOLUTION: During an air-heating mode for heating a cabin, a refrigerant circuit switching part of a refrigeration cycle device switches a refrigerant circuit to a refrigerant circuit constituting a normal vapor compression type refrigeration cycle for radiating a refrigerant discharged from a compressor 11 at a water-refrigerant heat exchanger 12 constituting a heating portion for heating blown air to be distributed to an air-conditioned space. During an air-cooling + cooling mode for cooling the inside of the cabin and also cooling a battery 80 as a cooling object, the refrigerant circuit switching part of the refrigeration cycle device switches a refrigerant circuit to a refrigerant circuit constituting a gas injection cycle by connecting an indoor evaporator 18 for cooling the blown air and a chiller 19 constituting a cooling portion of the battery 80 in parallel with each other and evaporating the refrigerant by both of them. Further, a flow of an over-cooled liquid phase refrigerant is branched at a fifth three-way joint 15e as a downstream-side branch portion to flow out to an indoor evaporator 18 side and a chiller 19 side.SELECTED DRAWING: Figure 1

Description

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

  BACKGROUND ART Conventionally, Patent Literature 1 discloses a refrigeration cycle device that is applied to an air conditioner for a vehicle mounted on an electric vehicle and adjusts the temperature of blast air blown into a vehicle room, which is a space to be air conditioned. In the refrigeration cycle device of Patent Document 1, heating or cooling of the blown air is performed by switching the refrigerant circuit.

  More specifically, in the refrigerating cycle device of Patent Literature 1, a switching is made to a refrigerant circuit constituting a so-called gas injection cycle in a heating mode in which blast air is heated and blown into the vehicle interior. In this type of gas injection cycle, the compression efficiency of the compressor is improved by combining the intermediate-pressure refrigerant generated in the cycle with the refrigerant in the pressurization process in the compressor, and the coefficient of performance (COP) of the cycle is improved. Can be done.

  That is, in the refrigeration cycle device of Patent Document 1, in the heating mode in which the pressure difference between the refrigerant condensation pressure in the indoor condenser functioning as a radiator and the refrigerant evaporation pressure in the outdoor heat exchanger functioning as an evaporator tends to increase, Switch to the refrigerant circuit that constitutes the injection cycle. As a result, the COP is improved, and the heating capacity of the blown air exerted in the indoor condenser is to be improved.

Japanese Patent No. 5780166

  Incidentally, an electric vehicle is equipped with a secondary battery (that is, a battery) for supplying electric power to a traveling electric motor or the like. The output of this type of 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 which the performance of the battery can be sufficiently exhibited. Therefore, it is conceivable to adjust the temperature of the battery using the refrigeration cycle device of Patent Document 1.

  However, according to the study of the present inventors, even if an attempt is made to cool the battery together with the blast air by the cooling capacity exhibited by the indoor evaporator of the refrigeration cycle device of Patent Document 1, both the blast air and the battery are sufficiently increased. Could not be cooled. This is because the refrigeration cycle device of Patent Literature 1 does not have a specification capable of exerting the cooling capacity required for cooling the battery in addition to the cooling capacity required for cooling the blown air.

  On the other hand, if the specifications of the refrigeration cycle device of Patent Literature 1 are changed so that both the blast air and the battery can be sufficiently cooled, excessive cooling capacity and heating capacity are exhibited in another operation mode, The cycle cannot be operated efficiently. Furthermore, in order to properly cool both the blast air and the battery, the cooling capacity exhibited by the refrigeration cycle device must be appropriately distributed for cooling both.

  In view of the above, the present invention provides a refrigeration cycle device capable of sufficiently cooling the blast air blown into a space to be air-conditioned and an object to be cooled without exerting excessive cooling capacity or heating capacity. The purpose is to:

  It is another object of the present invention to provide a refrigeration cycle device that can appropriately cool blast air blown into a space to be air-conditioned and an object to be cooled.

In order to achieve the above object, the invention according to claim 1 compresses a low-pressure refrigerant sucked from a suction port (11a) until it becomes a high-pressure refrigerant and discharges the compressed low-pressure refrigerant from a discharge port (11c). A compressor (11) having an intermediate pressure suction port (11b) for allowing a refrigerant to flow therein and join the refrigerant in a compression process, and a blown air blown into a space to be air-conditioned using a high-pressure refrigerant discharged from the compressor as a heat source. A heating unit (40) for heating, a heating expansion valve (14a) for reducing the pressure of the refrigerant flowing from the heating unit, and an outdoor heat exchanger (16) for exchanging heat between the refrigerant flowing from the heating expansion valve and the outside air. An upstream branch (13g) for branching the flow of the refrigerant flowing out of the outdoor heat exchanger, and an intermediate pressure passage (22c) for guiding one of the refrigerants branched at the upstream branch to the intermediate pressure suction port side. Flows through the intermediate pressure passage An intermediate pressure expansion valve (14d, 141) for reducing the pressure of the medium to an intermediate pressure refrigerant, an intermediate temperature side passage (23a) for flowing the intermediate pressure refrigerant reduced in pressure by the intermediate pressure expansion valve, and an upstream branch portion. An internal heat exchanger (23) having a high-temperature side passage (23b) through which the other branched refrigerant flows, and exchanging heat between the intermediate-pressure refrigerant flowing through the intermediate-temperature side passage and the refrigerant flowing through the high-temperature side passage; A downstream branch (13e) for branching the flow of the refrigerant flowing out of the high-temperature side passage; and a cooling expansion valve (14b) for reducing the pressure of one of the refrigerants branched at the downstream branch to a low-pressure refrigerant. And an indoor evaporator (18) for evaporating the refrigerant flowing out of the cooling expansion valve to cool the blown air, and for cooling the other refrigerant branched at the downstream branch to a low-pressure refrigerant. Expansion valve (14c), cooling expansion (50, 52a) for evaporating the refrigerant flowing out of the cooling unit to cool the object to be cooled (80), and joining the flow of the refrigerant flowing out of the indoor evaporator and the flow of the refrigerant flowing out of the cooling unit. A joining section (13f) for allowing the refrigerant to flow out to the suction port side of the compressor, a heating passage (22b) for guiding the refrigerant flowing out of the outdoor heat exchanger to the suction port side of the compressor, and a refrigerant circuit switching section for switching the refrigerant circuit. (15a to 15e), and
The refrigerant circuit switching unit is
In the heating mode, in which the blast air is heated by the heating unit, the refrigerant circuit circulates the refrigerant in the order of compressor outlet → heating unit → heating expansion valve → outdoor heat exchanger → heating passage → compressor inlet. switching,
In the cooling + cooling mode, in which the blown air is cooled by the indoor evaporator and the object to be cooled is cooled by the cooling unit, the compressor outlet → heating expansion valve → outdoor heat exchanger → upstream branch section → middle The refrigerant circulates in the order of pressure expansion valve → intermediate temperature side passage → intermediate pressure suction port of the compressor, and furthermore, upstream branch section → high temperature side passage → downstream side branch section → cooling expansion valve → indoor evaporator → junction section → Recirculate the refrigerant in the order of the compressor suction port, and circulate the refrigerant in the order of the upstream branch section → the high temperature side passage → the downstream branch section → the expansion valve for cooling → the cooling section → the junction section → the suction port of the compressor. This is a refrigeration cycle device that switches to a refrigerant circuit.

  According to this, in the heating mode, a normal vapor compression refrigeration cycle is configured. Then, by blowing the blast air heated by the heating unit (40) to the space to be air-conditioned, the space to be air-conditioned can be heated.

  In the cooling / cooling mode, a gas injection cycle is configured in which the indoor evaporator (18) and the cooling units (50, 52a) are connected in parallel to the refrigerant flow. Then, by blowing the blast air cooled by the indoor evaporator (18) to the air-conditioned space, the air-conditioned space can be cooled. Further, the cooling object (80) can be cooled by the cooling units (50, 52a).

  That is, in the operation mode in which the heat load of the refrigeration cycle device is increased to cool both the blast air and the object to be cooled, as in the cooling / cooling mode, the gas injection cycle is configured, and as in the heating mode, A normal refrigeration cycle can be configured in the operation mode in which the heat load of the refrigeration cycle device is lower than in the cooling + cooling mode.

  Therefore, even if both the blown air and the object to be cooled (80) are sufficiently cooled in the cooling / cooling mode, an excessive heating capacity is not exhibited in the heating mode, and the heating mode is efficient. Can be activated.

  That is, according to the first aspect of the present invention, in the heating mode, the refrigeration cycle apparatus capable of sufficiently cooling the blast air and the object to be cooled (80) without exhibiting excessive heating capacity and cooling capacity. Can be provided.

According to the second aspect of the invention, the low-pressure refrigerant sucked from the suction port (11a) is compressed to a high-pressure refrigerant and discharged from the discharge port (11c), and the intermediate-pressure refrigerant in the cycle is caused to flow. A compressor (11) having an intermediate pressure suction port (11b) for joining the refrigerant in the compression process, an outdoor heat exchanger (16) for exchanging heat between the refrigerant discharged from the compressor and the outside air, and an outdoor heat exchanger An upstream branch portion (13g) for branching the flow of the refrigerant flowing out of the first branch portion, an intermediate pressure passage (22c) for guiding one of the refrigerants branched at the upstream branch portion to the intermediate pressure suction port side, and an intermediate pressure passage. An intermediate pressure expansion valve (14d, 141) for reducing the flowing refrigerant to an intermediate pressure refrigerant, an intermediate temperature side passage (23a) for flowing the intermediate pressure refrigerant depressurized by the intermediate pressure expansion valve, and an upstream branch portion The other refrigerant branched at An internal heat exchanger (23) having a high-temperature side passageway (23b) through which heat flows between the intermediate-pressure refrigerant flowing through the intermediate-temperature side passage and the refrigerant flowing through the high-temperature side passageway; A downstream branch (13e) for branching the flow of the cooled refrigerant, an expansion valve for cooling (14b) for reducing the pressure of one of the refrigerants branched at the downstream branch to a low-pressure refrigerant, and an expansion valve for cooling. An indoor evaporator (18) for evaporating the outflowing refrigerant to cool the blown air, a cooling expansion valve (14c) for decompressing the other refrigerant branched at the downstream branch portion to a low-pressure refrigerant, The cooling unit (50, 52a) for evaporating the refrigerant flowing out of the cooling expansion valve to cool the object to be cooled, and joining the flow of the refrigerant flowing out of the indoor evaporator and the flow of the refrigerant flowing out of the cooling unit. To flow out to the suction side of the compressor Flow section (13f), a refrigerant circuit switching section (15a to 15e) for switching a refrigerant circuit, and an expansion valve control section (14b) for controlling at least one of a cooling expansion valve (14b) and a cooling expansion valve (14c). 60b).
In the cooling + cooling mode, which cools the air blown by the indoor evaporator and cools the object to be cooled by the cooling unit, the refrigerant circuit switching unit is a discharge port of the compressor → a heating expansion valve → an outdoor heat exchanger → The refrigerant is circulated in the order of upstream branch section → intermediate pressure expansion valve → intermediate temperature side passage → intermediate pressure suction port of the compressor, and furthermore, upstream branch section → high temperature side passage → downstream branch section → cooling expansion valve → In addition to circulating the refrigerant in the order of the indoor evaporator → the junction → the compressor inlet, the upstream branch → the high-temperature passage → the downstream branch → the cooling expansion valve → the cooling unit → the junction → the compressor inlet Is switched to a refrigerant circuit that circulates the refrigerant in the order of
In the cooling + cooling mode, the expansion valve controller controls at least one of the cooling expansion valve (14b) and the cooling expansion valve (14c) so that the refrigerant flowing into the downstream branch becomes a high-pressure refrigerant having a supercooling degree. This is a refrigeration cycle device that controls one operation.

  According to this, in the cooling + cooling mode, a gas injection cycle is configured in which the indoor evaporator (18) and the cooling units (50, 52a) are connected in parallel to the refrigerant flow. Then, by blowing the blast air cooled by the indoor evaporator (18) to the space to be air-conditioned, the space to be air-conditioned can be cooled. Further, the cooling object (80) can be cooled by the cooling units (50, 52a).

  Further, the expansion valve control unit (60b) controls the cooling expansion valve (14b) and the cooling expansion valve (14c) so that the refrigerant flowing into the downstream branch portion (13e) becomes a high-pressure refrigerant having a degree of supercooling. Is controlled. Thereby, the flow of the liquid-phase refrigerant can be branched at the downstream branch portion (13e).

  Therefore, when the flow of the gas-liquid two-phase refrigerant is branched at the downstream branch part (13e), the flow rate (mass flow rate) of the refrigerant flowing into the indoor evaporator (18) via the cooling expansion valve (14b) ) And the flow rate (mass flow rate) of the refrigerant flowing into the cooling sections (50, 52a) via the cooling expansion valve (14c) can be adjusted with high accuracy.

  That is, according to the second aspect of the present invention, it is possible to provide a refrigeration cycle apparatus capable of appropriately cooling the blast air and the object to be cooled (80) in the cooling + cooling mode.

  The symbols in parentheses of each means described in this section and in the claims indicate 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. It is a flowchart which shows a part of control processing of the air conditioning control program of the first embodiment. It is a flowchart which shows another part of control processing of the air-conditioning control program of 1st Embodiment. It is a control characteristic figure for switching the operation mode of the air-conditioning control program of a 1st embodiment. It is another control characteristic figure for switching the operation mode of the air-conditioning control program of 1st Embodiment. It is another control characteristic figure for switching the operation mode of the air-conditioning control program of 1st Embodiment. It is a flowchart which shows the control processing of the cooling mode of 1st Embodiment. FIG. 4 is a Mollier chart showing a change in the state of the refrigerant in the refrigeration cycle device in the cooling mode according to the first embodiment. It is a flow chart which shows control processing of the series dehumidification heating mode of a 1st embodiment. It is a control characteristic figure for determining the opening degree pattern of the expansion valve for heating and the expansion valve for cooling in the series dehumidification heating mode of a 1st embodiment. It is a flow chart which shows control processing of a parallel dehumidification heating mode of a 1st embodiment. It is a control characteristic figure for determining the opening degree pattern of the expansion valve for heating and the expansion valve for cooling in the parallel dehumidification heating mode of a 1st embodiment. It is a flowchart which shows the control processing of the heating mode of 1st Embodiment. It is a flow chart which shows control processing of cooling + cooling mode of a 1st embodiment. FIG. 4 is a Mollier chart showing a change in the state of the refrigerant in the refrigeration cycle apparatus in the cooling + cooling mode according to the first embodiment. It is a flow chart which shows control processing of a series dehumidification heating + cooling mode of a 1st embodiment. It is a flow chart which shows control processing of parallel dehumidification heating + cooling mode of a 1st embodiment. It is a flowchart which shows the control processing of the heating + cooling mode of 1st Embodiment. It is a flow chart which shows control processing of heating + series cooling mode of a 1st embodiment. FIG. 4 is a control characteristic diagram for determining an opening degree pattern of a heating expansion valve and a cooling expansion valve in a heating + series cooling mode according to the first embodiment. It is a flow chart which shows control processing of heating + parallel cooling mode of a 1st embodiment. FIG. 5 is a control characteristic diagram for determining an opening degree pattern of the heating expansion valve and the cooling expansion valve in the heating + parallel cooling mode of the first embodiment. It is a flowchart which shows the control processing of the cooling mode of 1st Embodiment. FIG. 4 is a Mollier chart showing a change in the state of the refrigerant in the refrigeration cycle device in the cooling mode according to the first embodiment. It is a whole block diagram of the vehicle air conditioner of 2nd Embodiment. It is a whole block diagram of the air conditioner for vehicles of 3rd Embodiment. It is a whole block diagram of the air conditioner for vehicles of 4th Embodiment. It is a Mollier diagram showing change of a state of a refrigerant in a refrigeration cycle device at the time of heating mode of a 4th embodiment. It is the whole block diagram of the air conditioner for vehicles of other embodiments.

(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 adjusting the temperature of the battery 80 as well as performing air conditioning of a vehicle interior, which is a space to be air-conditioned. For this reason, the vehicle air conditioner 1 can also be called an air conditioner with a battery temperature adjusting 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 this type of 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, 15 ° C. or more and 55 ° C. or less) in which the charge / discharge capacity of the battery can be sufficiently utilized. .

  Therefore, in the vehicle air conditioner 1, the battery 80 can be cooled by the cold generated by the refrigeration cycle device 10. Therefore, the cooling object different from the blast air in the refrigeration cycle device 10 of the present embodiment is the battery 80.

  The vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioning unit 30, a high-temperature heat medium circuit 40, a low-temperature heat medium circuit 50, and the like, as shown in the overall configuration diagram of FIG.

  The refrigeration cycle device 10 has a function of cooling the air blown into the vehicle interior and a function of heating the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40 in order to perform air conditioning in the vehicle interior. Further, the refrigeration cycle apparatus 10 has a function of cooling the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50 in order to cool the battery 80.

  The refrigeration cycle device 10 is configured to be able to switch refrigerant circuits for various operation modes in order to perform air conditioning in the vehicle interior. For example, it is configured such that a refrigerant circuit in a cooling mode, a refrigerant circuit in a dehumidifying and heating mode, a refrigerant circuit in a heating mode, and the like can be switched. Further, the refrigeration cycle apparatus 10 can switch between an operation mode for cooling the battery 80 and an operation mode for not cooling the battery 80 in each operation mode for air conditioning.

  In the refrigeration cycle device 10, an HFO-based refrigerant (specifically, R1234yf) is employed as a refrigerant, and the pressure of the discharged refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Constructs a subcritical 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 is a two-stage booster-type electric compressor that sucks, compresses, and discharges the refrigerant in the refrigeration cycle device 10. The compressor 11 is configured by housing two compression mechanisms, a low-stage compression mechanism and a high-stage compression mechanism, and an electric motor that rotationally drives both compression mechanisms, inside a housing forming an outer shell thereof. It was done. The operation of the compressor 11 is controlled by a control signal output from a control device 60 described later.

  The compressor 11 is provided with a suction port 11a, an intermediate pressure suction port 11b, and a discharge port 11c. The suction port 11a is a suction port for sucking low-pressure refrigerant from outside the housing to the low-stage compression mechanism. The discharge port 11c is a discharge port that discharges the high-pressure refrigerant discharged from the high-stage compression mechanism to the outside of the housing.

  The intermediate-pressure suction port 11b is a suction port for the intermediate-pressure refrigerant for allowing the intermediate-pressure refrigerant to flow from outside the housing and to join the refrigerant in the compression process from low pressure to high pressure. That is, the intermediate-pressure suction port 11b is connected to the discharge port side of the low-stage compression mechanism and the suction port side of the high-stage compression mechanism inside the housing.

  The inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the discharge port 11c 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 heating heat exchanger that heats the high-temperature heat medium by exchanging heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage. is there.

  The inflow side of the 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 employed.

  Further, the refrigeration cycle device 10 includes second to seventh three-way joints 13b to 13g as described later. The basic configuration of these second to seventh three-way joints 13b to 13g is the same as that of the first three-way joint 13a.

  The inlet side of the heating expansion valve 14a is connected to one outlet of the first three-way joint 13a. The other outlet of the first three-way joint 13a is connected to one inlet of the second three-way joint 13b 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 that connects the other outlet side of the first three-way joint 13a and one inlet side of the second three-way joint 13b. Further, the refrigeration cycle device 10 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 of 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 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 60.

  The heating expansion valve 14a depressurizes the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 at least in the operation mode of heating the passenger compartment, and also causes the flow rate (mass flow rate) of the refrigerant to flow downstream. This is a heating decompression unit that adjusts the pressure. The heating expansion valve 14a is an electric variable throttle mechanism that includes a valve body configured to change the opening degree of the throttle and an electric actuator that changes the opening degree of the valve body.

  Further, the refrigeration cycle apparatus 10 includes a cooling expansion valve 14b, a cooling expansion valve 14c, and an intermediate pressure expansion valve 14d, as described later. The basic configuration of the cooling expansion valve 14b, the cooling expansion valve 14c, and the intermediate pressure expansion valve 14d is the same as that of the heating expansion valve 14a.

  The heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the intermediate pressure expansion valve 14d are simply refrigerants that hardly exhibit a flow rate adjusting function and a refrigerant pressure reducing function by fully opening the valve opening. It has a fully open function that functions as a passage and a fully closed function that closes the refrigerant passage by fully closing the valve opening.

  By the fully open function and the fully closed function, the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the intermediate pressure expansion valve 14d can switch the refrigerant circuit in each operation mode.

  Therefore, the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the intermediate pressure expansion valve 14d of the present embodiment also have a function as a refrigerant circuit switching unit. The operations of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c are controlled by a control signal (control pulse) output from the control device 60.

  The refrigerant inlet side of the outdoor heat exchanger 16 is connected to the outlet of the heating expansion valve 14a. The outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant flowing out of the heating expansion valve 14a and the outside air blown by a cooling fan (not shown). The outdoor heat exchanger 16 is arranged on the front side in the drive device room. Therefore, when the vehicle is traveling, the traveling wind can be applied to the outdoor heat exchanger 16.

  The inflow side of the third three-way joint 13c is connected to the refrigerant outlet of the outdoor heat exchanger 16. One outlet of the fourth three-way joint 13d is connected to one outlet of the third three-way joint 13c via a heating passage 22b. A heating on-off valve 15b for opening and closing this refrigerant passage is arranged in the heating passage 22b.

  The inflow side of the seventh three-way joint 13g is connected to the other outlet of the third three-way joint 13c via a check valve 17. The check valve 17 allows the refrigerant to flow from the third three-way joint 13c to the seventh three-way joint 13g, and inhibits the refrigerant from flowing from the seventh three-way joint 13g to the third three-way joint 13c. Fulfill.

  One outlet of the seventh three-way joint 13g is connected to the intermediate pressure suction port 11b of the compressor 11 via an intermediate pressure passage 22c. An intermediate pressure expansion valve 14d and an intermediate temperature side passage 23a of the internal heat exchanger 23 are disposed in the intermediate pressure passage 22c. The inlet of the high-temperature side passage 23b of the internal heat exchanger 23 is connected to the other outlet of the seventh three-way joint 13g.

  The intermediate-pressure expansion valve 14d depressurizes one of the refrigerants branched by the seventh three-way joint 13g until it becomes the intermediate-pressure refrigerant in a cooling + cooling mode in which at least both cooling in the vehicle compartment and cooling of the battery 80 are performed. In addition, it is an intermediate pressure reducing unit that adjusts the flow rate (mass flow rate) of the refrigerant sucked from the intermediate pressure suction port 11b of the compressor 11.

  The internal heat exchanger 23 has an intermediate-temperature side passage 23a through which the intermediate-pressure refrigerant depressurized by the intermediate-pressure expansion valve 14d flows, and a high-temperature side passage 23b through which the other refrigerant branched by the seventh three-way joint 13g flows. And The internal heat exchanger 23 is a heat exchanger that exchanges heat between the intermediate-pressure refrigerant flowing through the intermediate-temperature-side passage 23a and the refrigerant flowing through the high-temperature-side passage 23b.

  In the internal heat exchanger 23b, the intermediate-pressure refrigerant flowing through the intermediate-temperature-side passage 23a is heated to increase enthalpy. Further, the refrigerant flowing through the high-temperature side passage 23b is cooled to reduce enthalpy.

  The other inlet side of the second three-way joint 13b is connected to the outlet of the high-temperature side passage 23b of the internal heat exchanger 23. The outlet of the fifth three-way joint 13e is connected to the outlet of the second three-way joint 13b. The inlet side of the cooling expansion valve 14b is connected to one outlet of the fifth three-way joint 13e. The inlet side of the cooling expansion valve 14c is connected to the other outlet of the fifth three-way joint 13e.

  The cooling expansion valve 14b is a cooling depressurizing unit that depressurizes the refrigerant flowing out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant that flows downstream, at least in an operation mode for cooling the vehicle interior.

  The refrigerant inlet side of the indoor evaporator 18 is connected to the outlet of the cooling expansion valve 14b. 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 14b 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 cooling heat exchanger that cools air. One inlet side of the sixth three-way joint 13f is connected to the refrigerant outlet of the indoor evaporator 18.

  The cooling expansion valve 14c is a cooling decompression unit that depressurizes the refrigerant that has flowed out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant that flows out downstream at least in the operation mode in which the battery 80 is cooled.

  The inlet of the refrigerant passage of the chiller 19 is connected to the outlet of the cooling expansion valve 14c. The chiller 19 has a refrigerant passage through which the low-pressure refrigerant depressurized by the cooling expansion valve 14c flows, and a water passage through which the low-temperature heat medium circulating through the low-temperature heat medium circuit 50 flows. The chiller 19 is an evaporator that exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage and the low-temperature side heat medium flowing through the water passage, evaporates the low-pressure refrigerant, and exerts an endothermic effect. The other inlet side of the sixth three-way joint 13f is connected to the outlet of the refrigerant passage of the chiller 19.

  The inlet side of the evaporation pressure regulating valve 20 is connected to the outlet of the sixth three-way joint 13f. The evaporation pressure regulating 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.

  Thereby, 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 adjusting valve 20 of the present embodiment is disposed downstream of the sixth three-way joint 13f, which is the junction, on the refrigerant flow side. For this reason, the evaporation pressure regulating valve 20 also maintains the refrigerant evaporation temperature in the chiller 19 at a temperature equal to or higher than the frost formation suppression temperature.

  The other inlet side of the fourth three-way joint 13d 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 fourth three-way joint 13d. 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 outlet of the gas-phase refrigerant of the accumulator 21 is connected to the inlet 11 a of the compressor 11.

  As is clear from the above description, the seventh three-way joint 13g of the present embodiment functions as an upstream branch portion that branches the flow of the refrigerant flowing out of the outdoor heat exchanger 16.

  Further, the fifth three-way joint 13e functions as a downstream branch portion that branches the flow of the refrigerant flowing out of the high-temperature side passage 23b of the internal heat exchanger 23. The sixth three-way joint 13 f 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 chiller 19 are merged and flown out to the suction side of the compressor 11. And the indoor evaporator 18 and the chiller 19 are connected in parallel with each other with respect to the refrigerant flow.

  The bypass passage 22a guides the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 downstream of the high-temperature side passage 23b of the internal heat exchanger 23 and upstream of the fifth three-way joint 13e. ing. That is, the outlet of the bypass passage 22a is connected to the refrigerant flow passage from the outlet of the high-temperature side passage 23b of the internal heat exchanger 23 to the inlet of the fifth three-way joint 13e, which is the downstream branch.

  In addition, the heating passage 22 b guides the refrigerant upstream of the seventh three-way joint 13 g (ie, upstream of the high-temperature passage 23 b of the internal heat exchanger 23) to the suction port 11 a of the compressor 11. . That is, the inlet of the heating passage 22b is connected to the refrigerant flow path from the refrigerant outlet of the outdoor heat exchanger 16 to the inlet of the seventh three-way joint 13g, which is the upstream branch.

  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, a solution containing ethylene glycol, dimethylpolysiloxane, a nanofluid, or the like, an antifreeze, or the like can be used. The high-temperature side heat medium circuit 40 includes a water passage of the water-refrigerant heat exchanger 12, a high-temperature side heat medium pump 41, a heater core 42, 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 (ie, pumping capacity) is controlled by a control voltage output from the control device 60.

  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 heat medium outlet of the heater core 42 is connected to the suction port side of the high-temperature side heat medium pump 41.

  Therefore, in the high-temperature side heat medium circuit 40, the high-temperature side heat medium pump 41 adjusts the flow rate of the high-temperature side heat medium flowing into the heater core 42, so that the heat radiation amount of the high-temperature side heat medium to the blast air in the heater core 42, That is, the heating amount of the blown air in the heater core 42 can be adjusted.

  In other words, in the present embodiment, each component of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 40 constitutes a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source. I have.

  Next, the low-temperature side heating medium circuit 50 will be described. The low-temperature-side heat medium circuit 50 is a heat medium circulation circuit that circulates the low-temperature-side heat medium. The same fluid as the high-temperature side heat medium can be used as the low-temperature side heat medium. In the low-temperature side heat medium circuit 50, a water passage of the chiller 19, a low-temperature side heat medium pump 51, a cooling heat exchange section 52, a three-way valve 53, a low-temperature side radiator 54, and the like are arranged.

  The low-temperature heat medium pump 51 is a water pump that pumps the low-temperature heat medium to the inlet side of the water passage of the chiller 19. The basic configuration of the low-temperature-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 heat exchange unit 52 is connected to the outlet of the water passage of the chiller 19. The cooling heat exchanging section 52 has a plurality of metal heat medium passages arranged to be in contact with the plurality of battery cells 81 forming the battery 80. The heat exchange unit cools the battery 80 by exchanging heat between the battery cell 81 and the low-temperature side heat medium flowing through the heat medium flow path.

  Such a cooling heat exchange section 52 may be formed by arranging a heat medium flow path between the battery cells 81 that are stacked. Further, cooling heat exchanging section 52 may be formed integrally with 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 inlet of the three-way valve 53 is connected to the outlet of the cooling heat exchange unit 52. The three-way valve 53 is an electric three-way flow control valve having one inflow port and two outflow ports, and capable of continuously adjusting the passage area ratio of the two outflow ports. The operation of the three-way valve 53 is controlled by a control signal output from the control device 60.

  The heat medium inlet side of the low-temperature side radiator 54 is connected to one outlet of the three-way valve 53. The other outlet of the three-way valve 53 is connected to the suction port side of the low-temperature side heat medium pump 51. Therefore, the three-way valve 53 continuously adjusts the flow rate of the low-temperature side heat medium flowing into the low-temperature side radiator 54 among the low-temperature side heat medium flowing out of the cooling heat exchange section 52 in the low-temperature side heat medium circuit 50. Plays a function.

  The low-temperature radiator 54 exchanges heat between the low-temperature heat medium flowing out of the cooling heat exchange unit 52 and the outside air blown by an outside air fan (not shown), and radiates heat of the low-temperature heat medium to the outside air. It is a vessel.

The low-temperature radiator 54 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 low-temperature radiator 54. Therefore, the low temperature radiator 54 may be formed integrally with the outdoor heat exchanger 16 and the like. The heat medium outlet of the low-temperature radiator 54 is connected to the suction port side of the low-temperature heat medium pump 51. Therefore, in the low-temperature heat medium circuit 50, the low-temperature heat medium pump 51 By adjusting the flow rate of the inflowing low-temperature side heat medium, the amount of heat absorbed by the low-temperature side heat medium from the battery 80 in the cooling heat exchange section 52 can be adjusted. That is, in the present embodiment, the cooling unit that cools the battery 80 by evaporating the refrigerant flowing out of the cooling expansion valve 14c is configured by the respective components of the chiller 19 and the low-temperature side heat medium circuit 50.

  Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is for blowing 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 passenger compartment.

  As shown in FIG. 1, the indoor air-conditioning unit 30 houses 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.

  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) excellent in strength.

  An inside / outside air switching device 33 is arranged 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 introduction rate with respect to the introduction air volume. 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 60.

  A blower 32 is disposed downstream of the inside / outside air switching device 33 in 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 60.

  On the downstream side of the blower 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 with respect to 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 flows around the heater core 42. An air mix door 34 is arranged on the downstream side of the air flow of the indoor evaporator 18 in the air conditioning case 31 and on the upstream side of the 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, of 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 60.

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

  Furthermore, 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 the space to be air-conditioned, is disposed downstream of the airflow of the air-conditioning case 31.

  As this 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 inside surface of the vehicle front window glass.

  The face opening, the foot opening, and the defroster opening are respectively connected to a face outlet, a foot outlet, and a defroster outlet (all not shown) 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 60.

  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 passenger compartment. The bi-level mode is an outlet mode in which both the face outlet and the foot 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 and the defroster outlet is opened by a small opening, and air is mainly blown out from the foot outlet.

  Furthermore, the occupant can switch to the defroster mode by manually operating the blowout mode changeover switch provided on the operation panel 70. 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 60 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 14d, 15a, 15b, 32, 41, 51, 53 connected to the output side are performed. And the like.

  On the input side of the control device 60, as shown in the block diagram of FIG. 2, an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation sensor 63, first to fifth refrigerant temperature sensors 64a to 64e, an evaporator temperature. Sensor 64f, intermediate pressure temperature sensor 64g, first and second refrigerant pressure sensors 65a and 65b, intermediate pressure pressure sensor 65c, high temperature side heat medium temperature sensor 66a, first and second low temperature side heat medium temperature sensors 67a and 67b, A battery temperature sensor 68, an air conditioning wind temperature sensor 69, and the like are connected. The control unit 60 receives detection signals from these sensor groups.

  The internal air temperature sensor 61 is an internal air temperature detecting unit that detects a vehicle interior temperature (internal air temperature) Tr. The outside air temperature sensor 62 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam. The solar radiation sensor 63 is a solar radiation amount detecting unit that detects a solar radiation amount Ts irradiated to the vehicle interior.

  The first refrigerant temperature sensor 64a is a discharge refrigerant temperature detection unit that detects the temperature T1 of the refrigerant discharged from the compressor 11. The second refrigerant temperature sensor 64b is a second refrigerant temperature detector 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 64c is a third refrigerant temperature detecting unit that detects the temperature T3 of the refrigerant flowing out of the outdoor heat exchanger 16.

  The fourth refrigerant temperature sensor 64d is a fourth refrigerant temperature detector that detects the temperature T4 of the refrigerant flowing out of the indoor evaporator 18. The fifth refrigerant temperature sensor 64e is a fifth refrigerant temperature detector that detects the temperature T5 of the refrigerant flowing out of the refrigerant passage of the chiller 19.

  The evaporator temperature sensor 64f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 18. Specifically, the evaporator temperature sensor 64f of the present embodiment detects the heat exchange fin temperature of the indoor evaporator 18.

  The intermediate pressure temperature sensor 64g is an intermediate pressure temperature detecting unit that detects an intermediate pressure temperature T8 of the refrigerant flowing out of the intermediate temperature side passage 23a of the internal heat exchanger 23.

  The first refrigerant pressure sensor 65a is a first refrigerant pressure detector 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 65b is a second refrigerant pressure detector that detects the pressure P2 of the refrigerant flowing out of the refrigerant passage of the chiller 19. The intermediate pressure sensor 65c is an intermediate pressure detector that detects an intermediate pressure refrigerant pressure P3 of the refrigerant flowing out of the intermediate temperature side passage 23a of the internal heat exchanger 23.

  The high-temperature-side heat medium temperature sensor 66a is a high-temperature-side heat medium temperature detection unit that detects the high-temperature-side heat medium temperature TWH, which is the temperature of the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12.

  The first low-temperature heat medium temperature sensor 67a is a first low-temperature heat medium temperature detection unit that detects the first low-temperature heat medium temperature TWL1, which is the temperature of the low-temperature heat medium flowing out of the water passage of the chiller 19. The second low-temperature-side heat medium temperature sensor 67b is a second low-temperature-side heat medium temperature detection unit that detects the second low-temperature-side heat medium temperature TWL2 that is the temperature of the low-temperature side heat medium flowing out of the cooling heat exchange unit 52. .

  Battery temperature sensor 68 is a battery temperature detection unit that detects battery temperature TB (that is, the temperature of battery 80). The battery temperature sensor 68 of the present embodiment has a plurality of temperature sensors and detects temperatures at a plurality of locations of the battery 80. For this reason, the control device 60 can also detect a 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 69 is an air-conditioning air temperature detecting unit that detects an air temperature TAV that is blown from the mixing space into the vehicle interior.

  Further, as shown in FIG. 2, an operation panel 70 arranged near the instrument panel in the front of the vehicle compartment is connected to the input side of the control device 60, and various operation switches provided on the operation panel 70 An operation signal is input.

  The various operation switches provided on the operation panel 70 include, specifically, an auto switch for setting or canceling the automatic control operation of the vehicle air conditioner, and an air conditioner switch for requesting that the air blown by the indoor evaporator 18 be cooled. There are an air volume setting switch for manually setting the air volume of the blower 32, a temperature setting switch for setting the target temperature Tset in the vehicle compartment, and a blow mode switching switch for manually setting the blow mode.

  Note that the control device 60 of the present embodiment is configured such that a control unit that controls various types of controlled devices connected to the output side thereof is integrally formed. However, the control device 60 controls the operation of each controlled device. Hardware and software) constitute a control unit that controls the operation of each control target device.

  For example, of the control device 60, 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 60a. The configuration for controlling the operations of the heating expansion valve 14a, the cooling expansion valve 14b, the cooling expansion valve 14c, and the intermediate pressure expansion valve 14d constitutes an expansion valve control unit 60b. The configuration for controlling the operations of the dehumidifying on-off valve 15a and the heating on-off valve 15b constitutes a refrigerant circuit switching control unit 60c.

  Further, the configuration for controlling the high-temperature-side heat medium pumping capability of the high-temperature side heat medium pump 41 constitutes a high-temperature side heat medium pump control unit 60d. The configuration for controlling the low-temperature-side heat medium pumping capability of the low-temperature-side heat medium pump 51 constitutes a low-temperature-side heat medium pump control unit 60e.

  Next, the operation of this embodiment in the above configuration will be described. As described above, the vehicle air conditioner 1 of the present embodiment has a function of adjusting the temperature of the battery 80 as well as performing air conditioning of the vehicle interior. For this reason, in the refrigeration cycle apparatus 10, it is possible to perform operation in the following 11 operation modes by switching the refrigerant circuit.

  (1) Cooling mode: The cooling mode is an operation mode in which the inside of the vehicle compartment is cooled by cooling the blown air and blowing it out into the vehicle compartment without cooling the battery 80.

  (2) Series dehumidification and heating mode: In the series dehumidification and heating mode, the operation of performing dehumidification and heating in the vehicle compartment by reheating the blown air that has been cooled and dehumidified and blowing it out into the vehicle compartment without cooling the battery 80. Mode.

  (3) Parallel dehumidifying and heating mode: In the parallel dehumidifying and heating mode, the cooled and dehumidified blast air is reheated with a higher heating capacity than the serial dehumidifying and heating mode and blown out into the vehicle compartment without cooling the battery 80. This is an operation mode for performing dehumidification and heating of the vehicle interior.

  (4) Heating mode: The heating mode is an operation mode in which the air inside the vehicle is heated by heating the blown air and blowing it out into the vehicle interior without cooling the battery 80.

  (5) Cooling + cooling mode: The cooling + cooling mode is an operation mode in which the battery 80 is cooled, and the air in the vehicle compartment is cooled by cooling the blown air and blowing it out into the vehicle compartment.

  (6) Series dehumidification heating + cooling mode: In series dehumidification heating + cooling mode, the battery 80 is cooled, and the cooled and dehumidified blast air is reheated and blown into the vehicle interior to dehumidify and heat the vehicle interior. This is an operation mode in which is performed.

  (7) Parallel dehumidifying heating and cooling mode: The parallel dehumidifying heating and cooling mode cools the battery 80 and reheats the cooled and dehumidified blast air with a higher heating capacity than the serial dehumidifying heating and cooling mode. This is an operation mode in which dehumidifying and heating of the vehicle interior is performed by blowing the air into the vehicle interior.

  (8) Heating + cooling mode: The heating + cooling mode is an operation mode in which the battery 80 is cooled and the inside of the vehicle is heated by heating the blown air and blowing it out into the vehicle interior.

  (9) Heating + series cooling mode: The heating + series cooling mode cools the battery 80 and heats the blast air with a higher heating capacity than the heating + cooling mode and blows the air into the vehicle interior to heat the vehicle interior. This is an operation mode in which is performed.

  (10) Heating + parallel cooling mode: In the heating + parallel cooling mode, the battery 80 is cooled, and the blast air is heated with a higher heating capacity than the heating + serial cooling mode and is blown out into the vehicle cabin. This is an operation mode in which heating is performed.

  (11) Cooling mode: An operation mode in which the battery 80 is cooled without performing air conditioning in the vehicle compartment.

  Switching of these operation modes is performed by executing an air conditioning control program. The air-conditioning control program is executed when an automatic switch of the operation panel 70 is turned on (ON) by an occupant's operation and automatic control of the vehicle interior is set. The air conditioning control program will be described with reference to FIGS. Each control step shown in the flowchart of FIG. 3 and the like is a function realizing unit of the control device 60.

  First, in step S10 of FIG. 3, the detection signal of the above-described sensor group and the operation signal of the operation panel 70 are read. In a succeeding step S20, a target outlet temperature TAO, which is a target temperature of the air blown into the vehicle interior, is determined based on the detection signal and the operation signal read in step S10. Therefore, step S20 is a target outlet temperature determination unit.

Specifically, the target outlet temperature TAO is calculated by the following equation F1.
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × Ts + C (F1)
Note that 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.

  Next, in step S30, it is determined whether or not the air conditioner switch is ON (turned on). The fact that the air conditioner switch is turned on means that the occupant is requesting cooling or dehumidification in the vehicle interior. In other words, the fact that the air conditioner switch is ON means that it is required to cool the blown air in the indoor evaporator 18.

  If it is determined in step S30 that the air conditioner switch is ON, the process proceeds to step S40. If it is determined in step S30 that the air conditioner switch has not been turned on, the process proceeds to step S160.

  In step S40, it is determined whether or not the outside temperature Tam is equal to or higher than a predetermined reference outside temperature KA (0 ° C. in the present embodiment). The reference outside air temperature KA is set so that cooling of the blown air by the indoor evaporator 18 is effective for cooling or dehumidifying the space to be air-conditioned.

  More specifically, in the present embodiment, in order to suppress frost formation on the indoor evaporator 18, the evaporation pressure regulating valve 20 changes the refrigerant evaporation temperature in the indoor evaporator 18 into a frost formation suppression temperature (1 ° C. in this embodiment). ) Or more. For this reason, in the indoor evaporator 18, the blown air cannot be cooled to a temperature lower than the frost formation suppression temperature.

  That is, when the temperature of the blown air flowing into the indoor evaporator 18 is lower than the temperature of the frost formation suppression temperature, cooling the blown air by the indoor evaporator 18 is not effective. Therefore, the reference outside air temperature KA is set to a value lower than the frost formation suppression temperature, and when the outside air temperature Tam is lower than the reference outside air temperature KA, the air blown by the indoor evaporator 18 is not cooled. .

  If it is determined in step S40 that the outside temperature Tam is equal to or higher than the reference outside temperature KA, the process proceeds to step S50. If it is determined in step S40 that the outside temperature Tam is not equal to or higher than the reference outside temperature KA, the process proceeds to step S160.

  In step S50, it is determined whether the target outlet temperature TAO is equal to or lower than the cooling reference temperature α1. The cooling reference temperature α1 is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance. In the present embodiment, as shown in FIG. 5, the cooling reference temperature α1 is determined to be a low value as the outside temperature Tam decreases.

  If it is determined in step S50 that the target outlet temperature TAO is equal to or lower than the cooling reference temperature α1, the process proceeds to step S60. If it is determined in step S50 that the target outlet temperature TAO is not lower than the cooling reference temperature α1, the process proceeds to step S90.

  In step S60, it is determined whether cooling of battery 80 is necessary. Specifically, in the present embodiment, when the battery temperature TB detected by the battery temperature sensor 68 is equal to or higher than a predetermined reference cooling temperature KTB (35 ° C. in the present embodiment), the cooling of the battery 80 is performed. Is determined to be necessary. When battery temperature TB is lower than reference cooling temperature KTB, it is determined that cooling of battery 80 is not necessary.

  If it is determined in step S60 that cooling of battery 80 is necessary, the process proceeds to step S70, and (5) cooling + cooling mode is selected as the operation mode. If it is determined in step S60 that cooling of battery 80 is not necessary, the process proceeds to step S80, and (1) cooling mode is selected as the operation mode.

  In step S90, it is determined whether the target outlet temperature TAO is equal to or lower than the dehumidifying reference temperature β1. The dehumidifying reference temperature β1 is determined based on the outside temperature Tam with reference to a control map stored in the control device 60 in advance.

  In the present embodiment, as shown in FIG. 5, similarly to the cooling reference temperature α1, the dehumidification reference temperature β1 is determined to be a low value as the outside temperature Tam decreases. Further, the dehumidifying reference temperature β1 is determined to be higher than the cooling reference temperature α1.

  If it is determined in step S90 that the target outlet temperature TAO is equal to or lower than the dehumidifying reference temperature β1, the process proceeds to step S100. If it is determined in step S90 that the target outlet temperature TAO is not lower than the dehumidifying reference temperature β1, the process proceeds to step S130.

  In step S100, similarly to step S60, it is determined whether cooling of battery 80 is necessary.

  If it is determined in step S100 that cooling of battery 80 is necessary, the process proceeds to step S110, and (6) in-line dehumidifying heating + cooling mode is selected as the operation mode of refrigeration cycle apparatus 10. If it is determined in step S100 that cooling of battery 80 is not necessary, the process proceeds to step S120, and (2) in-line dehumidifying and heating mode is selected as the operation mode.

  In step S130, similarly to step S60, it is determined whether cooling of battery 80 is necessary.

  If it is determined in step S130 that cooling of battery 80 is necessary, the process proceeds to step S140, and (7) parallel dehumidifying heating + cooling mode is selected as the operation mode of refrigeration cycle apparatus 10. If it is determined in step S100 that cooling of battery 80 is not necessary, the process proceeds to step S150, and (3) the parallel dehumidifying and heating mode is selected as the operation mode.

  Subsequently, a case where the process proceeds from step S30 or step S40 to step S160 will be described. When the process proceeds from step S30 or step S40 to step S160, it is determined that cooling the blown air by the indoor evaporator 18 is not effective. In step S160, as shown in FIG. 4, it is determined whether or not the target outlet temperature TAO is equal to or higher than the heating reference temperature γ.

  The heating reference temperature γ is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance. In the present embodiment, as shown in FIG. 6, the heating reference temperature γ is determined to be a low value as the outside temperature Tam decreases. The heating reference temperature γ is set such that heating of the blast air by the heater core 42 is effective for heating the space to be air-conditioned.

  If it is determined in step S160 that the target outlet temperature TAO is equal to or higher than the heating reference temperature γ, it means that the blower air needs to be heated by the heater core 42, and the process proceeds to step S170. If it is determined in step S160 that the target outlet temperature TAO is not equal to or higher than the heating reference temperature γ, it is not necessary to heat the blown air by the heater core 42, and the process proceeds to step S240.

  In step S170, similarly to step S60, it is determined whether cooling of battery 80 is necessary.

  If it is determined in step S170 that cooling of battery 80 is necessary, the process proceeds to step S180. If it is determined in step S170 that cooling of battery 80 is not necessary, the process proceeds to step S230, and (4) heating mode is selected as the operation mode.

  Here, when it is determined in step S170 that the battery 80 needs to be cooled, and the process proceeds to step S180, it is necessary to perform both heating of the vehicle interior and cooling of the battery 80. For this reason, in the refrigeration cycle apparatus 10, the amount of heat released by the refrigerant to the high-temperature heat medium in the water-refrigerant heat exchanger 12 and the amount of heat absorbed by the refrigerant in the chiller 19 from the low-temperature heat medium are appropriately determined. Need to adjust.

  Therefore, in the refrigeration cycle apparatus 10 of the present embodiment, when it is necessary to perform both heating of the vehicle interior and cooling of the battery 80, as shown in steps S180 to S220 in FIG. The three operation modes of a cooling mode, (9) heating + series cooling mode, and (10) heating + parallel cooling mode are switched.

  First, in step S180, it is determined whether the target outlet temperature TAO is equal to or lower than the low-temperature side cooling reference temperature α2. The low-temperature side cooling reference temperature α2 is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance.

  In the present embodiment, as shown in FIG. 7, the low-temperature side cooling reference temperature α2 is determined to be a low value as the outside temperature Tam decreases. Further, at the same outside air temperature Tam, the low-temperature side cooling reference temperature α2 is determined to be higher than the cooling reference temperature α1.

  If it is determined in step S180 that the target outlet temperature TAO is equal to or lower than the low-temperature side cooling reference temperature α2, the process proceeds to step S190, and (8) the heating + cooling mode is selected as the operation mode. If it is determined in step S180 that the target outlet temperature TAO is not lower than the low-temperature side cooling reference temperature α2, the process proceeds to step S200.

  In step S200, it is determined whether the target outlet temperature TAO is equal to or lower than the high-temperature side cooling reference temperature β2. The high-temperature side cooling reference temperature β2 is determined based on the outside air temperature Tam with reference to a control map stored in the control device 60 in advance.

  In the present embodiment, as shown in FIG. 7, similarly to the low-temperature-side cooling reference temperature α2, the high-temperature-side cooling reference temperature β2 is determined to be a low value as the outside air temperature Tam decreases. Furthermore, the high temperature side cooling reference temperature β2 is determined to be higher than the low temperature side cooling reference temperature α2. Further, at the same outside air temperature Tam, the high-temperature side cooling reference temperature β2 is determined to be higher than the dehumidification reference temperature β1.

  When it is determined in step S200 that the target outlet temperature TAO is equal to or lower than the high-temperature side cooling reference temperature β2, the process proceeds to step S210, and (9) heating + series cooling mode is selected as the operation mode. If it is determined in step S200 that the target outlet temperature TAO is not lower than the high-temperature side cooling reference temperature β2, the process proceeds to step S220, and (10) heating + parallel cooling mode is selected as the operation mode.

  Subsequently, a case where the process proceeds from step S160 to step S240 will be described. When the process proceeds from step S160 to step S240, it is not necessary to heat the blown air by the heater core 42. Therefore, in step S240, similarly to step S60, it is determined whether cooling of battery 80 is necessary.

  If it is determined in step S240 that cooling of battery 80 is necessary, the process proceeds to step S250, and (11) cooling mode is selected as the operation mode. If it is determined in step S200 that cooling of battery 80 is not necessary, the process proceeds to step S260, where the air blowing mode is selected as the operation mode, and the process returns to step S10.

  The blower mode is an operation mode in which the compressor 11 is stopped and the blower 32 is operated in accordance with the setting signal set by the airflow setting switch. If it is determined in step S240 that cooling of battery 80 is not necessary, it means that it is not necessary to operate refrigeration cycle device 10 for air conditioning in the vehicle compartment and cooling of the battery.

  In the air conditioning control program of the present embodiment, the operation mode of the refrigeration cycle device 10 is switched as described above. Further, in this air-conditioning control program, not only the operation of each component of the refrigeration cycle apparatus 10, but also the high-temperature side heat medium pump 41 of the high-temperature side heat medium circuit 40 constituting the heating section, and the low temperature side pump constituting the cooling section The operation of the low-temperature side heat medium pump 51 and the three-way valve 53 of the heat medium circuit 50 is also controlled.

  Specifically, the control device 60 controls the operation of the high-temperature side heat transfer medium pump 41 so as to exhibit a predetermined reference pumping capacity in each of the predetermined operation modes regardless of the operation mode of the refrigeration cycle device 10 described above. I do.

  Therefore, in the high-temperature heat medium circuit 40, when the high-temperature heat medium is heated in the water passage of the water-refrigerant heat exchanger 12, the heated high-temperature heat medium is pumped to the heater core 42. The high-temperature side heat medium flowing into the heater core 42 exchanges heat with the blown air. Thereby, the blown air is heated. The high-temperature-side heat medium flowing out of the heater core 42 is sucked into the high-temperature-side heat medium pump 41 and is pressure-fed to the water-refrigerant heat exchanger 12.

  In addition, the control device 60 controls the operation of the low-temperature side heat transfer medium pump 51 so as to exhibit a predetermined reference pumping capacity in each operation mode, regardless of the operation mode of the refrigeration cycle device 10 described above.

  Further, when the second low-temperature heat medium temperature TWL2 detected by the second low-temperature heat medium temperature sensor 67b is equal to or higher than the outside air temperature Tam, the control device 60 flows out of the cooling heat exchange unit 52. The operation of the three-way valve 53 is controlled so that the low-temperature side heat medium flows into the low-temperature side radiator 54.

  If the second low-temperature heat medium temperature TWL2 is not equal to or higher than the outside air temperature Tam, the three-way heat medium flowing out of the cooling heat exchange unit 52 is sucked into the suction port of the low-temperature heat medium pump 51 in three directions. The operation of the valve 53 is controlled.

  Therefore, in the low-temperature side heat medium circuit 50, when the low-temperature side heat medium is cooled in the water passage of the chiller 19, the cooled low-temperature side heat medium is pumped to the cooling heat exchange section 52. The low-temperature side heat medium that has flowed into the cooling heat exchange section 52 absorbs heat from the battery 80. Thereby, battery 80 is cooled. The low-temperature side heat medium flowing out of the cooling heat exchange section 52 flows into the three-way valve 53.

  At this time, when the second low-temperature heat medium temperature TWL2 is equal to or higher than the outside air temperature Tam, the low-temperature heat medium flowing out of the cooling heat exchange unit 52 flows into the low-temperature radiator 54 and radiates heat to the outside air. I do. Thus, the low-temperature side heat medium is cooled until it becomes equal to the outside air temperature Tam. The low-temperature-side heat medium flowing out of the low-temperature-side radiator 54 is sucked into the low-temperature-side heat medium pump 51 and sent to the chiller 19 under pressure.

  On the other hand, when the second low-temperature-side heat medium temperature TWL2 is lower than the outside air temperature Tam, the low-temperature-side heat medium flowing out of the cooling heat exchange unit 52 is sucked into the low-temperature-side heat medium pump 51 and chilled. It is pumped to 19. For this reason, the temperature of the low-temperature side heat medium sucked into the low-temperature side heat medium pump 51 becomes equal to or lower than the outside air temperature Tam.

  Hereinafter, detailed operations of the vehicle air conditioner 1 in each operation mode will be described. The control maps referred to in each operation mode described below are stored in the control device 60 in advance for each operation mode. The corresponding control maps of the respective operation modes may be equivalent to each other or may be different from each other.

(1) Cooling Mode In the cooling mode, the control device 60 executes the control flow of the cooling mode shown in FIG. First, in step S600, a target evaporator temperature TEO is determined. The target evaporator temperature TEO is determined by referring to a control map stored in the control device 60 based on the target outlet temperature TAO. In the control map of the present embodiment, it is determined that the target evaporator temperature TEO increases as the target outlet temperature TAO increases.

  In step S610, an increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined. The amount of increase / decrease ΔIVO is based on the deviation between the target evaporator temperature TEO and the evaporator temperature Tefin detected by the evaporator temperature sensor 64f, and the feedback control method is used so that the evaporator temperature Tefin approaches the target evaporator temperature TEO. It is determined.

  In step S620, the target supercooling degree SCO1 of the refrigerant flowing out of the outdoor heat exchanger 16 is determined. The target degree of supercooling SCO1 is determined with reference to a control map, for example, based on the outside air temperature Tam. In the control map of the present embodiment, the target degree of supercooling SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

  In step S630, an increase / decrease amount ΔEVC of the throttle opening of the cooling expansion valve 14b is determined. The amount of increase / decrease ΔEVC is based on a deviation between the target degree of supercooling SCO1 and the degree of supercooling SC1 of the refrigerant on the outlet side of the outdoor heat exchanger 16, and the degree of supercooling of the refrigerant on the outlet side of the outdoor heat exchanger 16 is determined by a feedback control method. SC1 is determined so as to approach target supercooling degree SCO1.

  The degree of supercooling SC1 of the refrigerant on the outlet side of the outdoor heat exchanger 16 is calculated based on the temperature T3 detected by the third refrigerant temperature sensor 64c and the pressure P1 detected by the first refrigerant pressure sensor 65a.

  In step S640, the target degree of superheat SHIO of the outlet side refrigerant of the intermediate temperature side passage 23a of the internal heat exchanger 23 is determined. As the target degree of superheat SHIO, a predetermined constant (10 ° C. in the present embodiment) can be adopted.

  In step S650, an increase / decrease amount ΔEVI of the throttle opening of the intermediate pressure expansion valve 14d is determined. The increase / decrease amount ΔEVI is determined based on a difference between the target superheat degree SHIO and the superheat degree SHI of the refrigerant on the outlet side of the intermediate temperature side passage 23a of the internal heat exchanger 23 by a feedback control method. The superheat degree SHI of the refrigerant on the outlet side of the passage 23a is determined so as to approach the target superheat degree SHIO.

  The superheat degree SHI of the refrigerant on the outlet side of the intermediate temperature side passage 23a of the internal heat exchanger 23 is determined by the intermediate pressure temperature T8 detected by the intermediate pressure temperature sensor 64g and the intermediate pressure refrigerant pressure P3 detected by the intermediate pressure pressure sensor 65c. Is calculated based on

In step S660, the opening degree SW of the air mix door 34 is calculated 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 66a. C2 is a control constant.

  In step S670, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the cooling mode, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is set to the throttle state for exerting the refrigerant depressurizing action, and the cooling expansion valve 14c is set. Is fully closed, the intermediate pressure expansion valve 14d is in the throttled state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S610, S630, S650, and S660 is obtained, and the process returns to step S10.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 (→ the heating expansion valve 14a) → the outdoor heat exchanger 16 → the check valve 17 → the seventh three-way joint. 13g → the intermediate pressure expansion valve 14d → the intermediate temperature side passage 23a of the internal heat exchanger 23 → the refrigerant is circulated in the order of the intermediate pressure suction port 11b of the compressor 11, and the seventh three-way joint 13g → the internal heat exchanger 23 A gas injection cycle is formed in which the refrigerant is circulated in the order of the high-temperature side passage 23b, the cooling expansion valve 14b, the indoor evaporator 18, the evaporation pressure regulating valve 20, the accumulator 21, and the suction port 11a of the compressor 11.

  More specifically, when the control device 60 operates the compressor 11, the high-pressure refrigerant (point a9 in FIG. 9) discharged from the discharge port 11c of the compressor 11, as shown in the Mollier diagram of FIG. The refrigerant flows into the refrigerant passage of the water-refrigerant heat exchanger 12. The high-temperature and high-pressure refrigerant flowing into the refrigerant passage of the water-refrigerant heat exchanger 12 exchanges heat with the high-temperature side heat medium flowing through the water passage and radiates heat (point a9 → point b9 in FIG. 9). Thereby, the high-temperature side heat medium is heated.

  The high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 is pressure-fed to the heater core 42. In the heater core 42, the blown air cooled by the indoor evaporator 18 is heated according to the opening of the air mix door 34. 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 outdoor heat exchanger 16 via the heating expansion valve 14a which is in a fully opened state. The refrigerant flowing into the outdoor heat exchanger 16 exchanges heat with the outside air and radiates heat (point b9 → point c9 in FIG. 9). The flow of the refrigerant flowing out of the outdoor heat exchanger 16 is branched at the seventh three-way joint 13g, which is the upstream branch portion.

  One of the refrigerants branched at the seventh three-way joint 13g flows into the intermediate pressure passage 22c, is decompressed by the intermediate pressure expansion valve 14d until the refrigerant becomes the intermediate pressure refrigerant, and the temperature drops (point c9 in FIG. 9 → d9). point). At this time, the throttle opening of the intermediate pressure expansion valve 14d is adjusted such that the superheat degree SHI of the outlet side refrigerant (point e9 in FIG. 9) of the intermediate temperature side passage 23a of the internal heat exchanger 23 approaches the target superheat degree SHIO. Is done.

  The intermediate-pressure refrigerant decompressed by the intermediate-pressure expansion valve 14 d flows into the intermediate-temperature side passage 23 a of the internal heat exchanger 23. The intermediate-pressure refrigerant flowing into the intermediate-temperature-side passage 23a of the internal heat exchanger 23 exchanges heat with the refrigerant flowing through the high-temperature-side passage 23b of the internal heat exchanger 23 to increase enthalpy (point d9 in FIG. 9 → e9). point).

  The refrigerant flowing out of the intermediate temperature side passage 23 a of the internal heat exchanger 23 is sucked through the intermediate pressure suction port 11 b of the compressor 11. The refrigerant (point e9 in FIG. 9) sucked from the intermediate pressure suction port 11b of the compressor 11 joins the refrigerant (point i9 in FIG. 9) pressurized by the low stage compression mechanism of the compressor 11 (point i9). 9 (point j9 in FIG. 9), and is sucked into the high-stage compression mechanism of the compressor 11.

  The other refrigerant branched at the seventh three-way joint 13 g flows into the high-temperature side passage 23 b of the internal heat exchanger 23. The refrigerant flowing into the high-temperature side passage 23b of the internal heat exchanger 23 exchanges heat with the refrigerant flowing through the intermediate-temperature side passage 23a of the internal heat exchanger 23 to reduce enthalpy (point c9 → point f9 in FIG. 9). .

  Since the cooling expansion valve 14c is in a fully closed state, the refrigerant flowing out of the high-temperature side passage 23b of the internal heat exchanger 23 flows into the cooling expansion valve 14b and is decompressed until it becomes a low-pressure refrigerant (FIG. 9 f9 point → g9 point). At this time, the throttle opening of the cooling expansion valve 14b is adjusted such that the supercooling degree SC1 of the outlet-side refrigerant of the outdoor heat exchanger 16 (point c9 in FIG. 9) approaches the target supercooling degree SCO1.

  The low-pressure refrigerant depressurized by the cooling expansion valve 14 b flows into the indoor evaporator 18. The low-pressure refrigerant that has flowed into the indoor evaporator 18 absorbs heat from the air blown by the blower 32 and evaporates (point g9 → point h9 in FIG. 9). Thereby, the blown air is cooled. The refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 21 via the evaporation pressure adjusting valve 20.

  In the accumulator 21, gas-liquid of the refrigerant is separated. The gas-phase refrigerant separated by the accumulator 21 is drawn from the suction port 11a of the compressor 11, and is pressurized by the low-stage compression mechanism (point h9 → point i9 in FIG. 9).

  According to this, it is possible to cool the blown air in the indoor evaporator 18 and to heat the high-temperature side heat medium in the water-refrigerant heat exchanger 12.

  Therefore, in the vehicle air conditioner 1 in the cooling mode, by adjusting the opening of the air mix door 34, a part of the blast air cooled by the indoor evaporator 18 is reheated by the heater core 42 to reach the target outlet temperature TAO. By blowing the blast air whose temperature has been adjusted so as to approach the interior of the vehicle, the interior of the vehicle can be cooled.

  Further, in the refrigeration cycle apparatus 10 in the cooling mode, since the gas injection cycle is configured, the action of the internal heat exchanger 23 changes the enthalpy of the refrigerant on the outlet side of the indoor evaporator 18 to the enthalpy of the refrigerant on the inlet side of the indoor evaporator 18. Enthalpy difference can be enlarged. As a result, the cooling capacity of the blown air can be improved as compared with a normal vapor compression refrigeration cycle.

(2) Series dehumidification heating mode In the series dehumidification heating mode, the control device 60 executes the control flow of the series dehumidification heating mode shown in FIG. First, in step S700, the target evaporator temperature TEO is determined as in the cooling mode. In step S710, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined as in the cooling mode.

  In step S720, the target high-temperature heat medium temperature TWHO of the high-temperature heat medium is determined so that the blower air can be heated by the heater core 42. The target high-temperature-side heat medium temperature TWHO is determined with reference to a control map based on the target outlet temperature TAO and the efficiency of the heater core 42. In the control map of the present embodiment, it is determined that the target high-temperature-side heat medium temperature TWHO increases as the target blowout temperature TAO increases.

  In step S730, a change amount ΔKPN1 of the opening degree pattern KPN1 is determined. The opening degree pattern KPN1 is a parameter for determining a combination of a throttle opening degree of the heating expansion valve 14a and a throttle opening degree of the cooling expansion valve 14b.

  Specifically, in the series dehumidifying and heating mode, as shown in FIG. 11, the opening degree pattern KPN1 increases as the target outlet temperature TAO increases. Then, as the opening degree pattern KPN1 increases, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14b increases.

  In step S740, similarly to the cooling mode, the opening degree SW of the air mix door 34 is calculated. Here, in the in-line dehumidifying and heating mode, the target outlet temperature TAO is higher than in the cooling mode, so that the opening degree SW of the air mix door 34 approaches 100%. For this reason, in the serial dehumidification heating mode, the opening of the air mix door 34 is determined such that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.

  In step S750, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the serial dehumidifying and heating mode, the heating expansion valve 14a is set in the throttled state, the cooling expansion valve 14b is set in the throttled state, and the cooling expansion valve 14c is fully closed. The intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S710, S730, and S740 is obtained, and the process returns to step S10.

  Therefore, in the refrigeration cycle apparatus 10 in the series dehumidifying and heating mode, the discharge port 11c of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, and the cooling expansion valve. A vapor compression refrigeration cycle in which the refrigerant is circulated in the order of 14b → the indoor evaporator 18 → the evaporation pressure regulating valve 20 → the accumulator 21 → the suction port 11a of the compressor 11 is configured.

  That is, in the refrigeration cycle apparatus 10 in the serial dehumidifying and heating mode, the water-refrigerant heat exchanger 12 functions as a radiator for radiating the refrigerant discharged from the compressor 11, and the heating expansion valve 14a and the cooling expansion valve 14b are used. A vapor compression refrigeration cycle in which the indoor evaporator 18 functions as an evaporator, functioning as a pressure reducing unit.

  Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as a radiator is configured. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as an evaporator is configured.

  Here, in the refrigeration cycle apparatus 10 in the series dehumidification heating mode, the intermediate pressure expansion valve 14d is in a fully closed state. Therefore, no refrigerant is sucked from the intermediate pressure suction port 11b of the compressor 11. In this case, the compressor 11 functions as a single-stage compressor that compresses the refrigerant sucked from the suction port 11a and discharges it from the discharge port 11c.

  Further, the refrigerant flowing out of the outdoor heat exchanger 16 and flowing through the high temperature side passage 23b of the internal heat exchanger 23 does not exchange heat with the refrigerant flowing through the intermediate temperature side passage 23a. Therefore, the high temperature side passage 23b functions as a simple refrigerant passage. This is the same in other operation modes in which the intermediate pressure expansion valve 14d is fully closed.

  According to this, it is possible to cool the blown air in the indoor evaporator 18 and to heat the high-temperature side heat medium in the water-refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the series dehumidifying and heating mode, the blast air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42 and blown out into the cabin, thereby dehumidifying and heating the cabin. It can be performed.

  Further, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, the opening degree pattern KPN1 is increased in accordance with the increase of the target blowout temperature TAO, so that the outdoor heat exchanger The refrigerant saturation temperature at 16 decreases, and the difference from the outside air temperature Tam decreases. Thereby, the heat radiation amount of the refrigerant in the outdoor heat exchanger 16 can be reduced, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased.

  Further, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outdoor temperature Tam, the opening degree pattern KPN1 is increased with an increase in the target blowing temperature TAO, so that the outdoor heat exchanger 16 is increased. The mild temperature of the refrigerant at 16 decreases, and the temperature difference from the outside air temperature Tam increases. Thereby, the heat absorption amount of the refrigerant in the outdoor heat exchanger 16 can be increased, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased.

  That is, in the in-line dehumidifying and heating mode, the amount of heat released from the refrigerant in the water-refrigerant heat exchanger 12 to the high-temperature side heat medium can be increased by increasing the opening degree pattern KPN1 as the target outlet temperature TAO increases. it can. Therefore, in the in-line dehumidifying and heating mode, the heating capability of the heater core 42 for blowing air can be improved with an increase in the target outlet temperature TAO.

(3) Parallel dehumidifying and heating mode In the parallel dehumidifying and heating mode, the control device 60 executes the control flow of the parallel dehumidifying and heating mode shown in FIG. First, in step S800, the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined so that the blower air can be heated by the heater core 42, as in the serial dehumidifying and heating mode.

  In step S810, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined. In the parallel dehumidifying and heating mode, the increase / decrease amount ΔIVO is determined by the feedback control method based on the deviation between the target high-temperature heat medium temperature TWHO and the high-temperature heat medium temperature TWH, and the high-temperature heat medium temperature TWH is set to the target high-temperature heat medium temperature It is determined to approach TWHO.

  In step S820, the target superheat degree SHEO of the refrigerant on the outlet side of the indoor evaporator 18 is determined. As the target superheat degree SHEO, a predetermined constant (5 ° C. in the present embodiment) can be adopted.

  In step S830, a change amount ΔKPN1 of the opening degree pattern KPN1 is determined. In the parallel dehumidification heating mode, the superheat degree SHE is determined to be close to the target superheat degree SHEO by a feedback control method based on a deviation between the target superheat degree SHEO and the superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18. .

  The superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18 is calculated based on the temperature T4 detected by the fourth refrigerant temperature sensor 64d and the evaporator temperature Tefin.

  In the parallel dehumidifying / heating mode, as shown in FIG. 13, as the opening degree pattern KPN1 increases, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14b increases. Become. Therefore, when the opening degree pattern KPN1 increases, the flow rate of the refrigerant flowing into the indoor evaporator 18 increases, and the superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18 decreases.

  In step S840, the opening degree SW of the air mix door 34 is calculated as in the cooling mode. Here, in the parallel dehumidifying and heating mode, the target outlet temperature TAO is higher than in the cooling mode, so that the opening degree SW of the air mix door 34 approaches 100% as in the serial dehumidifying and heating mode. For this reason, in the parallel dehumidifying and heating mode, the opening of the air mix door 34 is determined so that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.

  In step S850, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the parallel dehumidifying and heating mode, the heating expansion valve 14a is set to the throttled state, the cooling expansion valve 14b is set to the throttled state, and the cooling expansion valve 14c is set to the fully closed state. The intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened. Furthermore, a control signal or a control voltage is output to each control target device so that the control state determined in steps S810, S830, and S840 is obtained, and the process returns to step S10.

  Therefore, in the refrigerating cycle device 10 in the parallel dehumidifying and heating mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the heating expansion valve 14a → the outdoor heat exchanger 16 → the heating passage 22b → the accumulator 21 → compression. The refrigerant circulates in the order of the suction port 11a of the compressor 11 and the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the bypass passage 22a → the cooling expansion valve 14b → the indoor evaporator 18 → the evaporation pressure regulating valve 20. A vapor compression refrigeration cycle is formed in which the refrigerant is circulated in the order of the accumulator 21 and the suction port 11a of the compressor 11.

  That is, in the refrigerating cycle device 10 in the parallel dehumidifying and heating mode, the water-refrigerant heat exchanger 12 functions as a radiator for radiating the refrigerant discharged from the compressor 11, the heating expansion valve 14a functions as a pressure reducing unit, The outdoor heat exchanger 16 functions as an evaporator, and the heating expansion valve 14a and the cooling expansion valve 14b connected in parallel to the outdoor heat exchanger 16 function as a pressure reducing unit. A refrigeration cycle that functions as an evaporator is configured.

  According to this, the blown air can be cooled by the indoor evaporator 18, and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the parallel dehumidifying and heating 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 interior, thereby dehumidifying and heating the vehicle interior. It can be performed.

  Further, in the refrigeration cycle apparatus 10 in the parallel dehumidifying and heating mode, the outdoor heat exchanger 16 and the indoor evaporator 18 are connected in parallel to the refrigerant flow, and the evaporation pressure regulating valve 20 is disposed downstream of the indoor evaporator 18. Have been. Thereby, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be made lower than the refrigerant evaporation temperature in the indoor evaporator 18.

  Therefore, in the parallel dehumidification heating mode, the heat absorption amount of the refrigerant in the outdoor heat exchanger 16 can be increased, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased as compared with the serial dehumidification heating mode. . As a result, in the parallel dehumidifying and heating mode, the blown air can be reheated with a higher heating capacity than in the serial dehumidifying and heating mode.

(4) Heating Mode In the heating mode, the control device 60 executes the control flow of the heating mode shown in FIG. First, in step S900, similarly to the parallel dehumidification heating mode, the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined. In step S910, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined as in the parallel dehumidifying / heating mode.

  In step S920, the target supercooling degree SCO2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is determined. The target degree of supercooling SCO2 is determined by referring to a control map based on the suction temperature of the air blown into the indoor evaporator 18 or the outside temperature Tam. In the control map of the present embodiment, the target degree of supercooling SCO2 is determined such that the coefficient of performance (COP) of the cycle approaches the maximum value.

  In step S930, an increase / decrease amount ΔEVH of the throttle opening of the heating expansion valve 14a is determined. The increase / decrease amount ΔEVH is determined based on a deviation between the target supercooling degree SCO2 and the supercooling degree SC2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 by a feedback control method. The supercooling degree SC2 of the refrigerant flowing out of the refrigerant passage is determined so as to approach the target supercooling degree SCO2.

  The supercooling degree SC2 of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is calculated based on the temperature T2 detected by the second refrigerant temperature sensor 64b and the pressure P1 detected by the first refrigerant pressure sensor 65a. Is done.

  In step S940, similarly to the cooling mode, the opening degree SW of the air mix door 34 is calculated. Here, in the heating mode, the target outlet temperature TAO is higher than in the cooling mode, so that the opening degree SW of the air mix door 34 approaches 100%. Therefore, in the heating mode, the opening of the air mix door 34 is determined such that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the heater core 42.

  In step S950, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the heating mode, the heating expansion valve 14a is set to the throttled state, the cooling expansion valve 14b is set to the fully closed state, and the cooling expansion valve 14c is set to the fully closed state. The intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is opened. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S910, S930, and S940 is obtained, and the process returns to step S10.

  Therefore, in the refrigeration cycle apparatus 10 in the heating mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the expansion valve 14a for heating → the outdoor heat exchanger 16 → the passage 22b for heating → the accumulator 21 → the compressor 11 , A vapor compression refrigeration cycle in which the refrigerant is circulated in the order of the suction ports 11a.

  That is, in the refrigeration cycle apparatus 10 in the heating mode, the water-refrigerant heat exchanger 12 functions as a radiator that radiates the refrigerant discharged from the compressor 11, the heating expansion valve 14a functions as a pressure reducing unit, and the outdoor heat A refrigeration cycle in which the exchanger 16 functions as an evaporator is configured.

  According to this, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the heating mode, the air in the vehicle compartment can be heated by blowing the blast air heated by the heater core 42 into the vehicle compartment.

(5) Cooling + cooling mode In the cooling + cooling mode, the control device 60 executes a control flow in the cooling + cooling mode shown in FIG. First, in steps S1100 to S1160, similar to steps S600 to 660 in the cooling mode, the target evaporator temperature TEO, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11, the increase / decrease amount ΔEVC of the throttle opening of the cooling expansion valve 14b, The amount of increase / decrease ΔEVI of the throttle opening of the intermediate pressure expansion valve 14d and the opening SW of the air mix door 34 are determined.

  Next, in step S1170, the target superheat degree SHCO of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 is determined. As the target degree of superheat SHCO, a predetermined constant (5 ° C. in the present embodiment) can be adopted.

  In step S1180, the amount of increase or decrease ΔEVB of the throttle opening of the cooling expansion valve 14c is determined. In the cooling + cooling mode, the amount of increase / decrease ΔEVB is based on the deviation between the target superheat degree SHCO and the superheat degree SHC of the refrigerant flowing out of the refrigerant passage of the chiller 19, and the refrigerant flowing out of the refrigerant passage of the chiller 19 by a feedback control method. Is determined such that the superheat degree SHC approaches the target superheat degree SHCO.

  The superheat degree SHC of the refrigerant flowing out of the refrigerant passage of the chiller 19 is calculated based on the temperature T5 detected by the fifth refrigerant temperature sensor 64e and the pressure P2 detected by the second refrigerant pressure sensor 65b.

  In step S1190, the target low-temperature-side heat medium temperature TWLO of the low-temperature-side heat medium flowing out of the water passage of the chiller 19 is determined. The target low-temperature-side heat medium temperature TWLO is determined with reference to a control map based on the heat generation amount of the battery 80 and the outside air temperature Tam. In the control map of the present embodiment, the target low-temperature-side heat medium temperature TWLO is determined to decrease with an increase in the amount of heat generated by the battery 80 and an increase in the outside temperature Tam.

  In step S1200, it is determined whether the first low-temperature heat medium temperature TWL1 detected by the first low-temperature heat medium temperature sensor 67a is higher than the target low-temperature heat medium temperature TWLO.

  If it is determined in step S1200 that the first low-temperature heat medium temperature TWL1 is higher than the target low-temperature heat medium temperature TWLO, the process proceeds to step S1220, where the first low-temperature heat medium temperature TWL1 is set to the target low temperature. If it is not determined that the temperature is higher than the side heat medium temperature TWLO, the process proceeds to step S1210. In step S1210, the cooling expansion valve 14c is fully closed, and the process proceeds to step S1220.

  In step S1220, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit of the cooling + cooling mode, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is throttled, and the cooling expansion valve 14c is throttled. Then, the intermediate pressure expansion valve 14d is set in the throttle state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed.

  Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S1110, S1130, S1150, S1160, S1180, and S1210 is obtained, and the process returns to step S10.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling / cooling mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 (→ the heating expansion valve 14a) → the outdoor heat exchanger 16 → the check valve 17 → the seventh valve. The refrigerant is circulated in the order of the three-way joint 13g → the intermediate pressure expansion valve 14d → the intermediate temperature side passage 23a of the internal heat exchanger 23 → the intermediate pressure suction port 11b of the compressor 11, and the seventh three-way joint 13g → the internal heat exchanger The refrigerant flows in the order of the high-temperature side passage 23b → the fifth three-way joint 13e → the cooling expansion valve 14b → the indoor evaporator 18 → the sixth three-way joint 13f → the evaporating pressure regulating valve 20 → the accumulator 21 → the suction port 11a of the compressor 11. While circulating, the seventh three-way joint 13g → the high-temperature side passage 23b of the internal heat exchanger 23 → the fifth three-way joint 13e → the cooling expansion valve 14c → the chiller 19 → the sixth three-way joint 13f → the evaporating pressure regulating valve 20 Accumulator 21 → gas injection cycle for circulating refrigerant in order of the suction port 11a of the compressor 11 is constructed.

  More specifically, when the control device 60 operates the compressor 11, the state of the refrigerant changes as shown in the Mollier diagram of FIG. In FIG. 16, the state of the refrigerant at the same position in the cycle configuration as the Mollier diagram of FIG. 9 described in the cooling mode is indicated by the same reference numeral (alphabet) as in FIG. Changed according to the figure number. This applies to the following Mollier diagrams.

  That is, the high-pressure refrigerant (point a16 in FIG. 16) discharged from the discharge port 11c of the compressor 11 releases heat in the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 in the same manner as in the cooling mode. 7 The branch is made at the three-way joint 13g (point a16 → point b16 → point c16 in FIG. 16).

  One refrigerant branched at the seventh three-way joint 13g is reduced in pressure by the intermediate pressure expansion valve 14d, and increases the enthalpy when flowing through the intermediate temperature side passage 23a of the internal heat exchanger 23 (FIG. 16). c16 point → d16 point → e16 point). Then, the refrigerant is sucked from the intermediate pressure suction port 11b of the compressor 11 and merges with the refrigerant (point i16 in FIG. 16) that has been pressurized by the low-stage compression mechanism of the compressor 11 (point j16 in FIG. 16).

  The other refrigerant branched at the seventh three-way joint 13g reduces the enthalpy when flowing through the high-temperature side passage 23b of the internal heat exchanger 23 (point c16 → point f16 in FIG. 16). The flow of the refrigerant flowing out of the high-temperature side passage 23b of the internal heat exchanger 23 is the fifth three-way joint, which is the downstream branch portion, because both the cooling expansion valve 14b and the cooling expansion valve 14c are in the throttled state. Branched at 13e.

  One of the refrigerants branched at the fifth three-way joint 13e is reduced in pressure by the cooling expansion valve 14b as in the cooling mode, and absorbs heat from the blown air to evaporate when flowing through the indoor evaporator 18 ( (Point f16 → point g16 → point h16 in FIG. 16). Thereby, the blown air is cooled.

  The other refrigerant branched at the fifth three-way joint 13e flows into the cooling expansion valve 14c and is reduced in pressure until it becomes a low-pressure refrigerant (point f16 → point k16 in FIG. 16). At this time, the throttle opening of the cooling expansion valve 14c is adjusted such that the superheat degree SHC of the refrigerant flowing out of the refrigerant passage of the chiller 19 approaches the target superheat degree SHCO.

  The low-pressure refrigerant decompressed by the cooling expansion valve 14c flows into the refrigerant passage of the chiller 19. The low-pressure refrigerant flowing into the refrigerant passage of the chiller 19 absorbs heat from the low-temperature side heat medium flowing through the water passage and evaporates (point k16 → point m16 in FIG. 16). Thereby, the low-temperature side heat medium is cooled. Then, the low-temperature side heat medium cooled by the chiller 19 is pressure-fed to the cooling heat exchange unit 52, and the battery 80 is cooled.

  The flow of the refrigerant flowing out of the refrigerant passage of the chiller 19 merges with the flow of the refrigerant flowing out of the indoor evaporator 18 at the sixth three-way joint 13f, which is the junction (points h16 → n16 and m16 in FIG. 16). → n16 points). The refrigerant flowing out of the sixth three-way joint 13f flows into the accumulator 21. The gas-phase refrigerant separated by the accumulator 21 is sucked through the suction port 11a of the compressor 11, and is pressurized by the low-stage compression mechanism (point n16 → point i16 in FIG. 16).

  According to this, it is possible to cool the blown air in the indoor evaporator 18 and to heat the high-temperature side heat medium in the water-refrigerant heat exchanger 12. Further, the chiller 19 can cool the low-pressure side heat medium.

  Therefore, in the vehicle air conditioner 1 in the cooling / cooling mode, a part of the blast air cooled by the indoor evaporator 18 is reheated by the heater core 42 by adjusting the opening degree of the air mix door 34, and the target outlet temperature is set. By blowing the blast air whose temperature has been adjusted so as to approach the TAO into the vehicle interior, the interior of the vehicle interior can be cooled.

  Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.

  Further, in the refrigeration cycle apparatus 10 in the cooling / cooling mode, a gas injection cycle is configured. Therefore, the operation of the internal heat exchanger 23 changes the enthalpy of the refrigerant on the outlet side of the indoor evaporator 18 to the refrigerant on the inlet side of the indoor evaporator 18. Enthalpy difference can be enlarged. As a result, the cooling capacity of the blown air can be improved as compared with a normal vapor compression refrigeration cycle.

  Similarly, the enthalpy difference obtained by subtracting the enthalpy of the refrigerant on the inlet side of the refrigerant passage of the chiller 19 from the enthalpy of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 can be increased. As a result, the cooling capacity of the low-temperature side heat medium can be improved as compared with a normal vapor compression refrigeration cycle.

  In the Mollier diagram of FIG. 16, for the sake of clarity, the pressure of the refrigerant flowing out of the indoor evaporator 18 (point h16 in FIG. 16) and the pressure of the refrigerant flowing out of the refrigerant passage of the chiller 19 (see FIG. (point m16) are slightly different pressures, but the pressures of these refrigerants are equal. The refrigerant branched at the fifth three-way joint 15e and decompressed by the cooling expansion valve 14b (point g16 in FIG. 16) and the refrigerant depressurized by the cooling expansion valve 14c (point k16 in FIG. 16). The enthalpy is also equivalent.

(6) Series dehumidification heating + cooling mode In the series dehumidification heating + cooling mode, the control device 60 executes a control flow in the series dehumidification heating + cooling mode shown in FIG. First, in steps S1300 to S1340, similarly to steps S700 to S740 in the series dehumidifying and heating mode, the target evaporator temperature TEO, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11, the change amount ΔKPN1 of the opening degree pattern KPN1, the air mix door The opening degree SW of No. 34 is determined.

  In subsequent steps S1350 to S1370, similarly to steps S1170 to S1190 in the cooling + cooling mode, the target superheat degree SHCO, the increase / decrease amount ΔEVB of the throttle opening of the cooling expansion valve 14c, and the target low-temperature side heat medium temperature TWLO are determined.

  Next, in step S1380, when it is determined that the first low-temperature side heat medium temperature TWL1 is higher than the target low-temperature side heat medium temperature TWLO, similarly to the cooling + cooling mode, the process proceeds to step S1400. If it is not determined that the first low-temperature-side heat medium temperature TWL1 is higher than the target low-temperature-side heat medium temperature TWLO, the process proceeds to step S1390. In step S1390, the cooling expansion valve 14c is fully closed, and the process proceeds to step S1400.

  In step S1400, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit of the serial dehumidifying heating and cooling mode, the heating expansion valve 14a is set in the throttled state, the cooling expansion valve 14b is set in the throttled state, and the cooling expansion valve 14c is throttled. Then, the intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed.

  Furthermore, a control signal or a control voltage is output to each control target device so that the control state determined in steps S1310, S1330, S1340, S1360, and S1390 is obtained, and the process returns to step S10.

  Therefore, in the series dehumidification heating + cooling mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the heating expansion valve 14a → the outdoor heat exchanger 16 → the check valve 17 → the fifth three-way joint 13e → the cooling. The refrigerant circulates in the order of the expansion valve 14b for use → the indoor evaporator 18 → the evaporating pressure regulating valve 20 → the accumulator 21 → the suction port 11a of the compressor 11 and the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → Heating expansion valve 14a → outdoor heat exchanger 16 → check valve 17 → fifth three-way joint 13e → cooling expansion valve 14c → chiller 19 → evaporating pressure regulating valve 20 → accumulator 21 → suction port 11a of compressor 11. A vapor compression refrigeration cycle in which the refrigerant circulates is configured.

  That is, in the refrigeration cycle apparatus 10 in the series dehumidification heating and cooling mode, a water-refrigerant heat exchanger 12 functions as a radiator, and a vapor compression refrigeration cycle in which the indoor evaporator 18 and the chiller 19 function as an evaporator is configured. Is done.

  That is, in the refrigeration cycle apparatus 10 in the serial dehumidification heating mode, the water-refrigerant heat exchanger 12 functions as a radiator that radiates the refrigerant discharged from the compressor 11, the heating expansion valve 14a functions as a pressure reducing unit, Further, the cooling expansion valve 14b functions as a decompression unit, the indoor evaporator 18 functions as an evaporator, and the cooling expansion valve 14c connected in parallel to the cooling expansion valve 14b and the indoor evaporator 18. Functions as a decompression unit, and a refrigeration cycle in which the chiller 19 functions as an evaporator is configured.

  Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as a radiator is configured. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as an evaporator is configured.

  According to this, the blown air can be cooled by the indoor evaporator 18, and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the chiller 19 can cool the low-pressure side heat medium.

  Therefore, in the refrigeration cycle apparatus 10 in the series dehumidifying heating and cooling 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 interior, thereby dehumidifying the vehicle interior. Heating can be performed. At this time, by increasing the opening degree pattern KPN1, it is possible to improve the heating capability of the blower air in the heater core 42, as in the serial dehumidifying and heating mode.

  Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.

(7) Parallel dehumidification heating + cooling mode In the parallel dehumidification heating + cooling mode, the control device 60 executes a control flow in the parallel dehumidification heating + cooling mode shown in FIG. First, in steps S1500 to S1540, similarly to steps S800 to S840 in the parallel dehumidifying and heating mode, the target high-temperature side heat medium temperature TWHO, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11, the target superheat degree SHEO, and the opening degree pattern KPN1 are determined. The change amount ΔKPN1 and the opening degree SW of the air mix door 34 are determined.

  In subsequent steps S1550 to S1570, similarly to steps S1170 to S1190 in the cooling + cooling mode, the target superheat degree SHCO, the increase / decrease amount ΔEVB of the throttle opening of the cooling expansion valve 14c, and the target low-temperature side heat medium temperature TWLO are determined.

  Next, in step S1580, when it is determined that the first low-temperature side heat medium temperature TWL1 is higher than the target low-temperature side heat medium temperature TWLO, similarly to the cooling + cooling mode, the process proceeds to step S1600. If it is not determined that the first low-temperature-side heat medium temperature TWL1 is higher than the target low-temperature-side heat medium temperature TWLO, the process proceeds to step S1590. In step S1590, the cooling expansion valve 14c is fully closed, and the process proceeds to step S1600.

  In step S1600, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the parallel dehumidifying heating + cooling mode, the heating expansion valve 14a is set in the throttled state, the cooling expansion valve 14b is set in the throttled state, and the cooling expansion valve 14c is throttled. Then, the intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened.

  Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S1510, S1530, S1540, S1560, and S1590 is obtained, and the process returns to step S10.

  Therefore, in the refrigerating cycle device 10 in the parallel dehumidifying heating and cooling mode, the discharge port 11c of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the heating passage 22b, and the accumulator 21. → The refrigerant circulates in the order of the suction port 11a of the compressor 11 and the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the bypass passage 22a → the cooling expansion valve 14b → the indoor evaporator 18 → the evaporation pressure adjustment. Refrigerant circulates in the order of valve 20 → accumulator 21 → suction port 11a of compressor 11; further, discharge port 11c of compressor 11 → water-refrigerant heat exchanger 12 → bypass passage 22a → cooling expansion valve 14c → chiller 19 A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the evaporating pressure regulating valve 20, the accumulator 21, and the suction port 11a of the compressor 11 is configured.

  That is, in the refrigerating cycle device 10 in the parallel dehumidifying heating / cooling mode, the water-refrigerant heat exchanger 12 functions as a radiator that radiates the refrigerant discharged from the compressor 11, and the heating expansion valve 14a functions as a pressure reducing unit. In addition, the outdoor heat exchanger 16 functions as an evaporator, and the heating expansion valve 14a and the cooling expansion valve 14b connected in parallel to the outdoor heat exchanger 16 function as a decompression unit. Reference numeral 18 functions as an evaporator, and a cooling expansion valve 14c connected in parallel to the heating expansion valve 14a and the outdoor heat exchanger 16 functions as a pressure reducing unit, and the chiller 19 functions as an evaporator. A refrigeration cycle is configured.

  According to this, the blown air can be cooled by the indoor evaporator 18, and the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Further, the chiller 19 can cool the low-pressure side heat medium.

  Therefore, in the vehicle air conditioner 1 in the parallel dehumidification heating + cooling mode, the blast air cooled and dehumidified by the indoor evaporator 18 is re-heated by the heater core 42 and blown out into the vehicle interior, so that the vehicle interior is improved. Dehumidification heating can be performed. At this time, by making the refrigerant evaporation temperature in the outdoor heat exchanger 16 lower than the refrigerant evaporation temperature in the indoor evaporator 18, the blown air can be reheated with a higher heating capacity than in the series dehumidifying heating + cooling mode.

  Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.

(8) Heating + Cooling Mode In the heating + cooling mode, the control device 60 executes the control flow of the heating + cooling mode shown in FIG. First, in step S300, the target low-temperature-side heat medium temperature TWLO of the low-temperature side heat medium is determined so that the battery 80 can be cooled by the cooling heat exchange unit 52, similarly to the cooling + cooling mode.

  In step S310, an increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined. In the heating + cooling mode, the increase / decrease amount ΔIVO is determined based on the deviation between the target low-temperature side heat medium temperature TWLO and the first low-temperature side heat medium temperature TWL1, and the first low-temperature side heat medium temperature TWL1 is set to the target low temperature. It is determined so as to approach the side heat medium temperature TWLO.

  In step S320, the target supercooling degree SCO1 of the refrigerant flowing out of the outdoor heat exchanger 16 is determined. The target supercooling degree SCO1 in the heating + cooling mode is determined by referring to the control map based on the outside temperature Tam. In the control map of the present embodiment, the target degree of supercooling SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

  In step S330, the amount of increase or decrease ΔEVB of the throttle opening of the cooling expansion valve 14c is determined. The increase / decrease amount ΔEVB is based on a deviation between the target degree of supercooling SCO1 and the degree of supercooling SC1 of the refrigerant on the outlet side of the outdoor heat exchanger 16, and is based on a feedback control method. SC1 is determined so as to approach target supercooling degree SCO1. The degree of supercooling SC1 is calculated in the same manner as in the cooling mode.

  In step S340, the opening degree SW of the air mix door 34 is calculated as in the cooling mode.

  In step S350, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit of the heating + cooling mode, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is fully closed, and the cooling expansion valve 14c is throttled. The intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each control target device so that the control state determined in steps S310, S330, and S340 is obtained, and the process returns to step S10.

  Accordingly, in the refrigeration cycle apparatus 10 in the heating + cooling mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 (→ the heating expansion valve 14a) → the outdoor heat exchanger 16 → the check valve 17 → the cooling. A vapor compression refrigeration cycle is formed in which the refrigerant circulates in the order of the expansion valve 14c, the chiller 19, the evaporating pressure regulating valve 20, the accumulator 21, and the suction port 11a of the compressor 11.

  That is, in the refrigeration cycle apparatus 10 in the heating + cooling mode, the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as a radiator for radiating the refrigerant discharged from the compressor 11, and the cooling expansion valve 14c is provided. A vapor compression refrigeration cycle in which the chiller 19 functions as an evaporator and functions as a decompression unit that decompresses the refrigerant is configured.

  According to this, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12, and the low-temperature side heat medium can be cooled by the chiller 19.

  Therefore, in the vehicle air conditioner 1 in the heating + cooling mode, the inside of the vehicle compartment can be heated by blowing the blast air heated by the heater core 42 into the vehicle compartment. Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.

(9) Heating + Series Cooling Mode In the heating + series cooling mode, the control device 60 executes the control flow of the heating + series cooling mode shown in FIG. First, in step S400, the target low-temperature-side heat medium temperature TWLO is determined as in the heating + cooling mode. In step S410, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined as in the heating + cooling mode. In step S420, the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined in the same manner as in the series dehumidification heating mode.

  In step S430, the change amount ΔKPN2 of the opening degree pattern KPN2 is determined. The opening pattern KPN2 is a parameter for determining a combination of the throttle opening of the heating expansion valve 14a and the throttle opening of the cooling expansion valve 14c.

  Specifically, in the heating + series cooling mode, as shown in FIG. 21, the opening degree pattern KPN2 increases as the target outlet temperature TAO increases. Then, as the opening degree pattern KPN2 increases, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14c increases.

  In step S440, the opening degree SW of the air mix door 34 is calculated as in the cooling mode.

  In step S450, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit of the heating + series cooling mode, the heating expansion valve 14a is set in the throttled state, the cooling expansion valve 14b is set in the fully closed state, and the cooling expansion valve 14c is throttled. Then, the intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or a control voltage is output to each control target device so that the control state determined in steps S310, S330, and S340 is obtained, and the process returns to step S10.

  Accordingly, in the refrigeration cycle apparatus 10 in the heating + series cooling mode, the discharge port 11c of the compressor 11, the water-refrigerant heat exchanger 12, the heating expansion valve 14a, the outdoor heat exchanger 16, the check valve 17, and the expansion for cooling. A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the suction port 11a of the compressor 11 is configured.

  That is, in the refrigeration cycle apparatus 10 in the heating + series cooling mode, the water-refrigerant heat exchanger 12 functions as a radiator for radiating the refrigerant discharged from the compressor 11, and the heating expansion valve 14a and the cooling expansion valve 14c. Function as a decompression unit, and a refrigeration cycle of a vapor compression type in which the chiller 19 functions as an evaporator.

  Furthermore, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as a radiator is configured. When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, a cycle in which the outdoor heat exchanger 16 functions as an evaporator is configured.

  According to this, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12, and the low temperature side heat medium can be cooled by the chiller 19.

  Therefore, in the vehicle air conditioner 1 in the heating + series cooling mode, the inside of the vehicle compartment can be heated by blowing the blast air heated by the heater core 42 into the vehicle compartment. Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.

  Further, when the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is higher than the outside temperature Tam, the outdoor heat exchanger 16 increases the opening degree pattern KPN2 in accordance with the increase in the target outlet temperature TAO. The refrigerant saturation temperature at 16 decreases, and the difference from the outside air temperature Tam decreases. Thereby, the heat radiation amount of the refrigerant in the outdoor heat exchanger 16 can be reduced, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased.

  When the saturation temperature of the refrigerant in the outdoor heat exchanger 16 is lower than the outside air temperature Tam, the outdoor heat exchanger 16 increases the opening degree pattern KPN2 as the target outlet temperature TAO increases. The mild temperature of the refrigerant at 16 decreases, and the temperature difference from the outside air temperature Tam increases. Thereby, the heat absorption amount of the refrigerant in the outdoor heat exchanger 16 can be increased, and the heat radiation amount of the refrigerant in the water-refrigerant heat exchanger 12 can be increased.

  In other words, in the heating + series cooling mode, the amount of heat released from the refrigerant to the high-temperature side heat medium in the water-refrigerant heat exchanger 12 is increased by increasing the opening degree pattern KPN2 in accordance with the increase in the target outlet temperature TAO. Can be. Therefore, in the heating + series cooling mode, the heating capacity of the blower air in the heater core 42 can be improved as the target outlet temperature TAO increases.

  As a result, in the heating + series cooling mode, the blown air can be heated with a higher heating capacity than in the heating + cooling mode. In other words, the heating + cooling mode is an operation mode in which the blast air is heated with a lower heating capacity than the heating + series cooling mode.

(10) Heating + Parallel Cooling Mode In the heating + parallel cooling mode, the control device 60 executes the control flow of the heating + parallel cooling mode shown in FIG. First, in step S500, the target high-temperature-side heat medium temperature TWHO of the high-temperature side heat medium is determined so that the air blown by the heater core 42 can be heated, similarly to the serial dehumidifying and heating mode.

  In step S510, an increase / decrease amount ΔIVO of the rotation speed of the compressor 11 is determined. In the heating + parallel cooling mode, the increase / decrease amount ΔIVO is calculated by the feedback control method based on the deviation between the target high-temperature heat medium temperature TWHO and the high-temperature heat medium temperature TWH, as in the parallel dehumidifying / heating mode. The temperature TWH is determined so as to approach the target high-temperature-side heat medium temperature TWHO.

  In step S520, the target superheat degree SHCO of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 is determined. As the target degree of superheat SHCO, a predetermined constant (5 ° C. in the present embodiment) can be adopted.

  In step S530, a change amount ΔKPN2 of the opening degree pattern KPN2 is determined. In the heating + parallel cooling mode, the superheat degree SHC is determined to approach the target superheat degree SHCO by a feedback control method based on a difference between the target superheat degree SHCO and the superheat degree SHC of the refrigerant on the outlet side of the refrigerant passage of the chiller 19. Is done.

  In the heating + parallel cooling mode, as shown in FIG. 23, as the opening degree pattern KPN2 increases, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14c decreases. growing. Therefore, when the opening degree pattern KPN2 increases, the flow rate of the refrigerant flowing into the refrigerant passage of the chiller 19 increases, and the superheat degree SHC of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 decreases.

  In step S540, similarly to the cooling mode, the opening degree SW of the air mix door 34 is calculated. In step S550, the target low-temperature-side heat medium temperature TWLO of the low-temperature side heat medium is determined as in the cooling / cooling mode.

  In step S560, it is determined whether the first low-temperature heat medium temperature TWL1 detected by the first low-temperature heat medium temperature sensor 67a is higher than the target low-temperature heat medium temperature TWLO.

  If it is determined in step S560 that the first low-temperature heat medium temperature TWL1 is higher than the target low-temperature heat medium temperature TWLO, the process proceeds to step S580, where the first low-temperature heat medium temperature TWL1 is set to the target low temperature. If it is not determined that the temperature is higher than the side heat medium temperature TWLO, the process proceeds to step S570. In step S570, the cooling expansion valve 14c is fully closed, and the process proceeds to step S580.

  In step S580, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the heating + parallel cooling mode, the heating expansion valve 14a is set in the throttled state, the cooling expansion valve 14b is set in the fully closed state, and the cooling expansion valve 14c is throttled. Then, the intermediate pressure expansion valve 14d is fully closed, the dehumidifying on-off valve 15a is opened, and the heating on-off valve 15b is opened. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S510, S530, S540, and S570 is obtained, and the process returns to step S10.

  Therefore, in the refrigeration cycle apparatus 10 in the heating + parallel cooling mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the heating expansion valve 14a → the outdoor heat exchanger 16 → the heating passage 22b → the accumulator 21 → The refrigerant circulates in the order of the suction port 11a of the compressor 11 and the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the bypass passage 22a → the cooling expansion valve 14c → the chiller 19 → the evaporation pressure regulating valve 20 → A vapor compression refrigeration cycle in which the refrigerant circulates in the order of the accumulator 21 and the suction port 11a of the compressor 11 is configured.

  That is, in the refrigerating cycle device 10 in the heating + parallel cooling mode, the water-refrigerant heat exchanger 12 functions as a radiator for radiating the refrigerant discharged from the compressor 11, and the heating expansion valve 14a functions as a pressure reducing unit. The outdoor heat exchanger 16 functions as an evaporator, the heating expansion valve 14a and the cooling expansion valve 14c connected in parallel to the outdoor heat exchanger 16 function as a pressure reducing unit, and the chiller 19 evaporates. A refrigeration cycle that functions as a vessel is configured.

  According to this, the high-temperature side heat medium can be heated by the water-refrigerant heat exchanger 12, and the low-temperature side heat medium can be cooled by the chiller 19.

  Therefore, in the vehicle air conditioner 1 in the heating + parallel cooling mode, the inside of the vehicle cabin can be heated by blowing the blast air heated by the heater core 42 into the vehicle cabin. Further, the battery 80 can be cooled by causing the low-temperature side heat medium cooled by the chiller 19 to flow into the cooling heat exchange section 52.

  Further, in the refrigeration cycle apparatus 10 in the heating + parallel cooling mode, the outdoor heat exchanger 16 and the chiller 19 are connected in parallel to the refrigerant flow, and the evaporation pressure regulating valve 20 is disposed downstream of the refrigerant passage of the chiller 19. Have been. Thereby, the refrigerant evaporation temperature in the outdoor heat exchanger 16 can be made lower than the refrigerant evaporation temperature in the refrigerant passage of the chiller 19.

  Therefore, in the heating + parallel cooling mode, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased more than in the heating + serial cooling mode, and the amount of heat release of the refrigerant in the water-refrigerant heat exchanger 12 can be increased. Can be. As a result, in the heating + parallel cooling mode, the blown air can be reheated with a higher heating capacity than in the heating + series cooling mode.

(11) Cooling Mode In the cooling mode, the control device 60 executes the control flow of the cooling mode shown in FIG. First, in steps S1000 to S1030, similarly to steps S300 to S330 in the heating + cooling mode, the target low-temperature side heat medium temperature TWLO of the low-temperature side heat medium, the increase / decrease amount ΔIVO of the rotation speed of the compressor 11, and the target degree of subcooling SCO1 The opening degree SW of the increase / decrease amount ΔEVB of the throttle opening degree of the cooling expansion valve 14c is determined.

  In steps S1040 to S1060, similarly to steps S640 to S660 in the cooling mode, the target superheat degree SHIO, the increase / decrease amount ΔEVI of the throttle opening of the intermediate pressure expansion valve 14d, and the opening SW of the air mix door 34 are determined.

  Here, in the cooling mode, since the target outlet temperature TAO becomes lower than the heating reference temperature γ, the opening degree SW of the air mix door 34 approaches 0%. For this reason, in the cooling mode, the opening of the air mix door 34 is determined so that substantially the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the cool air bypass passage 35.

  In step S1070, in order to switch the refrigeration cycle apparatus 10 to the refrigerant circuit in the cooling mode, the heating expansion valve 14a is fully opened, the cooling expansion valve 14b is fully closed, and the cooling expansion valve 14c is throttled, The intermediate pressure expansion valve 14d is set in the throttle state, the dehumidifying on-off valve 15a is closed, and the heating on-off valve 15b is closed. Further, a control signal or control voltage is output to each control target device so that the control state determined in steps S1010, S1030, S1050, and S1060 is obtained, and the process returns to step S10.

  Therefore, in the refrigeration cycle device 10 in the cooling mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 (→ the heating expansion valve 14a) → the outdoor heat exchanger 16 → the check valve 17 → the seventh three-way joint. 13g → the intermediate pressure expansion valve 14d → the intermediate temperature side passage 23a of the internal heat exchanger 23 → the refrigerant is circulated in the order of the intermediate pressure suction port 11b of the compressor 11, and the seventh three-way joint 13g → the internal heat exchanger 23 A gas injection cycle is formed in which the refrigerant is circulated in the order of the high-temperature side passage 23b, the cooling expansion valve 14c, the chiller 19, the evaporation pressure regulating valve 20, the accumulator 21, and the suction port 11a of the compressor 11.

  More specifically, when the control device 60 operates the compressor 11, the state of the refrigerant changes as shown in the Mollier diagram of FIG.

  That is, the high-pressure refrigerant (point a25 in FIG. 25) discharged from the discharge port 11c of the compressor 11 radiates heat in the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 in the same manner as in the cooling mode. 7 The branch is made at the three-way joint 13g (point a25 → point b25 → point c25 in FIG. 25).

  One refrigerant branched at the seventh three-way joint 13g is sucked from the intermediate pressure suction port 11b of the compressor 11 (point c25 → point d25 → point e25 in FIG. 25) as in the cooling mode. Similar to the cooling mode, the other refrigerant branched at the seventh three-way joint 13g reduces the enthalpy when flowing through the high-temperature side passage 23b of the internal heat exchanger 23 (point c25 → point f25 in FIG. 25). ).

  The refrigerant flowing out of the high-temperature side passage 23b of the internal heat exchanger 23 flows into the cooling expansion valve 14c because the cooling expansion valve 14b is in a fully closed state. The refrigerant flowing into the cooling expansion valve 14c is sucked from the suction port 11a of the compressor 11 (f25 point → k25 point → m25 point in FIG. 25), similarly to the cooling + cooling mode.

  According to this, the chiller 19 can cool the low-temperature side heat medium. Therefore, in the vehicle air conditioner 1 in the cooling mode, the battery 80 can be cooled by flowing the low-temperature side heat medium cooled by the chiller 19 into the cooling heat exchange unit 52.

  Furthermore, in the refrigeration cycle apparatus 10 in the cooling mode, a gas injection cycle is configured, and the operation of the internal heat exchanger 23 causes the enthalpy of the refrigerant on the outlet side of the refrigerant passage of the chiller 19 to enter the refrigerant on the inlet side of the refrigerant passage of the chiller 19. Enthalpy difference can be enlarged. As a result, the cooling capacity of the low-temperature side heat medium can be improved as compared with a normal vapor compression refrigeration cycle.

  As described above, in the refrigeration cycle apparatus 10 of the present embodiment, various operation modes can be switched. Thereby, in the vehicle air conditioner 1, comfortable air conditioning in the vehicle compartment can be realized while appropriately adjusting the temperature of the battery 80.

  For example, in the refrigeration cycle apparatus 10 of the present embodiment, the refrigerant circuit is switched in the order of (1) cooling mode → (2) serial dehumidification / heating mode → (3) parallel dehumidification / heating mode, thereby sequentially adjusting the temperature adjustment capability of the blown air. Can be changed. Therefore, the temperature of the blown air can be adjusted in a wide range from a high temperature to a low temperature.

  Similarly, by switching the refrigerant circuit in the order of (8) heating + cooling mode → (9) heating + series cooling mode → (10) heating + parallel cooling mode, the temperature of the blown air is adjusted while cooling the battery 80. The ability can be changed sequentially. Therefore, the temperature of the blown air can be adjusted in a wide range from a high temperature to a low temperature.

  By the way, in the refrigeration cycle device 10 used not only for air conditioning in the vehicle compartment but also for cooling the battery 80 as in the present embodiment, it is necessary to appropriately cool both the blown air and the low-temperature side heat medium. For this reason, in the refrigeration cycle apparatus 10, the heat load of the cycle in (5) the cooling + cooling mode among the above-described operation modes is higher than the heat load in the (4) heating mode.

  On the other hand, in the refrigeration cycle apparatus 10 of the present embodiment, (5) a gas injection cycle is configured in the cooling / cooling mode, and (4) a normal refrigeration cycle is configured in the heating mode. Therefore, (5) both the blown air and the battery 80 can be sufficiently cooled in the cooling + cooling mode. (4) In the heating mode, the refrigeration cycle apparatus 10 can be operated efficiently without exhibiting an excessive heating capacity of the blown air.

  Further, in the refrigeration cycle apparatus 10 of the present embodiment, as shown in step S1120 in FIG. 15, in the cooling + cooling mode, the refrigerant flowing out of the outdoor heat exchanger 16 (point c16 in FIG. 16) has a supercooling degree. The throttle opening of the cooling expansion valve 14b is controlled so that the refrigerant has the refrigerant. Therefore, the refrigerant (point f16 in FIG. 16) flowing out of the high-temperature side passage 23b of the internal heat exchanger 23 also becomes a refrigerant having a degree of supercooling.

  In other words, in the cooling + cooling mode, the refrigerant flowing into the fifth three-way joint 13e, which is the downstream branch portion, becomes a refrigerant having a degree of supercooling. Thereby, the flow of the liquid-phase refrigerant can be branched at the fifth three-way joint 13e.

  Therefore, when the flow of the gas-liquid two-phase refrigerant is branched at the fifth three-way joint 13e, the flow rate (mass flow rate) of the refrigerant flowing into the indoor evaporator 18 via the expansion valve 14b for cooling and the expansion valve for cooling The flow ratio with respect to the flow rate (mass flow rate) of the refrigerant flowing into the chiller 19 via 14c can be adjusted with high accuracy. As a result, in the cooling + cooling mode, the blown air and the low-temperature side heat medium can be appropriately cooled.

  Further, in the refrigeration cycle device 10 of the present embodiment, the evaporation pressure adjusting valve 20 is disposed on the downstream side of the sixth three-way joint 13f in the refrigerant flow. Therefore, in the (5) cooling + cooling mode, the refrigerant evaporation temperature in the indoor evaporator 18 and the refrigerant evaporation temperature in the chiller 19 can be kept equal to or higher than the frost formation suppression temperature.

  According to this, the control device 60 controls the operation of the cooling expansion valve 14b and the cooling expansion valve 14c to reduce the flow ratio between the refrigerant flow flowing into the indoor evaporator 18 and the refrigerant flow flowing into the chiller 19. The adjustment makes it possible to easily adjust the capacity ratio between the cooling capacity exhibited by the indoor evaporator 18 and the cooling capacity exhibited by the chiller 19. As a result, in the cooling + cooling mode, the blown air and the low-temperature side heat medium can be further appropriately cooled.

  In the refrigeration cycle device 10 of the present embodiment, the inlet of the heating passage 22b is connected to the refrigerant flow upstream of the seventh three-way joint 13g.

  According to this, for example, as in the (4) heating mode, the refrigerant flowing out of the outdoor heat exchanger 16 is guided to the suction port 11a side of the compressor 11 (more specifically, the inlet side of the accumulator 21). In the operation mode, the refrigerant flowing out of the outdoor heat exchanger 16 does not have to pass through the high-temperature side passage 23b of the internal heat exchanger 23. Therefore, the pressure loss when the refrigerant circulates through the cycle can be reduced, and the COP of the cycle can be improved.

  Further, in the refrigeration cycle device 10 of the present embodiment, the outlet of the bypass passage 22 a is connected to the downstream side of the high-temperature side passage 23 b of the internal heat exchanger 23.

  According to this, for example, in the operation mode in which the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is guided to the inflow side of the fifth three-way joint 13e, as in the (3) parallel dehumidification heating mode, -The refrigerant flowing out of the refrigerant passage of the refrigerant heat exchanger 12 does not have to pass through the high-temperature side passage 23b of the internal heat exchanger 23. Therefore, the pressure loss when the refrigerant circulates through the cycle can be reduced, and the COP of the cycle can be improved.

  Further, in the refrigeration cycle device 10 of the present embodiment, (1) the gas injection cycle is configured in the cooling mode. According to this, (1) the cooling capacity of the blast air by the refrigeration cycle device 10 in the cooling mode can be improved. Therefore, for example, it is effective when applied to a vehicle whose destination is an area where the outside air temperature is relatively high over the year.

  In the refrigeration cycle apparatus 10 of the present embodiment, (11) the gas injection cycle is configured in the cooling mode. According to this, (11) the ability of the refrigeration cycle apparatus 10 to cool the low-temperature side heat medium in the cooling mode can be improved. Therefore, for example, the present invention is effective when applied to a vehicle capable of quick charging in which the self-heating amount of the battery 80 increases.

(2nd Embodiment)
In the present embodiment, an example in which the low-temperature side heat medium circuit 50 is omitted from the first embodiment as shown in FIG. 26 will be described. In FIG. 26, the same or equivalent parts as in the first embodiment are denoted by the same reference numerals. This is the same in the following drawings.

  More specifically, in the refrigeration cycle device 10 of the present embodiment, the inlet side of the cooling heat exchange unit 52a is connected to the outlet of the cooling expansion valve 14c. The cooling heat exchange section 52a is a so-called direct cooling type cooler that cools the battery 80 by evaporating the refrigerant flowing through the refrigerant passage and exerting an endothermic effect. Therefore, in the present embodiment, a cooling unit is configured by the cooling heat exchange unit 52a.

  It is desirable that the cooling heat exchanging section 52a has a plurality of refrigerant flow paths connected in parallel with each other so that the entire area of the battery 80 can be uniformly cooled. The other inlet side of the sixth three-way joint 13f is connected to the outlet of the cooling heat exchange section 52a.

  In addition, a cooling heat exchange unit inlet temperature sensor 64h is connected to the input side of the control device 60 of the present embodiment. The cooling heat exchange unit entrance temperature sensor 64h is a cooling heat exchange unit entrance temperature detection unit that detects the temperature of the refrigerant flowing into the refrigerant passage of the cooling heat exchange unit 52.

  Further, the fifth refrigerant temperature sensor 64e of the present embodiment detects the temperature T5 of the refrigerant flowing out of the refrigerant passage of the cooling heat exchange unit 52. The second refrigerant pressure sensor 65b of the present embodiment detects the pressure P2 of the refrigerant flowing out of the refrigerant passage of the cooling heat exchange unit 52a.

  Further, in the control device 60 of the present embodiment, in the operation mode in which the battery 80 needs to be cooled, that is, in the operation mode in which the cooling expansion valve 14c is in the throttled state, the cooling heat exchange unit inlet temperature sensor 64h When the detected temperature T7 is equal to or lower than the reference inlet-side temperature, the cooling expansion valve 14c is closed. As a result, it is possible to prevent the battery 80 from being unnecessarily cooled and the output of the battery 80 from being reduced.

  Other configurations and operations of the refrigeration cycle device 10 are the same as those of the first embodiment. According to this, the same effect as in the first embodiment can be obtained. That is, also in the refrigeration cycle apparatus 10 of the present embodiment, the blown air and the battery 80 can be sufficiently and appropriately cooled without exhibiting excessive cooling capacity and heating capacity in any operation mode.

(Third embodiment)
In the present embodiment, as compared with the first embodiment, as shown in FIG. 27, an example in which a temperature type expansion valve 141 is adopted as an intermediate pressure expansion valve, and an intermediate pressure opening / closing valve 15c is arranged in an intermediate pressure passage 22c. Will be described.

  The thermal expansion valve 141 reduces the pressure of one of the refrigerants branched at the seventh three-way joint 13g until the refrigerant becomes an intermediate-pressure refrigerant, and adjusts the flow rate of the refrigerant flowing through the intermediate-pressure passage 22c. The temperature type expansion valve 141 controls the flow rate of the refrigerant so that the superheat degree SHI of the outlet side refrigerant of the intermediate temperature side passage 23a of the internal heat exchanger 23 approaches a predetermined target superheat degree SHIO (10 ° C. in the present embodiment). It is configured with a mechanical mechanism for adjusting.

  More specifically, the temperature-type expansion valve 141 has a deformable member (specifically, a diaphragm) that deforms according to the temperature and pressure of the refrigerant flowing out of the intermediate temperature side passage 23a of the internal heat exchanger 23. A warming portion and a valve body portion that changes in accordance with the deformation of the deformable member to change the opening degree of the throttle are provided. Further, in the present embodiment, the intermediate pressure temperature sensor 64g and the intermediate pressure sensor 65c are also eliminated.

  The intermediate pressure on-off valve 15c is an electromagnetic valve arranged on the upstream side of the refrigerant flow of the temperature type expansion valve 141 to open and close the intermediate pressure passage 22c. The basic configuration of the intermediate pressure on-off valve 15c is the same as the dehumidifying on-off valve 15a and the heating on-off valve 15b described in the first embodiment. Therefore, the intermediate pressure on-off valve 15c is a refrigerant circuit switching unit. Other configurations of the refrigeration cycle device 10 are the same as those of the first embodiment.

  The control device 60 of the present embodiment opens the intermediate pressure on-off valve 15c in (1) the cooling mode, (5) the cooling and cooling mode, and (11) the cooling mode, and opens and closes the intermediate pressure in other operation modes. The valve 15c is closed. Other operations of the refrigeration cycle device 10 are the same as those of the first embodiment.

  Therefore, also in the refrigeration cycle apparatus 10 of the present embodiment, a gas injection cycle can be configured in (1) cooling mode, (5) cooling + cooling mode, and (11) cooling mode. Further, the thermal expansion valve 141 changes the throttle opening such that the superheat degree SHI of the outlet-side refrigerant of the intermediate-temperature side passage 23a of the internal heat exchanger 23 approaches the target superheat degree SHIO. As a result, the same effect as in the first embodiment can be obtained.

  Furthermore, in the refrigeration cycle device 10 of the present embodiment, the temperature-type expansion valve 141 constituted by a mechanical mechanism is employed, so that complicated control is not required, and the intermediate temperature side of the internal heat exchanger 23 is not required. The flow rate of the refrigerant flowing through the passage 23a can be appropriately adjusted.

(Fourth embodiment)
In the present embodiment, an example will be described in which a heating gas-liquid separator 24, a heating fixed throttle 25, and the like are added to the first embodiment as shown in FIG. In the refrigeration cycle apparatus 10 of the present embodiment, a two-stage depressurization type gas injection cycle can be configured also in the heating mode.

  In the present embodiment, a refrigerant inlet of the heating gas-liquid separator 24 is connected to an outlet of the heating expansion valve 14a. The gas-liquid separator for heating 24 adopts a centrifugal separation system (so-called cyclone separator system) that separates refrigerant gas and liquid by the action of centrifugal force generated by swirling the flow of the refrigerant flowing into the inside. I have.

  The internal volume of the gas-liquid separator 24 for heating has a relatively small volume such that it is not possible to substantially store excess refrigerant even if a load fluctuation occurs in the cycle and the refrigerant circulation flow rate circulating in the cycle fluctuates. ing. Therefore, when the gas-phase refrigerant cannot flow out of the gas-phase refrigerant outlet of the gas-liquid separator for heating 24, the gas-phase refrigerant may flow out of the liquid-phase refrigerant outlet. That is, the refrigerant in the gas-liquid mixed phase may flow out of the liquid-phase refrigerant outlet.

  The gas-phase refrigerant outlet of the heating gas-liquid separator 24 is connected to the intermediate pressure port 11b of the compressor 11 via a gas-phase passage 22d. More specifically, the gas-phase passage 22d of the present embodiment is provided between the gas-phase refrigerant outlet of the gas-liquid separator 24 for heating and the refrigerant flow downstream of the intermediate-temperature side passage 23a of the internal heat exchanger 23 of the intermediate-pressure passage 22c. Side part. A gas-phase passage opening / closing valve 15d that opens and closes the gas-phase passage 22d is disposed in the gas-phase passage 22d.

  The refrigerant inlet side of the outdoor heat exchanger 16 is connected to the liquid-phase refrigerant outlet of the heating gas-liquid separator 24 via a liquid-phase passage 22e. A fixed throttle 25 for heating is arranged in the liquid phase passage 22e. The heating fixed throttle 25 is a pressure reducing unit that reduces the pressure of the refrigerant flowing out of the liquid-phase refrigerant outlet of the heating gas-liquid separator 24 until it becomes a low-pressure refrigerant. As the fixed throttle 25 for heating, a nozzle, an orifice, a capillary tube or the like having a fixed throttle opening can be adopted.

  Further, the liquid-phase refrigerant outlet of the heating gas-liquid separator 24 bypasses the fixed throttle 25 for heating to separate the liquid-phase refrigerant separated by the gas-liquid separator 24 for heating. A fixed throttle bypass passage 22f leading to the side is connected. A bypass passage opening / closing valve 15e that opens and closes the fixed throttle bypass passage 22f is disposed in the fixed throttle bypass passage 22f.

  Here, the pressure loss that occurs when the refrigerant passes through the bypass passage opening / closing valve 15e is extremely smaller than the pressure loss that occurs when the refrigerant passes through the fixed throttle 25 for heating. Therefore, when the bypass passage opening / closing valve 15e is opened, the liquid-phase refrigerant flowing out of the heating gas-liquid separator 24 hardly passes through the heating fixed throttle 25 and passes through the fixed throttle bypass passage 22f through the outdoor. It flows into the heat exchanger 16.

  The basic configuration of the gas phase passage opening / closing valve 15d and the bypass passage opening / closing valve 15e is the same as the dehumidifying opening / closing valve 15a and the heating opening / closing valve 15b described in the first embodiment. Therefore, the gas phase passage opening / closing valve 15d and the bypass passage opening / closing valve 15e are refrigerant circuit switching units. Other configurations of the refrigeration cycle device 10 are the same as those of the first embodiment.

  In the heating mode, the control device 60 of the present embodiment opens the gas phase passage opening / closing valve 15d and closes the bypass passage opening / closing valve 15e in the heating mode. Further, in other operation modes, the gas phase passage opening / closing valve 15d is closed, and the bypass passage opening / closing valve 15e is opened.

  Therefore, in the refrigerating cycle device 10 in the heating mode, the discharge port 11c of the compressor 11 → the water-refrigerant heat exchanger 12 → the expansion valve 14a for heating → the gas-liquid separator 24 for heating → the gas phase passage 22d → the compressor 11 The refrigerant is circulated in the order of the intermediate pressure suction port 11b, and further, the heating gas-liquid separator 24 → the heating fixed throttle 25 → the outdoor heat exchanger 16 → the heating passage 22b → the accumulator 21 → the suction port 11a of the compressor 11 A gas injection cycle in which the refrigerant is circulated in order is configured.

  More specifically, in the 4) heating mode, the heat exchanger functioning as an evaporator (specifically, the outdoor heat) is used for (1) cooling mode, (5) cooling + cooling mode, and (11) cooling mode. A two-stage depressurization type gas injection cycle is configured in which the refrigerant flowing into the exchanger 16) is depressurized by two depressurizing units of the heating expansion valve 14a and the heating fixed throttle 25.

  When the control device 60 operates the compressor 11, the state of the refrigerant changes as shown in the Mollier diagram of FIG. That is, the high-pressure refrigerant (point a29 in FIG. 29) discharged from the discharge port 11c of the compressor 11 radiates heat in the water-refrigerant heat exchanger 12 (point a29 → point b29 in FIG. 29). Thereby, the high-temperature side heat medium is heated.

  The refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 is decompressed by the heating expansion valve 14a until it becomes an intermediate-pressure refrigerant (point b29 → point be29 in FIG. 29). At this time, the degree of throttle opening of the heating expansion valve 14a is determined by the degree of supercooling of the refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 (see FIG. 29), similarly to the (4) heating mode of the first embodiment. (point b29) is adjusted so as to approach the target supercooling degree SCO2.

  The intermediate-pressure refrigerant decompressed by the heating expansion valve 14a is separated into a gas and a liquid by the heating gas-liquid separator 24.

  The gas-phase refrigerant (point bg29 in FIG. 29) separated by the heating gas-liquid separator 24 is suctioned to the intermediate pressure of the compressor 11 through the gas-phase passage 22d because the gas-phase passage opening / closing valve 15d is open. Inhaled into the mouth 11b. The refrigerant sucked from the intermediate pressure suction port 11b merges with the refrigerant (point i29 in FIG. 29) boosted by the low-stage compression mechanism of the compressor 11 (point j29 in FIG. 9), and It is sucked into the high-stage compression mechanism.

  The liquid-phase refrigerant (point b129 in FIG. 29) separated by the heating gas-liquid separator 24 is depressurized by the heating fixed throttle 25 to a low-pressure refrigerant because the bypass passage opening / closing valve 15e is closed. (Point bl29 → point ble29 in FIG. 29), and flows into the outdoor heat exchanger 16. The refrigerant flowing into the outdoor heat exchanger 16 absorbs heat from outside air and evaporates (point ble29 → point n29 in FIG. 29).

  The refrigerant flowing out of the outdoor heat exchanger 16 flows into the accumulator 21 via the heating passage 22b because the heating on-off valve 15b is open. In the accumulator 21, gas-liquid of the refrigerant is separated. The gas-phase refrigerant separated by the accumulator 21 is sucked through the suction port 11a of the compressor 11, and is pressurized by the low-stage compression mechanism (point n29 → point i29 in FIG. 29).

  According to this, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. Therefore, in the vehicle air conditioner 1 in the heating mode, the air in the vehicle compartment can be heated by blowing the blast air heated by the heater core 42 into the vehicle compartment. Other operations of the refrigeration cycle device 10 are the same as those of the first embodiment. Therefore, in the refrigeration cycle device 10 of the present embodiment, the same effect as that of the first embodiment can be obtained.

  Further, in the refrigeration cycle apparatus 10 of the present embodiment, since the gas injection cycle is also configured in the heating mode, the enthalpy of the refrigerant on the inlet side of the outdoor heat exchanger 16 is subtracted from the enthalpy of the refrigerant on the outlet side of the outdoor heat exchanger 16. Enthalpy difference can be enlarged. As a result, in the heating mode, the heating capability of the blown air can be improved as compared with a normal vapor compression refrigeration cycle.

  In addition, since the heating mode is an operation mode executed when the outside air temperature decreases, the pressure difference between the refrigerant condensation pressure in the water-refrigerant heat exchanger 12 and the refrigerant evaporation pressure in the outdoor heat exchanger 16 ( In other words, the high-low pressure difference of the cycle) tends to increase. Therefore, by configuring the gas injection cycle in the heating mode, the compression efficiency of the compressor 11 can be improved, and a high COP improvement effect can be obtained.

(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. In addition, the means disclosed in each of the above embodiments may be appropriately combined within a practicable range. For example, instead of the intermediate pressure expansion valve 14d of the refrigeration cycle device 10 described in the second and fourth embodiments, the temperature type expansion valve 141 and the intermediate pressure on-off valve 15c described in the third embodiment may be employed. .

  (A) In the above-described embodiment, an example in which the refrigerant circuit constituting the gas injection cycle is switched in (1) cooling mode, (5) cooling + cooling mode, and (11) cooling mode has been described. However, the present invention is not limited to this. .

  That is, at least in the operation mode in which the heat load of the refrigeration cycle device 10 can be the highest ((5) cooling + cooling mode in the above-described embodiment), the refrigerant circuit may be switched to the refrigerant circuit constituting the gas injection cycle. Therefore, in the (1) cooling mode and the (11) cooling mode, the intermediate pressure expansion valve 14d may be fully closed to configure a normal vapor compression refrigeration cycle.

  Further, in the above-described embodiment, the refrigeration cycle device 10 that can be switched to a plurality of operation modes has been described, but the switching of the operation mode of the refrigeration cycle device 10 is not limited to this. In other words, if the blast air and the battery 80 can be sufficiently and appropriately cooled without exhibiting excessive cooling capacity and heating capacity in any of the operation modes, all the operation modes described in the above-described embodiment will be described. It is not indispensable to be able to switch to.

  Further, the detailed control of each operation mode is not limited to the one disclosed in the above embodiment. For example, the blowing mode described in step S260 may be a stop mode for stopping not only the compressor 11 but also the blower 32.

  (B) The components of the refrigeration cycle device are not limited to those disclosed in the above embodiment.

  For example, in the above-described embodiment, an example has been described in which a two-stage booster type electric compressor in which two compression mechanisms are housed in one housing is used as the compressor 11, but the type of the compressor is not limited to this. Not done. If it is possible to flow the intermediate-pressure cycle refrigerant from the intermediate-pressure port 11b and to join the cycle refrigerant in the process of being compressed from low pressure to high pressure, one fixed-capacity type compression is provided inside the housing. An electric compressor configured to house a mechanism and an electric motor that rotationally drives one compression mechanism may be used.

  In addition, two compressors are connected in series, the suction port of the low-stage compressor arranged on the low stage side is set as the suction port 11a, and the high-stage compressor of the high stage The discharge port is defined as a discharge port 11c. Further, an intermediate-pressure suction port b is provided at a connection portion connecting the discharge port of the low-stage compressor and the suction port of the high-stage compressor. As described above, one two-stage booster-type compressor may be configured by using two compressors, the low-stage compressor and the high-stage compressor.

  A plurality of cycle components may be integrated so as to exert the above-described effects. For example, a four-way joint structure in which the second three-way joint 13b and the fifth three-way joint 13e are integrated may be employed. Further, as the cooling expansion valve 14b and the cooling expansion valve 14c, those in which an electric expansion valve having no fully closed function and an on-off valve may be directly connected may be employed.

  In the above-described embodiment, an example in which R1234yf is used 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.

  (C) The configuration of the heating unit is not limited to the one disclosed in the above embodiment. For example, a three-way valve 53 and a high-temperature-side radiator similar to the three-way valve 53 and the low-temperature-side radiator 54 of the low-temperature-side heat medium circuit 50 are added to the high-temperature-side heat medium circuit 40 described in the first embodiment, and excess heat is added. May be radiated to the outside air. Further, in a vehicle including an internal combustion engine (engine) such as a hybrid vehicle, engine cooling water may be circulated through the high-temperature side heat medium circuit 40.

  Alternatively, the high-temperature side heat medium circuit 40 may be eliminated, and an indoor condenser may be employed as the heating unit. The indoor condenser is a heating heat exchanger that exchanges heat between the high-temperature and high-pressure refrigerant discharged from the compressor 11 and the blast air to condense the refrigerant and heat the blast air.

  (D) The configuration of the cooling unit is not limited to the configuration disclosed in the above embodiment. For example, as the cooling unit, a thermosiphon that makes the chiller 19 of the low-temperature side heating medium circuit 50 described in the first embodiment a condensing unit and makes the cooling heat exchanging unit 52 function as an evaporating unit may be employed. According to this, the low-temperature side heat medium pump 51 can be eliminated.

  The thermosiphon has an evaporating section for evaporating the refrigerant and a condensing section for condensing the refrigerant, and is configured by connecting the evaporating section and the condensing section in a closed loop (that is, in an annular shape). Then, a temperature difference between the temperature of the refrigerant in the evaporating section and the temperature of the refrigerant in the condensing section causes a difference in specific gravity of the refrigerant in the circuit, and the refrigerant naturally circulates by the action of gravity to transport heat with the refrigerant. Circuit.

  For example, a battery evaporator for evaporating the refrigerant by exchanging heat between the refrigerant depressurized by the cooling expansion valve 14c and the cooling air, and a battery evaporating the cooling air toward the battery evaporator. An air-cooled cooling unit that includes a blower and cools the battery 80 by blowing cooling air cooled by the battery evaporator may be employed.

  Further, in the above-described embodiment, an example has been described in which the object to be cooled by the cooling unit is the battery 80, but the object to be cooled is not limited to this. An inverter that converts direct current and alternating current, a charger that charges the battery 80 with electric power, a motor generator that outputs driving power for traveling by being supplied with electric power, and generates regenerative electric power during deceleration and the like It may be an electric device that generates heat during operation as described above.

  (E) In the above embodiments, the refrigeration cycle device 10 according to the present invention is applied to the vehicle air conditioner 1, but the application of the refrigeration cycle device 10 is not limited to this. For example, the present invention may be applied to an air conditioner with a server cooling function that performs indoor air conditioning while appropriately adjusting the temperature of a computer server.

  (F) In each of the above embodiments, even when the operation mode does not heat the blown air, such as (1) cooling mode, (5) cooling and cooling mode, and (11) cooling mode, discharge from the compressor 11 is performed. Although the example in which the performed refrigerant is caused to flow into the heating unit (specifically, the water-refrigerant heat exchanger 12) has been described, the refrigerant circuit in each operation mode is not limited thereto.

  For example, as shown in FIG. 30, a heating unit bypass passage 22g for guiding the refrigerant discharged from the compressor 11 to the inlet side of the heating expansion valve 14a, and a water-refrigerant heat exchanger for discharging the refrigerant discharged from the compressor 11 A heating section switching valve 26 for switching between a refrigerant circuit leading to the heating section 12 (that is, the heating section) and a refrigerant circuit flowing into the heating section bypass passage 22g may be provided.

  Then, by comparing the required blowing temperature with the evaporator temperature Tefin, if it is not necessary to heat the blown air, the heating unit switching valve 26 causes the refrigerant discharged from the compressor 11 to flow into the heating unit. Alternatively, the refrigerant circuit may be switched so as to flow into the heating unit bypass passage 22g.

  The target outlet temperature TAO is compared with the blast air temperature TAV detected by the conditioned air temperature sensor 69, and when it is not necessary to heat the blast air, the heating unit switching valve 26 causes the compressor 11 to discharge the air from the compressor 11. The refrigerant circuit may be switched so that the supplied refrigerant flows into the heating unit bypass passage 22g.

  In the operation mode in which it is not necessary to heat the blast air, the heating unit switching valve 26 switches to the refrigerant circuit so that the refrigerant discharged from the compressor 11 flows into the heating unit bypass passage 22g, and heats the blast air. In the necessary operation mode, the heating section switching valve 26 may switch to the refrigerant circuit so that the refrigerant discharged from the compressor 11 flows into the heating section.

11 compressor, 11a suction port, 11b intermediate pressure suction port, 11c discharge port,
13g ... upstream branch section, 13e ... downstream branch section, 13f ... merging section,
14a: heating expansion valve, 14b: cooling expansion valve, 14c: cooling expansion valve,
14d: intermediate pressure expansion valve, 141: temperature type expansion valve (intermediate pressure expansion valve),
15a: On-off valve for dehumidification, 15b: On-off valve for heating (refrigerant circuit switching unit),
16 ... outdoor heat exchanger, 18 ... indoor evaporator,
22a: bypass passage, 22b: heating passage, 22c: intermediate pressure passage,
23 ... internal heat exchanger, 23a ... intermediate temperature side passage, 23b ... high temperature side passage,
40: High-temperature side heat medium circuit (heating unit),
50: low-temperature side heat medium circuit (cooling unit), 52a: cooling heat exchange unit (cooling unit)
80… Battery (object to be cooled)

Claims (6)

An intermediate-pressure suction port that compresses the low-pressure refrigerant sucked from the suction port (11a) to high-pressure refrigerant and discharges it from the discharge port (11c), and allows the intermediate-pressure refrigerant in the cycle to flow in and joins the refrigerant in the compression process. A compressor (11) having (11b);
A heating unit (40) for heating the blast air blown to the air-conditioned space, using the high-pressure refrigerant discharged from the compressor as a heat source;
A heating expansion valve (14a) for reducing the pressure of the refrigerant flowing out of the heating unit;
An outdoor heat exchanger (16) for exchanging heat between the refrigerant flowing out of the heating expansion valve and the outside air;
An upstream branch portion (13g) for branching a flow of the refrigerant flowing out of the outdoor heat exchanger;
An intermediate pressure passageway (22c) for guiding one refrigerant branched at the upstream branch portion to the intermediate pressure suction port side;
An intermediate pressure expansion valve (14d, 141) for reducing the pressure of the refrigerant flowing through the intermediate pressure passage to the intermediate pressure refrigerant,
An intermediate-temperature side passageway (23a) through which the intermediate-pressure refrigerant depressurized by the intermediate-pressure expansion valve flows and a high-temperature side passageway (23b) through which the other refrigerant branched at the upstream branch portion flows. An internal heat exchanger (23) for exchanging heat between the intermediate-pressure refrigerant flowing through the intermediate-temperature-side passage and the refrigerant flowing through the high-temperature-side passage;
A downstream branch portion (13e) for branching the flow of the refrigerant flowing out of the high temperature side passage;
A cooling expansion valve (14b) for reducing the pressure of one of the refrigerants branched at the downstream branch portion until the refrigerant becomes the low-pressure refrigerant;
An indoor evaporator (18) for evaporating the refrigerant flowing out of the cooling expansion valve to cool the blown air;
A cooling expansion valve (14c) for reducing the pressure of the other refrigerant branched at the downstream branch portion until the refrigerant becomes the low-pressure refrigerant;
Cooling units (50, 52a) for evaporating the refrigerant flowing out of the cooling expansion valve to cool the object to be cooled (80);
A merging section (13f) for merging a flow of the refrigerant flowing out of the indoor evaporator with a flow of the refrigerant flowing out of the cooling section and flowing out to a suction port side of the compressor;
A heating passageway (22b) for guiding the refrigerant flowing out of the outdoor heat exchanger to the suction port side of the compressor;
A refrigerant circuit switching unit (15a to 15e) for switching a refrigerant circuit,
The refrigerant circuit switching unit,
In a heating mode in which the blast air is heated by the heating section, the discharge port of the compressor → the heating section → the heating expansion valve → the outdoor heat exchanger → the heating passage → the suction of the compressor. Switch to a refrigerant circuit that circulates refrigerant in the order of mouth,
In a cooling + cooling mode in which the blown air is cooled by the indoor evaporator and the object to be cooled is cooled by the cooling unit, the discharge port of the compressor → the expansion valve for heating → the outdoor heat exchange The refrigerant is circulated in the order of a vessel → the upstream branch section → the intermediate pressure expansion valve → the intermediate temperature side passage → the intermediate pressure suction port of the compressor, and further the upstream branch section → the high temperature side passage → the The downstream branch section → the cooling expansion valve → the indoor evaporator → the junction section → the compressor is circulated in the order of the refrigerant, and the upstream branch section → the high temperature side passage → the downstream branch section. A refrigeration cycle apparatus that switches to a refrigerant circuit that circulates refrigerant in the order of the cooling expansion valve, the cooling unit, the junction, and the suction port of the compressor. An intermediate-pressure suction port that compresses the low-pressure refrigerant sucked from the suction port (11a) to high-pressure refrigerant and discharges it from the discharge port (11c), and allows the intermediate-pressure refrigerant in the cycle to flow in and joins the refrigerant in the compression process. A compressor (11) having (11b);
An outdoor heat exchanger (16) for exchanging heat between the refrigerant discharged from the compressor and outside air;
An upstream branch portion (13g) for branching a flow of the refrigerant flowing out of the outdoor heat exchanger;
An intermediate pressure passageway (22c) for guiding one refrigerant branched at the upstream branch portion to the intermediate pressure suction port side;
An intermediate pressure expansion valve (14d, 141) for reducing the pressure of the refrigerant flowing through the intermediate pressure passage to the intermediate pressure refrigerant,
An intermediate-temperature side passageway (23a) through which the intermediate-pressure refrigerant depressurized by the intermediate-pressure expansion valve flows and a high-temperature side passageway (23b) through which the other refrigerant branched at the upstream branch portion flows. An internal heat exchanger (23) for exchanging heat between the intermediate-pressure refrigerant flowing through the intermediate-temperature-side passage and the refrigerant flowing through the high-temperature-side passage;
A downstream branch portion (13e) for branching the flow of the refrigerant flowing out of the high temperature side passage;
A cooling expansion valve (14b) for reducing the pressure of one of the refrigerants branched at the downstream branch portion until the refrigerant becomes the low-pressure refrigerant;
An indoor evaporator (18) for evaporating the refrigerant flowing out of the cooling expansion valve to cool the blown air;
A cooling expansion valve (14c) for reducing the pressure of the other refrigerant branched at the downstream branch portion until the refrigerant becomes the low-pressure refrigerant;
A cooling unit (50, 52a) for evaporating the refrigerant flowing out of the cooling expansion valve to cool an object to be cooled;
A merging section (13f) for merging a flow of the refrigerant flowing out of the indoor evaporator with a flow of the refrigerant flowing out of the cooling section and flowing out to a suction port side of the compressor;
A refrigerant circuit switching unit (15a to 15e) for switching a refrigerant circuit;
An expansion valve controller (60b) for controlling at least one of the cooling expansion valve (14b) and the cooling expansion valve (14c).
The cooling circuit switching unit cools the blown air by the indoor evaporator and cools the object to be cooled by the cooling unit. The refrigerant circulates in the order of expansion valve → the outdoor heat exchanger → the upstream branch section → the intermediate pressure expansion valve → the intermediate temperature side passage → the intermediate pressure suction port of the compressor, and further, the upstream branch section → the high temperature side passage → the downstream side branch section → the cooling expansion valve → the indoor evaporator → the junction section → the refrigerant circulates in the order of the compressor, and the upstream side branch section → the high temperature side It is to switch to a refrigerant circuit that circulates refrigerant in the order of passage → the downstream branch section → the cooling expansion valve → the cooling section → the junction section → the suction port of the compressor,
The expansion valve control unit is configured to control the cooling expansion valve (14b) and the cooling expansion valve so that in the cooling + cooling mode, the refrigerant flowing into the downstream branch becomes a high-pressure refrigerant having a degree of supercooling. (14c) A refrigeration cycle apparatus for controlling at least one of the operations. A heating unit (40) for heating the blast air blown to the air-conditioned space, using the high-pressure refrigerant discharged from the compressor as a heat source;
A heating expansion valve (14a) for reducing the pressure of the refrigerant flowing out of the heating unit and flowing the refrigerant to the refrigerant inlet side of the outdoor heat exchanger;
A heating passageway (22b) for guiding the refrigerant flowing out of the outdoor heat exchanger to the suction port side of the compressor,
In the heating mode in which the blast air is heated by the heating unit, the refrigerant circuit switching unit is configured such that the discharge port of the compressor → the heating unit → the heating expansion valve → the outdoor heat exchanger → the heating passage. The refrigeration cycle apparatus according to claim 2, wherein the refrigerant circuit is switched to a refrigerant circuit that circulates refrigerant in the order of the suction port of the compressor.   4. The refrigeration cycle apparatus according to claim 1, wherein an inlet portion of the heating passage is connected to a refrigerant flow upstream side of the upstream branch portion. 5. In the cooling mode in which the blast air is cooled by the indoor evaporator, the refrigerant circuit switching unit is configured to be the discharge port of the compressor → the expansion valve for heating → the outdoor heat exchanger → the upstream branch unit → the The refrigerant is circulated in the order of an intermediate pressure expansion valve → the intermediate temperature side passage → the intermediate pressure suction port of the compressor, and further, the upstream side branch → the high temperature side passage → the cooling expansion valve → the indoor evaporator → to switch the refrigerant circuit to circulate the refrigerant in the order of the suction port of the compressor,
The refrigeration cycle apparatus according to any one of claims 1 to 4, wherein the heating expansion valve is fully opened in the cooling mode. In the cooling mode in which the object to be cooled is cooled by the cooling unit, the refrigerant circuit switching unit is configured to discharge the outlet of the compressor → the expansion valve for heating → the outdoor heat exchanger → the upstream branch unit → the cooling unit. The refrigerant is circulated in the order of an intermediate pressure expansion valve → the intermediate temperature side passage → the intermediate pressure suction port of the compressor, and further, the upstream branch section → the high temperature side passage → the cooling expansion valve → the cooling section → Switching to a refrigerant circuit that circulates refrigerant in the order of the suction port of the compressor,
The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the heating expansion valve is fully opened in the cooling mode.

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