JP2021124235A - Refrigeration cycle device - Google Patents

Abstract

To provide a refrigeration cycle device capable of appropriately adjusting a refrigerant evaporation temperature of one evaporation unit without being affected by a refrigerant evaporation temperature of another evaporation unit.SOLUTION: A refrigeration cycle device comprises an integrated evaporation pressure adjustment valve 20 that is arranged on the downstream side of an outdoor heat exchanger 16, an indoor evaporator 18 and a the chiller 19, which are a plurality of evaporation units, and that adjusts refrigerant evaporation pressure in the plurality of evaporation units. When one of the plurality of evaporation units is defined as a first evaporation unit, and another is defined as a second evaporation unit, the evaporation pressure adjustment valve 20 is configured so that the refrigerant evaporation pressure in the first evaporation unit can be adjusted to either a value higher or lower than the refrigerant evaporation pressure in the second evaporation unit.SELECTED DRAWING: Figure 1

Description

The present invention relates to a refrigeration cycle apparatus including a plurality of evaporation units connected in parallel with each other with respect to a refrigerant flow.

Conventionally, Patent Document 1 discloses a refrigeration cycle device applied to a vehicle air conditioner. The refrigeration cycle apparatus of Patent Document 1 includes a plurality of heat exchangers that function as an evaporation unit that evaporates the refrigerant, and is configured so that the refrigerant circuit can be switched. Then, in the dehumidifying / heating mode in which the dehumidifying / heating of the vehicle interior is performed, the outdoor heat exchanger and the indoor evaporator, which are heat exchangers functioning as evaporators, are switched to a refrigerant circuit connected in parallel with the refrigerant flow.

In the outdoor heat exchanger in the dehumidifying and heating mode, the refrigerant exchanges heat with the outside air to evaporate. In the indoor evaporator in the dehumidifying / heating mode, the refrigerant exchanges heat with the blown air blown into the vehicle interior to evaporate. Further, the refrigeration cycle device of Patent Document 1 includes an evaporation pressure adjusting valve (constant pressure valve in Patent Document 1). The evaporation pressure adjusting valve is a mechanical variable throttle device that is arranged on the downstream side of the refrigerant flow of the indoor evaporator and maintains the refrigerant evaporation pressure in the indoor evaporator at a predetermined reference value or higher.

As a result, in the refrigeration cycle apparatus of Patent Document 1, the refrigerant evaporation temperature in the outdoor heat exchanger is maintained at a temperature higher than the temperature at which frost formation in the indoor evaporator can be suppressed in the dehumidifying / heating mode. Is lower than the outside temperature. That is, in the refrigeration cycle apparatus of Patent Document 1, the refrigerant is evaporated at different temperatures in the outdoor heat exchanger and the indoor evaporator by utilizing the depressurizing action of the evaporation pressure adjusting valve in the dehumidifying and heating mode.

Japanese Unexamined Patent Publication No. 2012-225637

By the way, in recent years, with the spread of electric vehicles and the like, there is an increasing need to cool new objects to be cooled such as batteries and other in-vehicle devices by using a refrigeration cycle device applied to an air conditioner for vehicles. Therefore, an evaporation unit for cooling a new cooling object is added to the refrigeration cycle apparatus of Patent Document 1, and the refrigerant evaporation temperature in each evaporation unit is adjusted so that each cooling object can be appropriately cooled. The means to do this is conceivable.

However, the amount of heat generated by a cooling object such as a battery changes depending on the operating state. Therefore, the appropriate refrigerant evaporation temperature in the evaporation section for cooling the object to be cooled such as a battery also changes depending on the operating state of the object to be cooled. For example, the appropriate refrigerant evaporation temperature in the evaporator for cooling the battery changes to a value higher or lower than the refrigerant evaporation temperature in the indoor evaporator depending on the operating state of the battery.

However, in the refrigeration cycle apparatus of Patent Document 1, the refrigerant evaporation temperature in the two evaporation portions connected in parallel is set to different temperatures by utilizing the depressurizing action of the mechanical evaporation pressure regulating valve. In such a configuration, the refrigerant evaporation temperature in one evaporation section (for example, the indoor evaporator in Patent Document 1) is set from the refrigerant evaporation temperature in the other evaporation section (for example, the outdoor heat exchanger in Patent Document 1). Cannot be lowered.

On the other hand, in order to appropriately adjust the refrigerant evaporation temperature in all the evaporation parts, individual electric evaporation pressure adjustment valves are arranged on the downstream side of the refrigerant flow in each evaporation part, and each evaporation pressure adjustment valve is provided. A means for appropriately adjusting the throttle opening of the above can be considered. However, if individual evaporation pressure adjusting valves are arranged on the downstream side of the refrigerant flow in each evaporation section, the circuit configuration of the refrigeration cycle apparatus as a whole becomes complicated and large.

In view of the above points, the present invention is affected by the refrigerant evaporation temperature in one evaporative section and the refrigerant evaporation temperature in another evaporative section among a plurality of evaporative sections connected in parallel with each other with respect to the refrigerant flow. It is an object of the present invention to provide a refrigerating cycle apparatus that can be appropriately adjusted without any problem.

Further, the present invention provides a refrigerating cycle apparatus capable of appropriately adjusting the refrigerant evaporation temperature in a plurality of evaporation units connected in parallel with each other with respect to the refrigerant flow without incurring the complexity and size of the circuit configuration. Another purpose is to do.

In order to achieve the above object, the refrigeration cycle apparatus according to claim 1 has a plurality of evaporation units (16, 18, 19), an evaporation pressure adjusting unit (20, 210), and a refrigerant circuit switching unit (15a, 15b). ) And. The plurality of evaporators evaporate the refrigerant. The evaporation pressure adjusting unit is arranged on the downstream side of the refrigerant flow of the plurality of evaporation units, and adjusts the refrigerant evaporation pressure in the plurality of evaporation units. The refrigerant circuit switching unit switches the refrigerant circuit.

There are at least three or more evaporation sections. Of the plurality of evaporation units, any one is defined as the first evaporation unit, and the other one is defined as the second evaporation unit.

The refrigerant circuit switching unit switches to a refrigerant circuit that connects the first evaporation unit and the second evaporation unit in parallel with the refrigerant flow when the refrigerant is evaporated by both the first evaporation unit and the second evaporation unit. .. Further, the evaporation pressure adjusting unit is configured so that the refrigerant evaporation pressure in the first evaporation unit can be adjusted to a value higher or lower than the refrigerant evaporation pressure in the second evaporation unit.

According to this, the refrigerant circuit switching section (15a, 15b) connects two evaporation sections of the three or more plurality of evaporation sections (16, 18, 19) in parallel with each other with respect to the refrigerant flow. be able to. Then, the evaporation pressure adjusting unit (20, 210) can adjust the refrigerant evaporation pressure in the first evaporation unit to a value higher or lower than the refrigerant evaporation pressure in the second evaporation unit.

Therefore, among the plurality of evaporation parts (16, 18, 19) connected in parallel to the refrigerant flow, the refrigerant evaporation temperature in one evaporation part is affected by the refrigerant evaporation temperature in another evaporation part. It is possible to provide a refrigerating cycle apparatus that can be appropriately adjusted without any need.

The refrigeration cycle apparatus according to claim 6 includes a plurality of evaporation units (16, 18, 19) and an evaporation pressure adjusting unit (20, 210). The plurality of evaporators evaporate the refrigerant. The evaporation pressure adjusting unit is arranged on the downstream side of the refrigerant flow of the plurality of evaporation units, and adjusts the refrigerant evaporation pressure in the plurality of evaporation units.

The plurality of evaporation units are connected in parallel with each other with respect to the refrigerant flow. Of the plurality of evaporation units, any one is defined as the first evaporation unit, and the other one is defined as the second evaporation unit.

The evaporation pressure adjusting unit is configured so that the refrigerant evaporation pressure in the first evaporation unit can be adjusted to a value higher or lower than the refrigerant evaporation pressure in the second evaporation unit.

The evaporation pressure adjusting unit has a single opening degree adjusting unit (202, 212) and a driving unit (203, 213). The opening degree adjusting unit adjusts the passage cross-sectional area of a plurality of refrigerant passages through which the respective refrigerants flowing out from the plurality of evaporation units flow. The drive unit displaces the opening degree adjusting unit.

According to this, the evaporation pressure adjusting unit (20, 210) sets the refrigerant evaporation pressure in the first evaporation unit among the plurality of evaporation units (16, 18, 19) connected in parallel to each other in the second evaporation unit. It can be adjusted to a value higher or lower than the refrigerant evaporation pressure in. Further, the evaporation pressure adjusting unit (20, 210) has a single opening degree adjusting unit (202, 212) and a driving unit (203, 213).

Therefore, it is possible to provide a refrigerating cycle apparatus capable of appropriately adjusting the refrigerant evaporation temperature in a plurality of evaporation units (16, 18, 19) connected in parallel with each other without incurring a complicated circuit configuration or an increase in size. Can be done.

In addition, the reference numerals in parentheses of each means described in this column and the scope of claims are an example showing the correspondence with the specific means described in the embodiment described later.

It is a schematic overall block diagram of the refrigeration cycle apparatus of 1st Embodiment. It is a front view of the integrated evaporative pressure control valve of 1st Embodiment. FIG. 3 is a view taken along the line III of FIG. FIG. 2 is a sectional view taken along line IV-IV of FIG. It is a block diagram which shows the electric control part of the refrigeration cycle apparatus of 1st Embodiment. It is a front view of the integrated evaporative pressure control valve of the 2nd Embodiment. It is a VII arrow view of FIG. FIG. 6 is a cross-sectional view taken along the line VIII-VIII of FIG. It is a partially disassembled perspective view of the integrated evaporative pressure control valve of the second embodiment. It is explanatory drawing for demonstrating the shape of each communication hole of the valve body part of 2nd Embodiment. It is a schematic overall block diagram of the refrigeration cycle apparatus of 3rd Embodiment. It is a schematic overall block diagram of the refrigeration cycle apparatus of 4th Embodiment. It is a schematic overall block diagram of the refrigeration cycle apparatus of another embodiment.

Hereinafter, a plurality of embodiments for carrying out the present invention will be described with reference to the drawings. In each embodiment, the same reference numerals may be given to the parts corresponding to the items described in the preceding embodiments, and duplicate description may be omitted. When only a part of the configuration is described in each embodiment, the other embodiments described above can be applied to the other parts of the configuration. Not only the combination of the parts that clearly indicate that the combination is possible in each embodiment, but also the partial combination of the embodiments even if the combination is not specified if there is no particular problem in the combination. Is also possible.

(First Embodiment)
The first embodiment of the present invention will be described with reference to FIGS. 1 to 5. 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 not only air-conditions the interior of the vehicle, which is the space to be air-conditioned, but also has a function of cooling the battery 80, which is an in-vehicle device. That is, the vehicle air conditioner 1 is an air conditioner with an in-vehicle device cooling function.

The battery 80 stores electric power supplied to an in-vehicle device such as an electric motor. The battery 80 is a secondary battery (in this embodiment, a lithium ion battery). The battery 80 is an assembled battery formed by stacking a plurality of battery cells and electrically connecting these battery cells in series or in parallel.

This type of battery generates heat during operation (ie, during charging and discharging). The output of a battery tends to decrease at low temperatures, and deterioration tends to progress at high temperatures. Therefore, the temperature of the battery needs to be maintained within an appropriate temperature range (in this embodiment, 15 ° C. or higher and 55 ° C. or lower) in which the charge / discharge capacity of the battery can be fully utilized. ..

Therefore, the vehicle air conditioner 1 cools the battery 80 by using the cold heat generated by the refrigeration cycle device 10. As shown in the overall configuration diagram of FIG. 1, the vehicle air conditioner 1 includes a refrigeration cycle device 10, an indoor air conditioner unit 30, a high temperature side heat medium circuit 40, a low temperature side heat medium circuit 50, and the like.

The refrigeration cycle device 10 cools the blown air blown into the vehicle interior and heats 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 device 10 cools the low temperature side heat medium circulating in the low temperature side heat medium circuit 50 in order to cool the battery 80. The refrigerating cycle device 10 can switch the refrigerant circuit according to various operation modes described later.

In the refrigeration cycle apparatus 10, an HFO-based refrigerant (specifically, R1234yf) is used as the refrigerant. The refrigeration cycle device 10 constitutes a subcritical refrigeration cycle in which the refrigerant pressure on the high pressure side does not exceed the critical pressure of the refrigerant. Refrigerant oil (specifically, PAG oil) for lubricating the compressor 11 of the refrigeration cycle device 10 is mixed in the refrigerant. A part of the refrigerating machine oil circulates in the refrigerating cycle device 10 together with the refrigerant.

The compressor 11 sucks in the refrigerant, compresses it, and discharges it in the refrigeration cycle device 10. The compressor 11 is arranged in the drive unit room on the front side of the vehicle interior. The drive device room forms a space in which at least a part of a drive device (for example, a drive electric motor) for outputting a driving force for traveling is arranged.

The compressor 11 is an electric compressor that rotationally drives a fixed-capacity compression mechanism having a fixed discharge capacity by an electric motor. The number of revolutions (that is, the refrigerant discharge capacity) of the compressor 11 is controlled by a control signal output from the control device 60 described later.

The inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the discharge port of the compressor 11. The water-refrigerant heat exchanger 12 has a refrigerant passage for circulating the high-pressure refrigerant discharged from the compressor 11 and a water passage for circulating the high-temperature side heat medium circulating in the high-temperature side heat medium circuit 40. The water-refrigerator heat exchanger 12 is a heat exchanger for heating that heats the high temperature side heat medium by exchanging heat between the high pressure refrigerant flowing through the refrigerant passage and the high temperature side heat medium flowing through the water passage.

The inlet side of the first three-way joint 13a having three inflow outlets 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, one formed by providing a plurality of refrigerant passages in a metal block or a resin block, and the like can be adopted.

Further, the refrigeration cycle device 10 includes a second three-way joint 13b to a fourth three-way joint 13d, as will be described later. The basic configuration of the second three-way joint 13b to the fourth three-way joint 13d is the same as that of the first three-way joint 13a.

In the first three-way joint 13a to the fourth three-way joint 13d, when one of the three inflow ports is used as an inflow port and two are used as an outflow port, a branch that branches the flow of the refrigerant flowing in from one inflow port. Become a department. Further, when two of the three inflow ports are used as the inflow port and one is used as the outflow port, it becomes a merging portion where the flows of the refrigerant flowing in from the two inflow ports are merged.

The inlet side of the heating expansion valve 14a is connected to one outlet of the first three-way joint 13a. One inflow port side of the second three-way joint 13b is connected to the other outflow port of the first three-way joint 13a via a bypass passage 22a. A high-pressure on-off valve 15a is arranged in the bypass passage 22a.

The high-pressure on-off valve 15a is a solenoid valve that opens and closes a refrigerant passage connecting the other outlet side of the first three-way joint 13a and one inflow port side of the second three-way joint 13b. The opening / closing operation of the high-voltage on-off valve 15a is controlled by the control voltage output from the control device 60.

Further, the refrigeration cycle device 10 includes a low pressure on-off valve 15b as described later. The basic configuration of the low-pressure on-off valve 15b is the same as that of the high-pressure on-off valve 15a. The high-pressure on-off valve 15a and the low-pressure on-off valve 15b can switch the refrigerant circuit in each operation mode by opening and closing the refrigerant passage. Therefore, the high-pressure on-off valve 15a and the low-pressure on-off valve 15b are refrigerant circuit switching units for switching the refrigerant circuit.

The heating expansion valve 14a reduces the pressure of the high-pressure refrigerant flowing out from the refrigerant passage of the water-refrigerant heat exchanger 12 and adjusts the flow rate (mass flow rate) of the refrigerant flowing out to the downstream side in the outside air heating mode described later. It is a decompression unit for heating.

The heating expansion valve 14a is an electric variable throttle device including a valve body configured to change the throttle opening degree and an electric actuator for changing the throttle opening degree. The operation of the heating expansion valve 14a is controlled by a control signal (control pulse) output from the control device 60.

Further, the refrigeration cycle device 10 includes a cooling expansion valve 14b and a cooling expansion valve 14c, as will be described later. The basic configuration of the cooling expansion valve 14b and the cooling expansion valve 14c is the same as that of the heating expansion valve 14a.

The expansion valve 14a for heating, the expansion valve 14b for cooling, and the expansion valve 14c for cooling have a fully open function that functions as a mere refrigerant passage without exerting a flow rate adjusting action and a refrigerant depressurizing action by fully opening the valve opening. Have. Further, the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c have a fully closing function of closing the refrigerant passage by fully closing the valve opening degree.

Therefore, the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c also have a function as a blocking unit for blocking the inflow of the refrigerant into the evaporation unit connected to the downstream side of each. Of course, the heating expansion valve 14a or the like may be formed by combining a variable throttle mechanism having no fully closed function and an on-off valve. In this case, the on-off valve serves as a shutoff.

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 from 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 running, the running wind can be applied to the outdoor heat exchanger 16.

In the operation mode in which the temperature of the refrigerant flowing inside is higher than the outside air temperature, as in the cooling mode described later, the outdoor heat exchanger 16 dissipates the heat of the refrigerant to the outside air to condense the refrigerant. Become a department. Further, the outdoor heat exchanger 16 absorbs the heat of the outside air into the refrigerant in the operation mode in which the temperature of the refrigerant flowing inside is lower than the outside air temperature, as in the outdoor air heating mode described later, to supply the refrigerant. It becomes an evaporative part to evaporate.

The inflow port side of the third three-way joint 13c is connected to the refrigerant outlet of the outdoor heat exchanger 16. The first inlet 201a side of the integrated evaporation pressure regulating valve 20 is connected to one outlet of the third three-way joint 13c via a heating passage 22b. The detailed configuration of the integrated evaporative pressure regulating valve 20 will be described later. A low-pressure on-off valve 15b that opens and closes the refrigerant passage is arranged in the heating passage 22b.

The other inlet side of the second three-way joint 13b is connected to the other outlet of the third three-way joint 13c. A check valve 17 is arranged in the refrigerant passage connecting the other outlet side of the third three-way joint 13c and the other inlet side of the second three-way joint 13b. The check valve 17 allows the refrigerant to flow from the third three-way joint 13c side to the second three-way joint 13b side, and prohibits the refrigerant from flowing from the second three-way joint 13b side to the third three-way joint 13c side.

The inflow port side of the fourth three-way joint 13d is connected to the outflow port of the second three-way joint 13b. The inlet side of the cooling expansion valve 14b is connected to one of the outlets of the fourth three-way joint 13d. The inlet side of the cooling expansion valve 14c is connected to the other outlet of the fourth three-way joint 13d.

The cooling expansion valve 14b reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger 16 and adjusts the flow rate of the refrigerant flowing out to the downstream side in the operation mode of cooling the blown air, as in the cooling mode described later. It is a decompression unit for cooling.

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 the casing 31 of the indoor air conditioning unit 30, which will be described later. The indoor evaporator 18 is an evaporation unit that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant decompressed by the cooling expansion valve 14b and the blown air blown from the indoor blower 32. The second inlet 201b side of the integrated evaporation pressure regulating valve 20 is connected to the refrigerant outlet of the indoor evaporator 18.

The cooling expansion valve 14c reduces the pressure of the refrigerant flowing out of the outdoor heat exchanger 16 and reduces the flow rate of the refrigerant flowing out to the downstream side in the operation mode in which the battery 80 is cooled, as in the battery cooling mode described later. It is a cooling pressure reducing part to be adjusted.

The inlet side 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 for circulating the low-pressure refrigerant decompressed by the cooling expansion valve 14c and a water passage for circulating the low-temperature side heat medium circulating in the low-temperature side heat medium circuit 50. The chiller 19 is a cooling heat exchange unit that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant flowing through the refrigerant passage and the low-temperature side heat medium flowing through the water passage. Therefore, the chiller 19 is an evaporation unit.

The third inlet 201c side of the integrated evaporation pressure regulating valve 20 is connected to the outlet of the refrigerant passage of the chiller 19. The detailed configuration of the integrated evaporative pressure regulating valve 20 will be described with reference to FIGS. 2 to 4.

The integrated evaporation pressure regulating valve 20 is arranged on the downstream side of the refrigerant flow of a plurality of (three in this embodiment) evaporating portions such as the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 19, and the plurality of evaporating portions. It is an evaporation pressure adjusting part which can adjust the refrigerant evaporation pressure at the same time.

In other words, the integrated evaporation pressure regulating valve 20 is a variable throttle device capable of reducing the pressure of any of the refrigerants flowing out from the plurality of evaporation units. Therefore, as the amount of reduced pressure of the refrigerant in the integrated evaporation pressure adjusting valve 20 increases, the refrigerant evaporation pressure in the evaporation section connected to the upstream side can be increased.

The integrated evaporative pressure regulating valve 20 has a body 201, a valve body portion 202, and a driving portion 203. The body 201 is a metal bottomed cylindrical member. The body 201 forms the outer shell of the integrated evaporation pressure regulating valve 20 and also forms a columnar internal space inside.

Three inlets, a first inlet 201a, a second inlet 201b, and a third inlet 201c, are formed on the tubular side surface of the body 201 to allow the refrigerant to flow into the internal space. As shown in FIGS. 3 and 4, the three entrances are formed at equal angular intervals (120 ° intervals in the present embodiment) when viewed from the central axis direction of the internal space.

The three inlets of the first inlet 201a, the second inlet 201b, and the third inlet 201c are the inlets of the refrigerant passages through which the refrigerant flowing out from the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 19 are evaporated, respectively. Form.

As shown in FIG. 2, a drive unit 203 is arranged on one end side of the body 201 in the central axis direction. Further, as shown in FIGS. 2 to 4, an outlet 201d for flowing out the refrigerant from the internal space is formed in the central portion of the bottom surface of the body 201 on the other end side in the central axis direction.

The drive unit 203 is an electric actuator that displaces the valve body unit 202 arranged in the internal space of the body 201 around the central axis. The operation of the drive unit 203 is controlled by a control signal (control pulse) output from the control device 60.

The valve body portion 202 is a metal columnar member. As shown in FIG. 4, the valve body portion 202 is housed in the internal space of the body 201. The valve body portion 202 is formed in a fan shape in cross section when viewed from the central axis direction. The central axis of the cross-sectional fan shape of the valve body portion 202 is arranged coaxially with the central axis of the internal space of the body 201. The radius of the cross-sectional fan shape of the valve body 202 is slightly smaller than the radius of the columnar internal space of the body 201.

Therefore, as shown in FIG. 4, a seal member 205 for suppressing the leakage of the refrigerant from the gap between the valve body portion 202 and the body 201 is arranged on the inner peripheral side surface of the body 201. Therefore, when the drive unit 203 displaces the valve body portion 202 around the central axis, the outer peripheral side surface of the valve body portion 202 having an arcuate cross section slides with the seal member 205.

The central angle of the fan shape of the valve body portion 202 is formed to be about 80 ° to 110 °. Therefore, when the drive unit 203 displaces the valve body portion 202, the outer peripheral side surface of the valve body portion 202 having an arcuate cross section half-opens any one of the first inlet 201a, the second inlet 201b, and the third inlet 201c. , Or it can be fully closed. Then, the remaining two can be fully opened. The half-open inlet acts as a throttle (orifice) and exerts a refrigerant decompression effect.

Further, the valve body portion 202 can be fully opened at all the inlets of the first inlet 201a, the second inlet 201b, and the third inlet 201c. Therefore, the valve body portion 202 has a passage cross-sectional area (more specifically, a first inlet 201a, a second inlet 201b, and a third inlet 201c) of a plurality of refrigerant passages through which the refrigerants flowing out from the plurality of evaporation portions are circulated. It is a single opening adjustment unit that adjusts the opening area).

Further, at the first inlet 201a to the third inlet 201c, lead valves (not shown) for prohibiting the flow of the refrigerant from the internal space side of the body 201 to the plurality of evaporation portions are arranged. That is, the integrated evaporation pressure adjusting valve 20 has a backflow prevention function for prohibiting the flow of the refrigerant from the outlet 201d side to the plurality of evaporation parts sides.

Here, the function of the integrated evaporative pressure regulating valve 20 will be described. First, any one of the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 19 is defined as the first evaporation section, and the other one is defined as the second evaporation section. At this time, the integrated evaporation pressure adjusting valve 20 displaces the valve body portion 202 to set the refrigerant evaporation pressure in the first evaporation portion to a value higher or lower than the refrigerant evaporation pressure in the second evaporation portion. Can also be adjusted.

This function will be described by exemplifying an operation mode in which the outdoor heat exchanger 16 and the indoor evaporator 18 functioning as an evaporator are connected in parallel with respect to the refrigerant flow, as in the parallel dehumidification mode described later. In this example, the outdoor heat exchanger 16 is defined as the first evaporation unit, and the indoor evaporator 18 is defined as the second evaporation unit.

First, it is assumed that the drive unit 203 displaces the valve body unit 202 to a position where the second inlet 201b is half-opened, as shown in the cross-sectional view of FIG. In this case, the refrigerant flowing out of the outdoor heat exchanger 16 flows into the internal space through the fully open first inlet 201a. The refrigerant flowing out of the indoor evaporator 18 is decompressed when passing through the half-open second inlet 201b and flows into the internal space.

Therefore, in the integrated evaporation pressure adjusting valve 20, when the valve body portion 202 half-opens the second inlet 201b, the refrigerant evaporation pressure in the outdoor heat exchanger 16 which is the first evaporation portion is changed to the indoor evaporation which is the second evaporation portion. It can be adjusted to a value lower than the refrigerant evaporation pressure in the vessel 18.

Next, it is assumed that the drive unit 203 displaces the valve body unit 202 to a position where the first inlet 201a is half-opened. In this case, the refrigerant flowing out of the outdoor heat exchanger 16 is decompressed when passing through the half-opened first inlet 201a and flows into the internal space. The refrigerant flowing out of the indoor evaporator 18 flows into the internal space through the fully opened second inlet 201b.

Therefore, in the integrated evaporation pressure adjusting valve 20, when the valve body portion 202 half-opens the first inlet 201a, the refrigerant evaporation pressure in the outdoor heat exchanger 16 which is the first evaporation portion is changed to the indoor evaporation which is the second evaporation portion. It can be adjusted to a value higher than the refrigerant evaporation pressure in the vessel 18.

Further, an evaporation unit different from the first evaporation unit and the second evaporation unit is defined as a third evaporation unit. At this time, the integrated evaporation pressure adjusting valve 20 adjusts the refrigerant evaporation pressure in the third evaporation section to be equal to the lower of the refrigerant evaporation pressure in the first evaporation section and the refrigerant evaporation pressure in the second evaporation section. can do.

Regarding this function, as in the parallel dehumidification waste heat recovery mode described later, an operation mode in which the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 19 that function as an evaporator are connected in parallel with the refrigerant flow is provided. Let's take an example. In this example, the outdoor heat exchanger 16 is defined as the first evaporation section, the indoor evaporator 18 is defined as the second evaporation section, and the chiller 19 is defined as the third evaporation section.

Then, it is assumed that the drive unit 203 displaces the valve body unit 202 to a position where the second inlet 201b is half-opened, as shown in the cross-sectional view of FIG. In this case, as described above, the refrigerant evaporation pressure in the outdoor heat exchanger 16 which is the first evaporation unit is lower than the refrigerant evaporation pressure in the indoor evaporator 18 which is the second evaporation unit. Further, the refrigerant flowing out of the chiller 19 flows into the internal space through the fully opened third inlet 201c.

Therefore, in the integrated evaporation pressure adjusting valve 20, when the valve body portion 202 half-opens the second inlet 201b, the refrigerant evaporation pressure in the chiller 19 which is the third evaporation portion is changed to the outdoor heat exchanger 16 which is the first evaporation portion. It can be adjusted to be equivalent to the refrigerant evaporation pressure in. This is the same regardless of which evaporation part is used as the first to third evaporation parts.

The inlet side of the accumulator 21 is connected to the outlet 201d of the integrated evaporative pressure regulating valve 20. The accumulator 21 is a gas-liquid separator on the low-pressure side that separates the gas-liquid of the low-pressure refrigerant and stores the separated liquid-phase refrigerant as a surplus refrigerant in the cycle. The suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 21. That is, the compressor 11 sucks the refrigerant flowing out from the integrated evaporation pressure adjusting valve 20 through the accumulator 21.

Next, the high temperature side heat medium circuit 40 will be described. The high temperature side heat medium circuit 40 shown in FIG. 1 is a heat medium circulation circuit that circulates the high temperature side heat medium. An ethylene glycol aqueous solution is used as the heat medium on the high temperature side. In the high temperature side heat medium circuit 40, 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 are arranged.

The high temperature side heat medium pump 41 is a water pump that pumps the high temperature side heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12. The high temperature side heat medium pump 41 is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 60.

The heat medium inlet side of the heater core 42 is connected to the outlet of the water passage of the water-refrigerant heat exchanger 12. 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 in the casing 31 of the indoor air conditioning unit 30. The suction port side of the high temperature side heat medium pump 41 is connected to the heat medium outlet of the heater core 42.

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 to reduce the amount of heat radiated from the high temperature side heat medium to the blown air in the heater core 42. Can be adjusted. That is, the heating amount of the blown air in the heater core 42 can be adjusted.

That is, in the present embodiment, each component device 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. There is.

Next, the low temperature side heat 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. As the low temperature side heat medium, the same fluid as the high temperature side heat medium can be adopted. In the low temperature side heat medium circuit 50, the water passage of the chiller 19, the low temperature side heat medium pump 51, the cooling water passage 80a of the battery 80, and the like are arranged.

The low temperature side heat medium pump 51 is a water pump that pumps the low temperature side 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 water passage 80a of the battery 80 is connected to the outlet of the water passage of the chiller 19.

The cooling water passage 80a is formed inside a battery case that houses the battery cells of the battery 80. The cooling water passage 80a has a passage configuration in which a plurality of passages are connected in parallel inside the battery case. As a result, the cooling water passage 80a can evenly cool all the battery cells. The suction port side of the low temperature side heat medium pump 51 is connected to the outlet of the cooling water passage 80a.

That is, in the present embodiment, each component device of the chiller 19 and the low temperature side heat medium circuit 50 constitutes a cooling unit that cools the battery 80 that cools the object to be cooled.

Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is a unit for blowing out blown air adjusted to an appropriate temperature for blowing into the vehicle interior to an appropriate location in the vehicle interior. The indoor air conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the frontmost part of the vehicle interior.

The indoor air-conditioning unit 30 accommodates an indoor blower 32, an indoor evaporator 18 of a refrigeration cycle device 10, a heater core 42 of a high-temperature side heat medium circuit 40, and the like in a casing 31 that forms an air passage for blown air. The casing 31 is made of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.

An inside / outside air switching device 33 is arranged on the most upstream side of the blown air flow of the casing 31. The inside / outside air switching device 33 switches and introduces the inside air (vehicle interior air) and the outside air (vehicle interior outside air) into the casing 31. The operation of the inside / outside air switching device 33 is controlled by a control signal output from the control device 60.

An indoor blower 32 is arranged on the downstream side of the blower air flow of the inside / outside air switching device 33. The indoor blower 32 blows the air sucked through the inside / outside air switching device 33 toward the vehicle interior. The indoor blower 32 is an electric blower whose rotation speed (that is, blowing capacity) is controlled by a control voltage output from the control device 60.

On the downstream side of the blown air flow of the indoor 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 blown air flow with respect to the heater core 42. Further, a cold air bypass passage 35 is formed in the casing 31 to allow the blown air after passing through the indoor evaporator 18 to bypass the heater core 42 and flow to the downstream side.

The air mix door 34 is arranged on the downstream side of the blown air flow of the indoor evaporator 18 and on the upstream side of the blown air flow of the heater core 42. The air mix door 34 is an air volume ratio adjusting unit that adjusts the air volume ratio of the air volume of the air blown air passing through the heater core 42 and the air volume of the air blown air passing through the cold air bypass passage 35 among the air blown air after passing through the indoor evaporator 18. Is.

The air mix door 34 is driven by an electric actuator for the air mix door. The operation of the electric actuator for the air mix door is controlled by the control signal output from the control device 60.

A mixing space 36 is arranged on the downstream side of the blown air flow of the heater core 42 and the cold air bypass passage 35. The mixing space 36 is a space for mixing the blown air heated by the heater core 42 and the blown air that has not been heated through the cold air bypass passage 35. Further, at the most downstream portion of the blown air flow of the casing 31, a plurality of opening holes (not shown) for blowing out the blown air mixed in the mixing space 36 and having its temperature adjusted into the vehicle interior are arranged.

The plurality of opening holes communicate with a plurality of air outlets formed in the passenger compartment. As a plurality of outlets, a face outlet, a foot outlet, and a defroster outlet are provided. The fail outlet is an outlet that blows blown air toward the upper body of the occupant. The foot outlet is an outlet that blows blown air toward the feet of the occupant. The defroster outlet is an outlet that blows blown air toward the front window glass of the vehicle.

Therefore, the temperature of the conditioned air mixed in the mixing space 36 is adjusted by adjusting the air volume ratio between the air volume passing through the heater core 42 and the air volume passing through the cold air bypass passage 35 by the air mix door 34. As a result, the temperature of the blown air blown from each outlet into the vehicle interior is adjusted.

Next, the outline of the electric control unit of this embodiment will be described. The control device 60 is composed of a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof. Then, various calculations and processes are performed based on the air conditioning control program stored in the ROM, and various control target devices 11, 14a to 14c, 15a, 15b, 32, 33, 41, 51 connected to the output side thereof are performed. Etc. are controlled.

Further, on the input side of the control device 60, as shown in the block diagram of FIG. 5, the inside temperature sensor 61, the outside temperature sensor 62, the solar radiation sensor 63, the first refrigerant temperature sensor 64a to the third refrigerant temperature sensor 64c, and the discharge Temperature sensor 64d, evaporator temperature sensor 64f, first refrigerant pressure sensor 65a to fourth refrigerant pressure sensor 65d, high temperature side heat medium temperature sensor 66, low temperature side heat medium temperature sensor 67, battery temperature sensor 68, air conditioning air temperature sensor 69 Etc. are connected. Then, the detection signals of these sensor groups are input to the control device 60.

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

The first refrigerant temperature sensor 64a is a first refrigerant temperature detecting unit that detects the first temperature T1 of the refrigerant flowing out from the water-refrigerant heat exchanger 12. The second refrigerant temperature sensor 64b is a second refrigerant temperature detection unit that detects the second temperature T2 of the refrigerant flowing out of the outdoor heat exchanger 16. The third refrigerant temperature sensor 64c is a third refrigerant temperature detection unit that detects the third temperature T3 of the refrigerant flowing out of the chiller 19.

The discharge temperature sensor 64d is a discharge refrigerant temperature detection unit that detects the discharge temperature Td of the refrigerant discharged from the compressor 11. 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. The evaporator temperature sensor 64f of the present embodiment specifically detects the heat exchange fin temperature of the indoor evaporator 18.

The first refrigerant pressure sensor 65a is a first refrigerant pressure detecting unit that detects the first pressure P1 of the refrigerant flowing out from the water-refrigerant heat exchanger 12. The second refrigerant temperature sensor 64b is a second refrigerant pressure detecting unit that detects the second pressure P2 of the refrigerant flowing out from the outdoor heat exchanger 16. The third refrigerant pressure sensor 65c is a third refrigerant pressure detecting unit that detects the third pressure P3 of the refrigerant flowing out of the chiller 19. The fourth refrigerant pressure sensor 65d is a fourth refrigerant pressure detecting unit that detects the fourth pressure P4 of the refrigerant flowing out from the indoor evaporator 18.

The high temperature side heat medium temperature sensor 66 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 from the water passage of the water-refrigerant heat exchanger 12. The low temperature side heat medium temperature sensor 67 is a low temperature side heat medium temperature detection unit that detects the low temperature side heat medium temperature TWL which is the temperature of the low temperature side heat medium flowing out from the water passage of the chiller 19.

The battery temperature sensor 68 is a battery temperature detection unit that detects the battery temperature TB (that is, the temperature of the battery 80). The battery temperature sensor 68 of the present embodiment has a plurality of temperature sensors and detects the temperature of a plurality of locations of the battery 80. Therefore, the control device 60 can also detect the temperature difference of each part of the battery 80. Further, as the battery temperature TB, the average value of the detected values of a plurality of temperature sensors is adopted.

The conditioned air temperature sensor 69 is an conditioned air temperature detecting unit that detects the blast air temperature TAV blown from the mixed space to the vehicle interior.

Further, as shown in FIG. 5, an operation panel 70 arranged near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device 60, and various operation switches provided on the operation panel 70 are used. The operation signal is input. Various operation switches provided on the operation panel 70 include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, and a blowout mode switch.

The auto switch is an automatic control requesting unit that sets or cancels the automatic control operation of the vehicle air conditioner. The air conditioner switch is a cooling requesting unit that requires the indoor evaporator 18 to cool the blown air. The air volume setting switch is an air volume setting unit that manually sets the air volume of the indoor blower 32. The temperature setting switch is a temperature setting unit that sets a target temperature Tset in the vehicle interior. The blowout mode changeover switch is a blowout mode changeover unit for manually setting the blowout mode.

The control device 60 of the present embodiment is integrally composed of a control unit that controls various controlled devices connected to the output side of the control device 60. Then, the configuration (hardware and software) that controls the operation of each control target device constitutes a control unit that controls the operation of each control target device.

For example, in the control device 60, the configuration for controlling the refrigerant discharge capacity (specifically, the rotation speed of the compressor 11) of the compressor 11 constitutes the compressor control unit 60a. Further, the configuration for controlling the throttle opening of the heating expansion valve 14a, the cooling expansion valve 14b, and the cooling expansion valve 14c constitutes the expansion valve control unit 60b.

Further, the configuration for controlling the operation of the high-pressure on-off valve 15a, the low-pressure on-off valve 15b, and the like constitutes the on-off valve control unit 60c. Further, the configuration for controlling the operation of the integrated evaporation pressure adjusting valve 20 constitutes the evaporation pressure control unit 60d. The expansion valve control unit 60b, the on-off valve control unit 60c, and the like serve as a refrigerant circuit switching control unit that outputs a control signal when the refrigerant circuit is switched.

Next, the operation of the vehicle air conditioner 1 of the present embodiment in the above configuration will be described. As described above, the vehicle air conditioner 1 has a function of not only air-conditioning the interior of the vehicle but also cooling the battery 80. Therefore, the refrigeration cycle device 10 can switch the refrigerant circuit and execute the operation in various operation modes.

The operation modes of the vehicle air conditioner 1 include (1) cooling mode, (2) cooling battery cooling mode, (3) series dehumidification mode, (4) parallel dehumidification mode, (5) outside air heating mode, and (6) outside air. There are nine operation modes: heating waste heat recovery mode, (7) waste heat recovery heating mode, (8) battery cooling mode, and (9) parallel dehumidification waste heat recovery mode.

The switching of these operation modes is performed by executing the air conditioning control program. The air conditioning control program is executed when the auto switch of the operation panel 70 is turned on (ON) and automatic control of the vehicle interior is set. In the air conditioning control program, the detection signal of the sensor group and the operation signal of the operation panel 70 described above are read at a predetermined cycle, and the operation mode is switched.

More specifically, in the air conditioning control program, the operation mode is switched based on the outside air temperature Tam, the target blowing temperature TAO, and the operation signal of the air conditioning switch of the operation panel 70. The target blowout temperature TAO is the target temperature of the blown air blown into the vehicle interior.

The target blowout temperature TAO is calculated by the following mathematical formula F1.
TAO = Kset x Tset-Kr x Tr-Kam x Tam-Ks x Ts + C ... (F1)
In addition, Tset is the vehicle interior set temperature set by the temperature setting switch. Tr is the vehicle interior temperature detected by the inside air sensor. Tam is the outside temperature of the vehicle interior 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. The detailed operation of each operation mode will be described below.

(1) Cooling Mode The cooling mode is an operation mode in which the interior of the vehicle is cooled by blowing the cooled blown air into the interior of the vehicle without cooling the battery 80.

The cooling mode is executed when the air conditioner switch is turned on, the outside air temperature Tam is higher than the predetermined non-standard air temperature KTam, and the target outlet temperature TAO is equal to or less than the predetermined cooling standard temperature α1. Further, the cooling mode is executed when it is determined that the battery 80 does not need to be cooled.

The determination as to whether or not the battery 80 needs to be cooled is such that the battery temperature TB detected by the battery temperature sensor 68 is equal to or higher than the predetermined reference cooling temperature KTB (35 ° C. in the present embodiment). At that time, it is determined that the battery 80 needs to be cooled. Further, when the battery temperature TB is lower than the reference cooling temperature KTB, it is determined that the battery 80 does not need to be cooled.

In addition to this, when the low temperature side heat medium temperature TWL detected by the low temperature side heat medium temperature sensor 67 is equal to or higher than the predetermined reference heat medium temperature KTWL, it is determined that the battery 80 needs to be cooled. You may. Further, when the low temperature side heat medium temperature TWL is lower than the reference heat medium temperature KTWL, it may be determined that the battery 80 does not need to be cooled. The determination as to whether or not the battery 80 needs to be cooled is the same in the following operation modes.

In the cooling mode, the control device 60 closes the high-pressure on-off valve 15a and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in a fully open state, the cooling expansion valve 14b in a throttle state that exerts a refrigerant depressurizing action, and the cooling expansion valve 14c in a fully closed state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that at least the second inlet 201b is fully opened.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity.

Therefore, in the refrigerating cycle device 10 in the cooling mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the heating expansion valve 14a that is fully open → the outdoor heat exchanger 16 → the check valve 17 → the cooling expansion valve. It is switched to the refrigerant circuit in which the refrigerant circulates in the order of 14b → indoor evaporator 18 → integrated evaporation pressure regulating valve 20 → accumulator 21 → compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the rotation speed of the compressor 11 so that the evaporator temperature Tefien detected by the evaporator temperature sensor 64f approaches the target evaporator temperature TEO. The target evaporator temperature TEO is determined based on the target blowout temperature TAO with reference to the control map for the cooling mode stored in advance in the control device 60.

In the control map for the cooling mode, it is determined that the target evaporator temperature TEO increases as the target outlet temperature TAO increases. The target evaporator temperature TEO is determined to be a value within a range (specifically, 1 ° C. or higher) in which frost formation of the indoor evaporator 18 can be suppressed.

Further, the control device 60 controls the throttle opening degree of the cooling expansion valve 14b so that the supercooling degree SC1 of the refrigerant flowing into the cooling expansion valve 14b approaches the target supercooling degree SCO1.

The degree of supercooling SC1 is determined by using the second temperature T2 detected by the second refrigerant temperature sensor 64b and the second pressure P2 detected by the second refrigerant pressure sensor 65b. The target supercooling degree SCO1 is determined based on the outside air temperature Tam with reference to the control map for the cooling mode stored in advance in the control device 60. The target degree of supercooling SCO1 is determined so that the coefficient of performance (COP) of the cycle approaches the maximum value.

Further, with respect to the opening degree of the air mix door 34, the control device 60 operates the electric actuator for the air mix door so that the blown air temperature TAV detected by the air conditioning air temperature sensor 69 approaches the target blowing temperature TAO. Control. In the cooling mode, the target blowout temperature TAO is determined to be a relatively low value, so that the opening degree of the air mix door 34 is such that almost the entire flow rate of the blown air after passing through the indoor evaporator 18 passes through the cold air bypass passage 35. Is determined.

Therefore, in the refrigeration cycle device 10 in the cooling mode, a steam compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as the condensing unit and the indoor evaporator 18 functions as the evaporation unit. NS. As a result, in the refrigerating cycle device 10 in the cooling mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18.

In the high temperature side heat medium circuit 40 in the cooling mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the indoor air-conditioning unit 30 in the cooling mode, a part of the blown air cooled by the indoor evaporator 18 is reheated by the heater core 42, and the blown air whose temperature is adjusted so as to approach the target blowing temperature TAO is supplied to the passenger compartment. Can be blown out to. As a result, the interior of the vehicle can be cooled.

(2) Cooling Battery Cooling Mode The cooling battery cooling mode is an operation mode in which the battery 80 is cooled and the inside of the vehicle is cooled by blowing the cooled blown air into the vehicle interior.

The cooling battery cooling mode is executed when the air conditioner switch is turned on, the outside air temperature Tam is higher than the standard non-standard air temperature KTam, and the target blowout temperature TAO is equal to or lower than the standard cooling temperature α1. Further, the cooling battery cooling mode is executed when it is determined that the battery 80 needs to be cooled.

In the cooling battery cooling mode, the control device 60 closes the high-pressure on-off valve 15a and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the fully open state, the cooling expansion valve 14b in the throttle state, and the cooling expansion valve 14c in the throttle state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that one of the second inlet 201b and the third inlet 201c is half-open (throttle state) or fully open and the other is fully open.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity. Further, the control device 60 operates the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Therefore, in the refrigerating cycle device 10 in the cooling battery cooling mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the heating expansion valve 14a that is fully open → the outdoor heat exchanger 16 → the check valve 17 → the fourth. Refrigerant circulates in the order of three-way joint 13d → cooling expansion valve 14b → indoor evaporator 18 → integrated evaporation pressure regulating valve 20 → accumulator 21 → compressor 11. Further, compressor 11 → water-refrigerant heat exchanger 12 → fully open heating expansion valve 14a → outdoor heat exchanger 16 → check valve 17 → 4th three-way joint 13d → cooling expansion valve 14c → chiller 19 → The refrigerant circulates in the order of the integrated evaporation pressure regulating valve 20 → the accumulator 21 → the compressor 11.

That is, in the refrigerating cycle device 10 in the cooling battery cooling mode, one refrigerant branched at the fourth three-way joint 13d flows into the indoor evaporator 18, and the other refrigerant flows into the chiller 19. Then, the refrigerant flowing out of the indoor evaporator 18 and the refrigerant flowing out of the chiller 19 are switched to the refrigerant circuit where they are merged by the integrated evaporation pressure adjusting valve 20. That is, in the refrigerating cycle device 10 in the cooling battery cooling mode, the indoor evaporator 18 and the chiller 19 are switched to the refrigerant circuit connected in parallel with the refrigerant flow.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the throttle opening degree of the cooling expansion valve 14c so that the superheat degree SHC of the refrigerant on the outlet side of the chiller 19 approaches a predetermined target superheat degree SHCO. The degree of superheat SHC is determined using the third temperature T3 detected by the third refrigerant temperature sensor 64c and the third pressure P3 detected by the third refrigerant pressure sensor 65c.

Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 based on the throttle opening degree of the cooling expansion valve 14b and the throttle opening degree of the cooling expansion valve 14c.

Specifically, when the throttle opening of the cooling expansion valve 14b is smaller than the throttle opening of the cooling expansion valve 14c, the control device 60 opens the second inlet 201b fully and the third inlet. The operation of the integrated evaporation pressure regulating valve 20 is controlled so that the 201c is half-opened (throttle state). As a result, the refrigerant evaporation pressure in the indoor evaporator 18 becomes lower than the refrigerant evaporation pressure in the chiller 19.

As an operating condition in which the throttle opening of the cooling expansion valve 14b is smaller than the throttle opening of the cooling expansion valve 14c, the self-heating amount of the battery 80 is relatively small as in the normal discharge of the battery 80. There are operating conditions. Under such operating conditions, the refrigerant evaporation temperature in the indoor evaporator 18 is maintained at about 1 ° C., and the refrigerant evaporation temperature in the chiller 19 is set to about 10 ° C. in order to prevent frost formation in the indoor evaporator 18.

Further, in the control device 60, when the throttle opening of the cooling expansion valve 14b is larger than the throttle opening of the cooling expansion valve 14c, the second inlet 201b is half-opened (throttle state), and the third inlet is set to a third. The operation of the integrated evaporation pressure regulating valve 20 is controlled so that the inlet 201c is fully opened. As a result, the refrigerant evaporation pressure in the indoor evaporator 18 becomes higher than the refrigerant evaporation pressure in the chiller 19.

As an operating condition in which the throttle opening of the cooling expansion valve 14b is larger than the throttle opening of the cooling expansion valve 14c, the battery 80 is discharged as in a high load discharge in which a relatively large amount of electric power is discharged. There are operating conditions where the amount of self-heating is relatively large. Under such operating conditions, the refrigerant evaporation temperature in the indoor evaporator 18 is maintained at about 1 ° C., and the refrigerant evaporation temperature in the chiller 19 is set to about −5 ° C. in order to prevent frost formation in the indoor evaporator 18.

Further, in the control device 60, when the throttle opening of the cooling expansion valve 14b and the throttle opening of the cooling expansion valve 14c are equal, both the second inlet 201b and the third inlet 201c are fully opened. As a result, the operation of the integrated evaporation pressure regulating valve 20 is controlled. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 and the refrigerant evaporation pressure in the indoor evaporator 18 become equivalent. The control of other controlled devices is the same as in the cooling mode.

Therefore, in the refrigeration cycle device 10 in the cooling battery cooling mode, the water-refrigerant heat exchanger 12 and the outdoor heat exchanger 16 function as condensing parts, and the indoor evaporator 18 and the chiller 19 function as evaporating parts. A refrigeration cycle is configured.

As a result, in the refrigerating cycle device 10 in the cooling battery cooling mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18. The low temperature side heat medium can be cooled by the chiller 19.

In the high-temperature side heat medium circuit 40 in the cooling battery cooling mode, the high-temperature side heat medium pumped from the high-temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the low temperature side heat medium circuit 50 in the cooling battery cooling mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 circulates in the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled.

In the indoor air-conditioning unit 30 in the cooling battery cooling mode, a part of the blown air cooled by the indoor evaporator 18 is reheated by the heater core 42, and the blown air whose temperature is adjusted so as to approach the target blowing temperature TAO is supplied. It can be blown into the passenger compartment. As a result, the interior of the vehicle can be cooled.

Further, in the cooling battery cooling mode, the refrigerant evaporation pressure in the chiller 19 as the first evaporation part is higher than the refrigerant evaporation pressure in the indoor evaporator 18 as the second evaporation part by the action of the integrated evaporation pressure adjusting valve 20. It can be adjusted to either a value or a low value. Therefore, in the cooling battery cooling mode, the temperature of the low temperature side heat medium can be adjusted in a wide range of temperatures according to the amount of heat generated by the battery 80 and the like.

(3) Series dehumidification mode The series dehumidification mode is an operation mode in which the inside of the vehicle is dehumidified and heated by reheating the cooled and dehumidified blown air and blowing it into the vehicle interior without cooling the battery 80. ..

In the series dehumidification mode, the air conditioner switch is turned on, the outside air temperature Tam is higher than the standard non-standard temperature KTam, the target blowout temperature TAO is higher than the cooling reference temperature α1, and the target blowout temperature TAO is the predetermined dehumidification reference temperature. It is executed when it is β1 or less. Further, the series dehumidification mode is executed when it is determined that the battery 80 does not need to be cooled.

In the series dehumidification mode, the control device 60 closes the high-pressure on-off valve 15a and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the throttled state, and the cooling expansion valve 14c in the fully closed state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that at least the second inlet 201b is fully opened.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity.

Therefore, in the refrigeration cycle device 10 in the series dehumidification mode, the compressor 11 → water-refrigerant heat exchanger 12 → heating expansion valve 14a → outdoor heat exchanger 16 → check valve 17 → cooling expansion valve 14b → indoor evaporation. It is switched to the refrigerant circuit in which the refrigerant circulates in the order of the vessel 18 → the integrated evaporation pressure regulating valve 20 → the accumulator 21 → the compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 refers to the control map for the series dehumidification mode stored in the control device 60 in advance based on the target outlet temperature TAO for the heating expansion valve 14a and the cooling expansion valve 14b, respectively. Controls the aperture opening of.

In the control map for the series dehumidification mode, as the target outlet temperature TAO rises, the throttle opening of the heating expansion valve 14a decreases, and the throttle opening of the cooling expansion valve 14b increases. The throttle opening of 14a and the throttle opening of the cooling expansion valve 14b are determined. The control of other controlled devices is the same as in the cooling mode.

Therefore, in the refrigeration cycle device 10 in the series dehumidification mode, a steam compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the indoor evaporator 18 functions as an evaporation unit.

Further, 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 condensing unit 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 is configured in which the outdoor heat exchanger 16 functions as an evaporation unit.

As a result, in the refrigeration cycle device 10 in the series dehumidification mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. The indoor evaporator 18 can cool the blown air to dehumidify it.

In the high temperature side heat medium circuit 40 in the series dehumidification mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the indoor air conditioning unit 30 in the series dehumidification mode, the blast air cooled by the indoor evaporator 18 and dehumidified is reheated by the heater core 42, and the blast air whose temperature is adjusted so as to approach the target blowout temperature TAO is supplied to the passenger compartment. Can be blown out to. This makes it possible to perform dehumidifying and heating in the vehicle interior.

Further, in the series dehumidification mode, the throttle opening degree of the heating expansion valve 14a is reduced and the throttle opening degree of the cooling expansion valve 14b is increased as the target outlet temperature TAO rises. According to this, as the target blowing temperature TAO rises, the amount of heat radiated from the refrigerant in the water-refrigerant heat exchanger 12 can be increased, and the heating capacity of the blown air in the heater core 42 can be improved.

(4) Parallel dehumidification mode The parallel dehumidification mode is an operation mode in which the dehumidifying and heating of the vehicle interior is performed by reheating the cooled and dehumidified blown air and blowing it into the vehicle interior without cooling the battery 80. ..

The parallel dehumidification mode is executed when the air conditioner switch is turned on, the outside air temperature Tam is higher than the non-standard air temperature KTam, and the target blowout temperature TAO is higher than the dehumidification reference temperature β1. Further, the parallel dehumidification mode is executed when it is determined that the battery 80 does not need to be cooled.

In the parallel dehumidification mode, the control device 60 opens the high-pressure on-off valve 15a and the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the throttled state, and the cooling expansion valve 14c in the fully closed state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that one of the first inlet 201a and the second inlet 201b is half-open (throttle state) or fully open and the other is fully open.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity.

Therefore, in the refrigeration cycle device 10 in the parallel dehumidification mode, the compressor 11 → water-refrigerant heat exchanger 12 → first three-way joint 13a → heating expansion valve 14a → outdoor heat exchanger 16 → heating passage 22b → integrated type. The refrigerant circulates in the order of the evaporation pressure adjusting valve 20 → the accumulator 21 → the compressor 11. Further, the compressor 11 → water-refrigerant heat exchanger 12 → first three-way joint 13a → bypass passage 22a → cooling expansion valve 14b → indoor evaporator 18 → integrated evaporation pressure regulating valve 20 → accumulator 21 → compressor 11 The refrigerant circulates in order.

That is, in the refrigeration cycle device 10 in the parallel dehumidification mode, one refrigerant branched at the first three-way joint 13a flows into the outdoor heat exchanger 16, and the other refrigerant flows into the indoor evaporator 18. Then, the refrigerant flowing out of the outdoor heat exchanger 16 and the refrigerant flowing out of the indoor evaporator 18 are switched to the refrigerant circuit where they are merged by the integrated evaporation pressure adjusting valve 20. That is, in the refrigeration cycle device 10 in the parallel dehumidification mode, the outdoor heat exchanger 16 and the indoor evaporator 18 are switched to a refrigerant circuit connected in parallel with the refrigerant flow.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the rotation speed of the compressor 11 so that the high temperature side heat medium temperature TWH detected by the high temperature side heat medium temperature sensor 66 approaches a predetermined target high temperature side heat medium temperature TWHO. do.

Further, in the control device 60, for the heating expansion valve 14a and the cooling expansion valve 14b, the heating expansion valve so that the superheat degree SH of the refrigerant on the outlet side of the indoor evaporator 18 approaches the predetermined target superheat degree SHEO. The opening ratio of the throttle opening of the cooling expansion valve 14b to the throttle opening of 14a is adjusted. The degree of superheat SHE is determined using the evaporator temperature Tefien and the fourth pressure P4 detected by the fourth refrigerant pressure sensor 65d.

More specifically, when the superheat degree SH is larger than the target superheat degree SHEO, the opening ratio of the throttle opening of the cooling expansion valve 14b to the throttle opening of the heating expansion valve 14a is increased. .. When the superheat degree SH is smaller than the target superheat degree SHEO, the opening degree ratio of the throttle opening degree of the cooling expansion valve 14b to the throttle opening degree of the heating expansion valve 14a is reduced.

Further, the control device 60 controls the operation of the integrated evaporation pressure regulating valve 20 so that the evaporator temperature Tefien approaches the target evaporator temperature TEO.

Specifically, the control device 60 sets the first inlet 201a to fully open and the second inlet 201b to half open (throttle state) when the evaporator temperature Tefien becomes lower than the target evaporator temperature TEO. , Controls the operation of the integrated evaporation pressure regulating valve 20. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 becomes lower than the refrigerant evaporation pressure in the indoor evaporator 18.

As an operating condition in which the evaporator temperature Tefien becomes lower than the target evaporator temperature TEO, there is an operating condition in which the target blowing temperature TAO must rise to improve the heating capacity of the blown air. Under such operating conditions, the refrigerant evaporation temperature in the outdoor heat exchanger 16 is kept below the outside temperature while maintaining the refrigerant evaporation temperature in the indoor evaporator 18 at about 1 ° C. in order to prevent frost formation in the indoor evaporator 18. For example, about -5 ° C).

Further, the control device 60 is an integrated type so that when the evaporator temperature Tefien becomes higher than the target evaporator temperature TEO, the first inlet 201a is half-opened (squeezed state) and the second inlet 201b is fully opened. Controls the operation of the evaporation pressure regulating valve 20. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 becomes higher than the refrigerant evaporation pressure in the indoor evaporator 18.

As an operating condition in which the evaporator temperature Tefien is higher than the target evaporator temperature TEO, there is an operating condition in which the target blowing temperature TAO is lowered and the heating capacity of the blown air is lowered. Under such operating conditions, the refrigerant evaporation temperature in the indoor evaporator 18 is maintained at the target evaporator temperature TEO, the refrigerant evaporation temperature in the outdoor heat exchanger 16 is lower than the outside temperature, and the refrigerant in the indoor evaporator 18 is maintained. The temperature should be higher than the evaporation temperature. The control of other controlled devices is the same as in the cooling mode.

Therefore, in the refrigeration cycle device 10 in the parallel dehumidification mode, a steam compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit, and the outdoor heat exchanger 16 and the indoor evaporator 18 function as evaporating units. Will be done. As a result, in the refrigeration cycle device 10 in the parallel dehumidification mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18.

In the high temperature side heat medium circuit 40 in the parallel dehumidification mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the indoor air conditioning unit 30 in the parallel dehumidification mode, a part of the blown air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42, and the temperature of the blown air is adjusted so as to approach the target blowing temperature TAO. Can be blown into the passenger compartment. This makes it possible to perform dehumidifying and heating in the vehicle interior.

Further, in the parallel dehumidification mode, the refrigerant evaporation pressure in the outdoor heat exchanger 16 is adjusted to a value higher or lower than the refrigerant evaporation pressure in the indoor evaporator 18 by the action of the integrated evaporation pressure regulating valve 20. be able to.

According to this, when the target blowing temperature TAO rises, the refrigerant evaporation pressure in the outdoor heat exchanger 16 can be set to a value lower than the refrigerant evaporation pressure in the indoor evaporator 18. Therefore, the amount of heat absorbed from the outside air of the refrigerant in the outdoor heat exchanger 16 can be increased as compared with the series dehumidification mode. Then, the amount of heat radiated from the refrigerant in the water-refrigerant heat exchanger 12 to the heat medium on the high temperature side can be increased to improve the heating capacity of the blown air in the heater core 42.

Further, when the target blowing temperature TAO is lowered, the refrigerant evaporation pressure in the outdoor heat exchanger 16 can be set to a value higher than the refrigerant evaporation pressure in the indoor evaporator 18. Therefore, the amount of heat absorbed from the outside air of the refrigerant in the outdoor heat exchanger 16 can be reduced. Then, the amount of heat radiated from the refrigerant in the water-refrigerant heat exchanger 12 to the heat medium on the high temperature side can be reduced, and the heating capacity of the blown air in the heater core 42 can be reduced.

As a result, in the parallel dehumidification mode, the heating capacity of the blown air in the heater core 42 can be adjusted in a wide range according to the target blowing temperature TAO.

(5) Outside air heating mode The outside air heating mode is an operation mode in which the inside of the vehicle is heated by heating the blown air and blowing it into the vehicle interior without cooling the battery 80.

The outside air heating mode is executed when the air conditioner switch is not turned on and the target outlet temperature TAO is equal to or higher than the predetermined heating reference temperature γ1. Further, the outside air heating mode is executed when it is determined that the battery 80 does not need to be cooled.

In the outside air heating mode, the control device 60 closes the high-pressure on-off valve 15a and opens the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the fully closed state, and the cooling expansion valve 14c in the fully closed state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that at least the first inlet 201a is fully opened.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity.

Therefore, in the refrigeration cycle device 10 in the outside air heating mode, the compressor 11 → water-refrigerant heat exchanger 12 → heating expansion valve 14a → outdoor heat exchanger 16 → heating passage 22b → integrated evaporation pressure regulating valve 20 → It is switched to the refrigerant circuit in which the refrigerant circulates in the order of the accumulator 21 → the compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, in the control device 60, the heating expansion valve 14a is throttled open so that the supercooling degree SC2 of the refrigerant flowing into the heating expansion valve 14a approaches a predetermined target supercooling degree SCO2 for the outside air heating mode. Control the degree. The degree of supercooling SC2 is determined by using the first temperature T1 detected by the first refrigerant temperature sensor 64a and the first pressure P1 detected by the first refrigerant pressure sensor 65a. The control of other controlled devices is the same as in the parallel dehumidification mode.

Therefore, in the refrigeration cycle device 10 in the outside air heating mode, a steam compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the outdoor heat exchanger 16 functions as an evaporation unit. As a result, in the refrigeration cycle device 10 in the outside air heating mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12.

In the high temperature side heat medium circuit 40 in the outside air heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the indoor air conditioning unit 30 in the outside air heating mode, the blown air heated by the heater core 42 can be blown out into the vehicle interior. As a result, the interior of the vehicle can be heated.

(6) Outside air heating waste heat recovery mode The outside air heating waste heat recovery mode is an operation mode in which the battery 80 is cooled and the blast air is heated and blown into the vehicle interior to heat the vehicle interior. In other words, the outside air heating waste heat recovery mode is an operation mode in which the blown air is heated by using the heat absorbed from the outside air and the battery 80 as a heat source.

The outside air heating waste heat recovery mode is executed when the air conditioner switch is not turned on and the target outlet temperature TAO is equal to or higher than the heating reference temperature γ1. Further, the outside air heating waste heat recovery mode is executed when it is determined that the battery 80 needs to be cooled.

In the outside air heating waste heat recovery mode, the control device 60 opens the high-pressure on-off valve 15a and the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the fully closed state, and the cooling expansion valve 14c in the throttled state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that one of the first inlet 201a and the third inlet 201c is half-open (throttle state) or fully open and the other is fully open.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity. Further, the control device 60 operates the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Therefore, in the refrigeration cycle device 10 in the outside air heating waste heat recovery mode, the compressor 11 → water-refrigerant heat exchanger 12 → first three-way joint 13a → heating expansion valve 14a → outdoor heat exchanger 16 → heating passage 22b. → The refrigerant circulates in the order of the integrated evaporation pressure regulating valve 20 → the accumulator 21 → the compressor 11. Further, the compressor 11 → water-refrigerant heat exchanger 12 → first three-way joint 13a → bypass passage 22a → cooling expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → accumulator 21 → compressor 11 Circulates.

That is, in the refrigeration cycle device 10 in the outside air heating waste heat recovery mode, one refrigerant branched at the first three-way joint 13a flows into the outdoor heat exchanger 16, and the other refrigerant flows into the chiller 19. Then, the refrigerant flowing out of the outdoor heat exchanger 16 and the refrigerant flowing out of the chiller 19 are switched to the refrigerant circuit where they are merged by the integrated evaporation pressure adjusting valve 20. That is, in the refrigeration cycle device 10 in the outside air heating waste heat recovery mode, the outdoor heat exchanger 16 and the chiller 19 are switched to a refrigerant circuit connected in parallel with the refrigerant flow.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, in the control device 60, for the heating expansion valve 14a and the cooling expansion valve 14c, the throttle opening degree of the heating expansion valve 14a is such that the superheat degree SHC of the refrigerant on the outlet side of the chiller 19 approaches the target superheat degree SHCO. And the opening ratio of the cooling expansion valve 14c to the throttle opening is adjusted.

More specifically, when the superheat degree SHC is larger than the target superheat degree SHCO, the opening ratio of the throttle opening of the cooling expansion valve 14c to the throttle opening of the heating expansion valve 14a is increased. .. When the superheat degree SHC is smaller than the target superheat degree SHCO, the opening degree ratio of the throttle opening degree of the cooling expansion valve 14b to the throttle opening degree of the heating expansion valve 14a is reduced.

Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 based on the refrigerant evaporation temperature in the chiller 19. As the refrigerant evaporation temperature in the chiller 19, a third temperature T3 can be used.

Specifically, when the refrigerant evaporation temperature in the chiller 19 is lower than the predetermined reference temperature, the control device 60 makes the first inlet 201a fully open and the third inlet 201c half open (throttle state). , Controls the operation of the integrated evaporation pressure regulating valve 20. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 becomes lower than the refrigerant evaporation pressure in the chiller 19.

As an operating condition in which the refrigerant evaporation temperature in the chiller 19 is lower than the reference temperature, there is an operating condition in which the heating capacity of the blown air is improved by lowering the outside air temperature Tam or the like. Under such operating conditions, the refrigerant evaporation temperature in the outdoor heat exchanger 16 is kept below the outside air temperature (for example, −) while maintaining the refrigerant evaporation temperature in the chiller 19 at about 0 ° C. in order to suppress excessive cooling of the battery 80. Set to about 10 ° C).

Further, in the control device 60, when the refrigerant evaporation temperature in the chiller 19 is higher than the reference temperature, the integrated evaporation pressure is such that the first inlet 201a is half-opened (squeezed state) and the third inlet 201c is fully opened. Controls the operation of the regulating valve 20. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 becomes higher than the refrigerant evaporation pressure in the chiller 19.

As an operating condition in which the refrigerant evaporation temperature in the chiller 19 is higher than the reference temperature, it is possible to realize heating in the vehicle interior by using the waste heat of the battery 80 as a heat source, and there is an operating condition in which it is not necessary to improve the heating capacity of the blown air. be. Under such operating conditions, the refrigerant evaporation temperature in the outdoor heat exchanger 16 is set to about 1 ° C. so that frost formation in the outdoor heat exchanger 16 can be suppressed while maintaining the refrigerant evaporation temperature in the chiller 19 at about 0 ° C. .. The control of other controlled devices is the same as in the parallel dehumidification mode.

Therefore, in the refrigeration cycle device 10 in the outside air heating waste heat recovery mode, the steam compression type refrigeration cycle in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the outdoor heat exchanger 16 and the chiller 19 function as an evaporation unit. It is composed. As a result, in the refrigeration cycle device 10 in the outside air heating waste heat recovery mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. The low temperature side heat medium can be cooled by the chiller 19.

In the high-temperature side heat medium circuit 40 in the outside air heating waste heat recovery mode, the high-temperature side heat medium pumped from the high-temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the low temperature side heat medium circuit 50 in the outside air heating waste heat recovery mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows through the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled. In other words, the waste heat of the battery 80 can be absorbed by the low temperature side heat medium.

In the indoor air conditioning unit 30 in the outside air heating waste heat recovery mode, the blown air heated by the heater core 42 can be blown out into the vehicle interior. As a result, the interior of the vehicle can be heated.

Further, in the outside air heating waste heat recovery mode, the refrigerant evaporation pressure in the outdoor heat exchanger 16 is adjusted to either a value higher or lower than the refrigerant evaporation pressure in the chiller 19 by the action of the integrated evaporation pressure adjusting valve 20. can do.

According to this, when it becomes necessary to improve the heating capacity of the blown air, the refrigerant evaporation pressure in the outdoor heat exchanger 16 is set to be higher than the refrigerant evaporation pressure in the chiller 19 without changing the refrigerant evaporation pressure in the chiller 19. It can be a low value. Then, the amount of heat absorbed from the outside air of the refrigerant in the outdoor heat exchanger 16 can be increased.

Therefore, the amount of heat released from the refrigerant in the water-refrigerant heat exchanger 12 to the high-temperature side heat medium is increased without changing the temperature of the low-temperature side heat medium cooled by the chiller 19, and the blown air in the heater core 42 The heating capacity can be improved.

Further, when it becomes necessary to reduce the heating capacity of the blown air, the refrigerant evaporation pressure in the outdoor heat exchanger 16 is set to a value higher than the refrigerant evaporation pressure in the chiller 19 without changing the refrigerant evaporation pressure in the chiller 19. can do. Then, the amount of heat absorbed from the outside air of the refrigerant in the outdoor heat exchanger 16 can be reduced.

Therefore, the amount of heat released from the refrigerant in the water-refrigerant heat exchanger 12 to the high-temperature side heat medium is reduced without changing the temperature of the low-temperature side heat medium cooled by the chiller 19, and the blown air in the heater core 42 The heating capacity can be reduced.

As a result, in the outside air heating waste heat recovery mode, the heating capacity of the blown air in the heater core 42 can be adjusted in a wide range according to the required heating capacity of the blown air while appropriately cooling the battery 80. ..

(7) Waste Heat Recovery and Heating Mode The waste heat recovery and heating mode is an operation mode in which the battery 80 is cooled and the blast air is heated and blown into the vehicle interior to heat the vehicle interior. More specifically, the waste heat recovery heating mode is an operation mode in which the blown air is heated by using the heat absorbed from the battery 80 as a heat source.

The waste heat recovery heating mode is executed when the air conditioner switch is not turned on and the target outlet temperature TAO is equal to or higher than the heating reference temperature γ1. Further, the waste heat recovery heating mode is executed when it is determined that the battery 80 needs to be cooled.

In the waste heat recovery heating mode, the control device 60 opens the high-pressure on-off valve 15a and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in a fully closed state, the cooling expansion valve 14b in a fully closed state, and the cooling expansion valve 14c in a throttled state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that at least the third inlet 201c is fully opened.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity. Further, the control device 60 operates the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Therefore, in the refrigerating cycle device 10 in the waste heat recovery heating mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the bypass passage 22a → the cooling expansion valve 14c → the chiller 19 → the integrated evaporation pressure regulating valve 20 → the accumulator 21. → It is switched to the refrigerant circuit in which the refrigerant circulates in the order of the compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the throttle opening degree of the cooling expansion valve 14c so that the supercooling degree SC3 of the refrigerant flowing into the cooling expansion valve 14c approaches the target supercooling degree SCO3. The degree of supercooling SC3 is determined using the first temperature T1 and the first pressure P1.

The target supercooling degree SCO3 is determined based on the target high temperature side heat medium temperature TWHO with reference to the control map for the outside air heating mode stored in advance in the control device 60. The target supercooling degree SCO3 is determined so that the COP approaches the maximum value. The control of other controlled devices is the same as in the parallel dehumidification mode.

Therefore, in the refrigeration cycle device 10 in the waste heat recovery heating mode, a steam compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the chiller 19 functions as an evaporation unit. As a result, in the refrigeration cycle device 10 in the outside air heating mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. The low temperature side heat medium can be cooled by the chiller 19.

In the high temperature side heat medium circuit 40 in the waste heat recovery heating mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the low temperature side heat medium circuit 50 in the waste heat recovery heating mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows through the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled. In other words, the waste heat of the battery 80 can be absorbed by the low temperature side heat medium.

In the indoor air conditioning unit 30 in the waste heat recovery heating mode, the blown air heated by the heater core 42 can be blown out into the vehicle interior. As a result, the interior of the vehicle can be heated.

(8) Battery cooling mode The battery cooling mode is an operation mode in which the battery 80 is cooled without air-conditioning the interior of the vehicle. The battery cooling mode is executed when the air conditioning operation is not required or when the air conditioning switch is not turned on and the target outlet temperature TAO is lower than the heating reference temperature γ1. Further, the battery cooling mode is executed when it is determined that the battery 80 needs to be cooled.

In the battery cooling mode, the control device 60 closes the high-pressure on-off valve 15a and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in a fully open state, the cooling expansion valve 14b in a fully closed state, and the cooling expansion valve 14c in a throttled state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that at least the third inlet 201c is fully opened.

Further, the control device 60 stops the high temperature side heat medium pump 41. Further, the control device 60 operates the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Therefore, in the refrigerating cycle device 10 in the battery cooling mode, the compressor 11 (→ water-refrigerant heat exchanger 12) → fully open heating expansion valve 14a → outdoor heat exchanger 16 → check valve 17 → cooling. The expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → accumulator 21 → compressor 11 is switched to a refrigerant circuit in which the refrigerant circulates in this order.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the operation of the electric actuator for the air mix door so that the ventilation path on the heater core 42 side is fully closed with respect to the opening degree of the air mix door 34. Further, the control device 60 stops the indoor blower 32. The control of other controlled devices is the same as in the cooling / cooling mode.

Therefore, in the refrigeration cycle device 10 in the battery cooling mode, a vapor compression refrigeration cycle is configured in which the outdoor heat exchanger 16 functions as a condensing unit and the chiller 19 functions as an evaporation unit. As a result, in the refrigerating cycle device 10 in the battery cooling mode, the low temperature side heat medium can be cooled by the chiller 19.

In the low temperature side heat medium circuit 50 in the battery cooling mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. Further, the low temperature side heat medium cooled by the chiller 19 flows through the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled.

(9) Parallel dehumidifying waste heat recovery mode In the parallel dehumidifying waste heat recovery mode, the battery 80 is cooled, and the cooled and dehumidified blown air is reheated and blown into the vehicle interior to dehumidify and heat the vehicle interior. This is the operation mode to be performed. More specifically, the parallel dehumidifying waste heat recovery mode is an operation mode for reheating the blown air cooled by using the heat absorbed from the outside air and the battery 80 as a heat source.

In the parallel dehumidification waste heat recovery mode, the air conditioner switch is turned on, the outside air temperature Tam is higher than the standard non-standard temperature KTam, the target blowout temperature TAO is higher than the cooling reference temperature α1, and the target blowout temperature TAO is higher than the dehumidification reference temperature β1. Is executed when is also high. Further, the parallel dehumidification waste heat recovery mode is executed when it is determined that the battery 80 needs to be cooled.

In the parallel dehumidifying waste heat recovery mode, the control device 60 opens the high-pressure on-off valve 15a and the low-pressure on-off valve 15b. Further, in the control device 60, the heating expansion valve 14a is in the throttle state, the cooling expansion valve 14b is in the throttle state, and the cooling expansion valve 14c is in the throttle state. Further, the control device 60 controls the operation of the integrated evaporation pressure adjusting valve 20 so that either one of the first inlet 201a and the second inlet 201b is half-open (throttle state) or fully open.

Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity. Further, the control device 60 operates the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Therefore, in the refrigerating cycle device 10 in the parallel dehumidifying waste heat recovery mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the first three-way joint 13a → the heating expansion valve 14a → the outdoor heat exchanger 16 → the heating passage 22b. → The refrigerant circulates in the order of the integrated evaporation pressure regulating valve 20 → the accumulator 21 → the compressor 11. Further, compressor 11 → water-refrigerant heat exchanger 12 → first three-way joint 13a → bypass passage 22a → fourth three-way joint 13d → cooling expansion valve 14b → indoor evaporator 18 → integrated evaporation pressure regulating valve 20 → accumulator The refrigerant circulates in the order of 21 → compressor 11. Further, compressor 11 → water-refrigerant heat exchanger 12 → first three-way joint 13a → bypass passage 22a → fourth three-way joint 13d → cooling expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → accumulator 21 → The refrigerant circulates in the order of the compressor 11.

That is, in the refrigeration cycle device 10 in the parallel dehumidifying waste heat recovery mode, one refrigerant branched at the first three-way joint 13a flows into the outdoor heat exchanger 16, and the other refrigerant flows into the fourth three-way joint 13d. .. Further, one of the refrigerants branched at the fourth three-way joint 13d flows into the indoor evaporator 18, and the other refrigerant flows into the chiller 19.

Then, the refrigerant flowing out of the outdoor heat exchanger 16, the refrigerant flowing out of the indoor evaporator 18, and the refrigerant flowing out of the chiller 19 are switched to the refrigerant circuit where they are merged by the integrated evaporation pressure adjusting valve 20. That is, in the refrigeration cycle device 10 in the parallel dehumidification waste heat recovery mode, the indoor evaporator 18, the chiller 19, and the outdoor heat exchanger 16 are switched to a refrigerant circuit connected in parallel with the refrigerant flow.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, with respect to the control device 60 and the cooling expansion valve 14c, the throttle opening degree is controlled so as to be a reference opening degree for the parallel dehumidifying waste heat recovery mode defined in advance. Further, the control device 60 controls the heating expansion valve 14a and the cooling expansion valve 14b in the same manner as in the parallel dehumidification mode.

Further, the control device 60 controls the operation of the integrated evaporation pressure regulating valve 20 so that the evaporator temperature Tefien approaches the target evaporator temperature TEO, as in the parallel dehumidification mode.

Specifically, the control device 60 sets the first inlet 201a to fully open and the second inlet 201b to half open (throttle state) when the evaporator temperature Tefien becomes lower than the target evaporator temperature TEO. , Controls the operation of the integrated evaporation pressure regulating valve 20. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 becomes lower than the refrigerant evaporation pressure in the indoor evaporator 18.

At this time, since the third inlet 201c is fully opened, the refrigerant evaporation pressure in the chiller 19 becomes equivalent to the refrigerant evaporation pressure in the outdoor heat exchanger 16.

Further, the control device 60 is an integrated type so that when the evaporator temperature Tefien becomes higher than the target evaporator temperature TEO, the first inlet 201a is half-opened (squeezed state) and the second inlet 201b is fully opened. Controls the operation of the evaporation pressure regulating valve 20. As a result, the refrigerant evaporation pressure in the outdoor heat exchanger 16 becomes higher than the refrigerant evaporation pressure in the indoor evaporator 18.

At this time, since the third inlet 201c is fully opened, the refrigerant evaporation pressure in the chiller 19 becomes equivalent to the refrigerant evaporation pressure in the indoor evaporator 18. The control of other controlled devices is the same as in the parallel dehumidification mode.

Therefore, in the refrigeration cycle device 10 in the parallel dehumidifying waste heat recovery mode, the water-refrigerant heat exchanger 12 functions as a condensing unit, and the outdoor heat exchanger 16, the indoor evaporator 18, and the chiller 19 function as an evaporating unit. A compression refrigeration cycle is constructed.

As a result, in the refrigeration cycle device 10 in the parallel dehumidification waste heat recovery mode, the high temperature side heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18. The low temperature side heat medium can be cooled by the chiller 19.

In the high temperature side heat medium circuit 40 in the parallel dehumidifying waste heat recovery mode, the high temperature side heat medium pumped from the high temperature side heat medium pump 41 flows into the water-refrigerant heat exchanger 12. The high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the low temperature side heat medium circuit 50 in the parallel dehumidification waste heat recovery mode, the low temperature side heat medium pumped from the low temperature side heat medium pump 51 flows into the chiller 19. The low temperature side heat medium cooled by the chiller 19 flows through the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled. In other words, the waste heat of the battery 80 can be absorbed by the low temperature side heat medium.

In the indoor air conditioning unit 30 in the parallel dehumidifying waste heat recovery mode, a part of the blown air cooled and dehumidified by the indoor evaporator 18 is reheated by the heater core 42, and the temperature is adjusted so as to approach the target blowing temperature TAO. It is possible to blow out the blown air into the passenger compartment. This makes it possible to perform dehumidifying and heating in the vehicle interior.

Further, in the parallel dehumidifying waste heat recovery mode, the refrigerant evaporation pressure in the outdoor heat exchanger 16 is set to a value higher or lower than the refrigerant evaporation pressure in the indoor evaporator 18 by the action of the integrated evaporation pressure regulating valve 20. Can also be adjusted. Therefore, as in the parallel dehumidification mode, the amount of heat absorbed from the outside air can be increased as the target blowing temperature TAO rises, and the heating capacity of the blown air in the heater core 42 can be adjusted in a wide range.

In addition to this, in the parallel dehumidifying waste heat recovery mode, the refrigerant evaporation pressure in the chiller 19 is adjusted to be equal to the lower value of the refrigerant evaporation pressure in the outdoor heat exchanger 16 and the refrigerant evaporation pressure in the indoor evaporator 18. can do. Therefore, as the target blowing temperature TAO rises, the amount of heat absorbed from the battery 80 can be increased, and the heating capacity of the blown air in the heater core 42 can be improved as compared with the parallel dehumidification mode.

As described above, the refrigeration cycle device 10 of the present embodiment can switch various operation modes. As a result, the vehicle air conditioner 1 can realize comfortable air conditioning in the vehicle interior while appropriately adjusting the temperature of the battery 80.

Further, in the refrigeration cycle device 10, the two evaporation units are connected in parallel to the refrigerant flow in (2) cooling battery cooling mode, (4) parallel dehumidification mode, and (6) outside air heating waste heat recovery mode. be able to. That is, if any one of the plurality of evaporation parts is defined as the first evaporation part and the other one is defined as the second evaporation part, the first evaporation part and the second evaporation part are defined with respect to the refrigerant flow. Can be connected in parallel.

Further, the integrated evaporation pressure adjusting valve 20 can adjust the refrigerant evaporation pressure in the first evaporation section to a value higher or lower than the refrigerant evaporation pressure in the second evaporation section. Therefore, in the refrigeration cycle apparatus 10, the refrigerant evaporation temperature in one evaporation unit is affected by the refrigerant evaporation temperature in another evaporation unit among the plurality of evaporation units connected in parallel with each other with respect to the refrigerant flow. Can be adjusted appropriately.

Further, in the refrigeration cycle device 10, in (9) parallel dehumidification waste heat recovery mode, three evaporation units can be connected in parallel to each other with respect to the refrigerant flow. That is, if the evaporation section different from the first evaporation section and the second evaporation section is defined as the third evaporation section among the plurality of evaporation sections, the first evaporation section, the second evaporation section, and the third evaporation section are the refrigerant flows. Can be connected in parallel to.

Further, the integrated evaporation pressure adjusting valve 20 adjusts the refrigerant evaporation pressure in the third evaporation section to be equal to the lower of the refrigerant evaporation pressure in the first evaporation section and the refrigerant evaporation pressure in the second evaporation section. .. According to this, the control for adjusting the refrigerant evaporation pressure in the plurality of evaporation units is not unnecessarily complicated.

This means that the outdoor heat exchanger 16 that exchanges heat between the refrigerant and the outside air at least in the plurality of evaporating parts, the indoor evaporator 18 that exchanges heat between the refrigerant and the blown air, and the low-temperature side heat that is the cooling object with the refrigerant. This is effective when the chiller 19 that exchanges heat with the medium is included.

More specifically, in order for the outdoor heat exchanger 16 to function as an evaporation unit, it is necessary to lower the refrigerant evaporation temperature below the outside air temperature Tam. Therefore, the refrigerant evaporation pressure in the outdoor heat exchanger 16 must be adjusted according to the outside air temperature Tam.

Further, the refrigerant evaporation pressure in the indoor evaporator 18 must be adjusted so as to prevent frost formation in the indoor evaporator 18 so as to realize comfortable air conditioning in the vehicle interior. Therefore, for example, in the refrigeration cycle device 10 of the present embodiment, the refrigerant evaporation temperature of the indoor evaporator 18 is adjusted to 1 ° C. or higher.

On the other hand, the refrigerant evaporation temperature in the chiller 19 needs to be adjusted in a wider range than the refrigerant evaporation temperature in the outdoor heat exchanger 16 and the indoor evaporator 18, although it is necessary to consider the self-heating amount of the battery 80. It will be possible. Therefore, if the chiller 19 is used as the third evaporation unit, the control for adjusting the refrigerant evaporation pressure in the plurality of evaporation units is not unnecessarily complicated.

Further, in the refrigerating cycle device 10, the cooling expansion valve 14c functions as a blocking unit that blocks the inflow of the refrigerant into the third evaporation unit when the refrigerant is evaporated in the first evaporation unit and the second evaporation unit. have. Therefore, if there is a risk that the refrigerant evaporation temperature in the chiller 19 will be unnecessarily lowered and the temperature of the low temperature side heat medium will be excessively lowered, the inflow of the refrigerant into the chiller 19 can be blocked.

In other words, the refrigeration cycle device 10 of the present embodiment has a cooling expansion valve 14c having a function as a shutoff portion. Therefore, in the (9) parallel dehumidification waste heat recovery mode, if there is a risk of excessively lowering the temperature of the low temperature side heat medium, the cooling expansion valve 14c is fully closed and the mode is switched to the (4) parallel dehumidification mode. Can be done.

Further, the integrated evaporation pressure adjusting valve 20 has a single valve body portion 202 and a driving portion 203 that simultaneously adjust the passage cross-sectional areas of a plurality of refrigerant passages. According to this, as compared with the case where individual evaporation pressure adjusting valves are arranged on the downstream side of the refrigerant flow of the plurality of evaporation parts, they are connected in parallel with each other without incurring complicated circuit configuration and large size. The refrigerant evaporation temperature in the plurality of evaporation units can be appropriately adjusted.

Further, since the integrated evaporation pressure adjusting valve 20 has a backflow prevention function, it is possible to prevent the refrigerant from flowing from the suction port side of the compressor 11 to the evaporation part side when switching the operation mode or the like. ..

(Second Embodiment)
In this embodiment, an example in which the integrated evaporation pressure regulating valve 210 shown in FIGS. 6 to 10 is adopted instead of the integrated evaporation pressure regulating valve 20 will be described.

The integrated evaporative pressure regulating valve 210 has a body 211, a valve body portion 212, and a drive portion 213. The body 211 is a metal cylindrical member. The body 211 forms the outer shell of the integrated evaporation pressure regulating valve 210 and forms a columnar internal space inside.

Three inlets, a first inlet 211a, a second inlet 211b, and a third inlet 211c, are formed on the tubular side surface of the body 211 to allow the refrigerant to flow into the internal space. As shown in FIG. 6, the three entrances are formed side by side in the direction of the central axis of the body 211. The first inlet 211a, the second inlet 211b, and the third inlet 211c correspond to the first inlet 201a, the second inlet 201b, and the third inlet 201c of the integrated evaporation pressure regulating valve 20 described in the first embodiment, respectively. There is.

As shown in FIG. 6, a drive unit 213 is arranged on one end side of the body 211 in the central axis direction. As shown in FIGS. 6 and 7, an outlet 211d for flowing out the refrigerant from the internal space is formed on the other end side of the body 211 in the central axis direction.

The drive unit 203 is an electric actuator that displaces the valve body unit 212 arranged in the internal space of the body 211 around the central axis. The basic configuration of the drive unit 213 is the same as that of the drive unit 203 of the integrated evaporative pressure regulating valve 20 described in the first embodiment.

The valve body portion 212 is a metal cylindrical member. As shown in FIGS. 8 and 9, the valve body portion 212 is housed in the internal space of the body 211. The central axis of the valve body portion 212 is arranged coaxially with the central axis of the internal space of the body 211. The outer diameter of the valve body portion 212 is slightly smaller than the inner diameter of the columnar internal space of the body 211.

Therefore, as shown in FIG. 8, a seal member 205 for suppressing the leakage of the refrigerant from the gap between the valve body portion 212 and the body 211 is arranged on the inner peripheral side surface of the body 211. Therefore, when the drive unit 213 displaces the valve body portion 212 around the central axis, the outer peripheral side surface of the valve body portion 212 slides with the seal member 215.

As shown in FIGS. 9 and 10, the side surface of the valve body portion 212 has a first communication hole 212a, a second communication hole 212b, and a third communication hole that communicate the outer peripheral side and the inner peripheral side of the valve body portion 212. 212c is formed. The first communication hole 212a, the second communication hole 212b, and the third communication hole 212c are formed in a band shape extending in the circumferential direction (that is, the rotation direction).

The first communication hole 212a, the second communication hole 212b, and the third communication hole 212c are arranged side by side in the central axis direction. The first communication hole 212a, the second communication hole 212b, and the third communication hole 212c are arranged so as to be polymerizable with the first entrance 211a, the second entrance 211b, and the third entrance 211c, respectively.

Further, the strip-shaped first communication hole 212a, the second communication hole 212b, and the third communication hole 212c have different width dimensions (that is, axial dimensions) as shown in the developed view of FIG. Therefore, when the drive unit 213 displaces the valve body portion 212 around the central axis, the first inlet 211a and the first communication hole 211a and the first communication hole 211a and the third communication hole 212a are arranged according to the width dimensions of the first communication hole 212a, the second communication hole 212b, and the third communication hole 212c. The opening degree of the 2nd inlet 211b and the 3rd inlet 211c can be changed.

Specifically, the inlet that overlaps with the wide portion of each communication hole is fully open. The entrance that overlaps with the narrow part of the communication hole is half-open. The half-opened inlet serves as a throttle passage and exerts a refrigerant decompression effect. The inlet that overlaps with the part where the communication hole is not formed is fully closed.

In the valve body portion 212 of the present embodiment, as shown in FIG. 10, the width dimension pattern of the first communication hole 212a, the second communication hole 212b, and the third communication hole 212c is changed. According to the pattern of the present embodiment, when the drive unit 213 displaces the valve body portion 212, any one of the first inlet 211a, the second inlet 211b, and the third inlet 211c is closed as a throttle passage or fully closed. be able to. Then, the remaining two can be fully opened.

Therefore, the valve body portion 212 has a passage cross-sectional area (more specifically, a first inlet 211a, a second inlet 211b, and a third inlet 211c) of a plurality of refrigerant passages through which the refrigerants flowing out from the plurality of evaporation portions are circulated. It is a single opening adjustment unit that adjusts the opening area). Note that FIG. 10 is an explanatory diagram for explaining the shape of each communication hole and the opening degree of each inlet by using the developed view of the valve body portion 212.

Further, at the first inlet 211a to the third inlet 211c, a lead valve (not shown) for prohibiting the flow of the refrigerant from the internal space side of the body 211 to the plurality of evaporation portions side is arranged. That is, the integrated evaporation pressure adjusting valve 210 has a backflow prevention function for prohibiting the flow of the refrigerant from the outlet 211d side to the plurality of evaporation parts sides.

The configurations of the other refrigeration cycle device 10 and the vehicle air conditioner 1 are the same as those in the first embodiment. Further, in the vehicle air conditioner 1 of the present embodiment, (1) cooling mode, (2) cooling battery cooling mode, (3) series dehumidification mode, (4) parallel dehumidification mode, and (5) described in the first embodiment. Eight operation modes corresponding to (6) outside air heating mode, (6) outside air heating waste heat recovery mode, (7) waste heat recovery heating mode, and (8) battery cooling mode can be executed.

Therefore, the same effect as that of the first embodiment can be obtained in the refrigeration cycle apparatus 10 provided with the integrated evaporation pressure regulating valve 210 as in the present embodiment.

That is, among a plurality of evaporation parts connected in parallel to each other with respect to the refrigerant flow, the refrigerant evaporation temperature in one evaporation part is appropriately adjusted without being affected by the refrigerant evaporation temperature in another evaporation part. Can be done. Further, it is possible to appropriately adjust the refrigerant evaporation temperature in a plurality of evaporation units connected in parallel with each other without causing the circuit configuration to become complicated or large.

Here, in the integrated evaporation pressure regulating valve 210 of the present embodiment, as shown in FIG. 10, the width dimension pattern of the first communication hole 212a, the second communication hole 212b, and the third communication hole 212c is changed. .. Therefore, it is not possible to fully open all the inlets of the first inlet 211a, the second inlet 211b, and the third inlet 211c, but the width dimension pattern is not limited to this.

That is, a pattern having a width dimension that allows all the inlets of the first inlet 211a, the second inlet 211b, and the third inlet 211c to be fully opened may be formed. In this case, the operation of (9) parallel dehumidification waste heat recovery mode may be executed.

(Third Embodiment)
In the present embodiment, the refrigeration cycle device 10a applied to the vehicle air conditioner 1a will be described as shown in the overall configuration diagram of FIG.

In FIG. 11, for the sake of clarification, the indoor air conditioning unit 30, the high temperature side heat medium circuit 40, and the low temperature side heat medium circuit 50 are not shown. Therefore, also in the refrigeration cycle device 10a, the water passage of the water-refrigerant heat exchanger 12 is connected to the high temperature side heat medium circuit 40. The water passage of the chiller 19 is connected to the low temperature side heat medium circuit 50. The indoor evaporator 18 is arranged in the casing 31 of the indoor air conditioning unit 30.

In the refrigeration cycle device 10a, the accumulator 21 is abolished and the receiver 23 is adopted. The receiver 23 is a gas-liquid separator on the high-pressure side that separates the gas-liquid of the high-pressure refrigerant flowing out of the heat exchanger that functions as a condenser. Further, the receiver 23 causes a part of the separated liquid-phase refrigerant to flow out to the downstream side, and stores the remaining liquid-phase refrigerant as the surplus refrigerant in the cycle.

The inlet side of the heating expansion valve 14a is connected to one outlet of the first three-way joint 13a of the refrigeration cycle device 10a via the first high-pressure on-off valve 15c and the fifth three-way joint 13e. The inlet side of the receiver 23 is connected to the other outlet of the first three-way joint 13a via the inlet side passage 22c. A second high-pressure on-off valve 15d and a second three-way joint 13b are arranged in the inlet side passage 22c.

The first high-pressure on-off valve 15c is a solenoid valve that opens and closes a refrigerant passage from one outlet of the first three-way joint 13a to one inflow port of the fifth three-way joint 13e. The outlet side of the receiver 23 is connected to the other inflow port of the fifth three-way joint 13e via the outlet side passage 22d. A sixth three-way joint 13f and a second check valve 17b are arranged in the outlet side passage 22d. The inlet side of the fourth three-way joint is connected to the remaining outlet of the sixth three-way joint 13f.

The second check valve 17b allows the refrigerant to flow from the 6th three-way joint 13f side to the fifth three-way joint 13e side, and prohibits the refrigerant from flowing from the fifth three-way joint 13e side to the sixth three-way joint 13f side. doing. In other words, the second check valve 17b allows the refrigerant to flow from the outlet side of the receiver 23 to the inlet side of the heating expansion valve 14a, and allows the refrigerant to flow from the inlet side of the heating expansion valve 14a to the outlet side of the receiver 23. Is prohibited from flowing.

The basic configuration of the fifth three-way joint 13e and the sixth three-way joint 13f is the same as that of the first three-way joint 13a and the like. The basic configurations of the first high-pressure on-off valve 15c and the second high-pressure on-off valve 15d are the same as those of the high-pressure on-off valve 15a and the like described in the first embodiment. The first high-pressure on-off valve 15c and the second high-pressure on-off valve 15d are refrigerant circuit switching portions. The basic configuration of the second check valve 17b is the same as that of the check valve 17 described in the first embodiment. In this embodiment, the check valve 17 described in the first embodiment is referred to as a first check valve 17a for the sake of clarification of the description.

Further, in the refrigeration cycle device 10a, the suction port side of the compressor 11 is connected to the outlet 201d of the integrated evaporation pressure regulating valve 20. Therefore, the compressor 11 sucks in the refrigerant flowing out from the integrated evaporation pressure regulating valve 20.

The configurations of the other refrigeration cycle device 10a and the vehicle air conditioner 1a are the same as those of the refrigeration cycle device 10 and the vehicle air conditioner 1 described in the first embodiment. Further, in the vehicle air conditioner 1a of the present embodiment, (1) cooling mode, (2) cooling battery cooling mode, (4) parallel dehumidifying mode, (5) outside air heating mode, and (6) described in the first embodiment. ) Seven operation modes corresponding to the outside air heating waste heat recovery mode, (8) battery cooling mode, and (9) parallel dehumidification waste heat recovery mode can be executed. The detailed operation of each operation mode will be described below.

(1) Cooling mode In the cooling mode, the control device 60 opens the first high-pressure on-off valve 15c, closes the second high-pressure on-off valve 15d, and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the fully open state, the cooling expansion valve 14b in the throttle state, and the cooling expansion valve 14c in the fully closed state.

Therefore, in the refrigeration cycle device 10a in the cooling mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the expansion valve 14a for heating that is fully open → the outdoor heat exchanger 16 → the first check valve 17a → the receiver 23. → The expansion valve 14b for cooling → the indoor evaporator 18 → the integrated evaporation pressure regulating valve 20 → the compressor 11 are switched to the refrigerant circuit in which the refrigerant circulates in this order.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the throttle opening degree of the cooling expansion valve 14b so that the superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18 approaches a predetermined target superheat degree SHEO.

The control of the other controlled devices is the same as that of the cooling mode of the first embodiment. Therefore, the interior of the vehicle can be cooled as in the first embodiment.

Further, in the refrigerating cycle device 10a in the cooling mode, since the excess refrigerant of the cycle is stored in the receiver 23, the refrigerant on the outlet side of the indoor evaporator 18 can have a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased and the cooling capacity of the blown air can be improved as compared with the cycle in which the excess refrigerant in the cycle is stored in the accumulator.

(2) Cooling Battery Cooling Mode In the cooling battery cooling mode, the control device 60 opens the first high-pressure on-off valve 15c, closes the second high-pressure on-off valve 15d, and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the fully open state, the cooling expansion valve 14b in the throttle state, and the cooling expansion valve 14c in the throttle state.

Therefore, in the refrigerating cycle device 10a in the cooling battery cooling mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the heating expansion valve 14a that is fully open → the outdoor heat exchanger 16 → the first check valve 17a → Refrigerant circulates in the order of receiver 23 → 4th three-way joint 13d → cooling expansion valve 14b → indoor evaporator 18 → integrated evaporation pressure regulating valve 20 → compressor 11. Further, compressor 11 → water-refrigerant heat exchanger 12 → fully open heating expansion valve 14a → outdoor heat exchanger 16 → first check valve 17a → receiver 23 → fourth three-way joint 13d → cooling expansion Refrigerant circulates in the order of valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → compressor 11.

That is, in the refrigerating cycle device 10a in the cooling battery cooling mode, the indoor evaporator 18 and the chiller 19 are switched to the refrigerant circuit connected in parallel with the refrigerant flow.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, in the control device 60, for the cooling expansion valve 14b and the cooling expansion valve 14c, the superheat degree SH of the outlet side refrigerant of the indoor evaporator 18 and the superheat degree SHC of the outlet side refrigerant of the chiller 19 are the same target superheat degree. The opening ratio between the throttle opening of the cooling expansion valve 14b and the throttle opening of the cooling expansion valve 14c is adjusted so as to approach SHEO.

The control of the other controlled devices is the same as that of the cooling battery cooling mode of the first embodiment. Therefore, as in the first embodiment, the vehicle interior can be cooled and the battery 80 can be cooled. At this time, by the action of the integrated evaporation pressure adjusting valve 20, the temperature of the low temperature side heat medium can be adjusted in a wide range of temperatures according to the amount of heat generated by the battery 80 and the like.

Further, in the refrigerating cycle device 10a in the cooling battery cooling mode, the outlet-side refrigerant of the indoor evaporator 18 and the outlet-side refrigerant of the chiller 19 can be provided with a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased, and the cooling capacity of the blown air can be improved. Further, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased, and the cooling capacity of the battery 80 can be improved.

(4) Parallel dehumidification mode In the parallel dehumidification mode, the control device 60 closes the first high-pressure on-off valve 15c, opens the second high-pressure on-off valve 15d, and opens the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the throttled state, and the cooling expansion valve 14c in the fully closed state.

Therefore, in the refrigeration cycle device 10a in the parallel dehumidification mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the inlet side passage 22c → the receiver 23 → the sixth three-way joint 13f of the outlet side passage 22d → the heating expansion valve 14a → The refrigerant circulates in the order of the outdoor heat exchanger 16 → the heating passage 22b → the integrated evaporation pressure regulating valve 20 → the compressor 11. Further, the compressor 11 → the water-refrigerant heat exchanger 12 → the inlet side passage 22c → the receiver 23 → the sixth three-way joint 13f of the outlet side passage 22d → the expansion valve 14b for cooling → the indoor evaporator 18 → the integrated evaporation pressure adjusting valve. The refrigerant circulates in the order of 20 → compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, in the control device 60, for the heating expansion valve 14a and the cooling expansion valve 14b, the heating expansion valve 14a is such that the superheat degree SHE of the refrigerant on the outlet side of the indoor evaporator 18 approaches the same target superheat degree SHEO. The opening ratio between the throttle opening of the cooling expansion valve 14b and the throttle opening of the cooling expansion valve 14b is adjusted.

The control of the other controlled devices is the same as the parallel dehumidification mode of the first embodiment. Therefore, the dehumidifying and heating of the vehicle interior can be performed as in the first embodiment. At this time, by the action of the integrated evaporation pressure adjusting valve 20, the heating capacity of the blown air in the heater core 42 can be adjusted in a wide range according to the target blowing temperature TAO.

Further, in the refrigeration cycle device 10a in the parallel dehumidification mode, the outlet-side refrigerant of the outdoor heat exchanger 16 and the outlet-side refrigerant of the indoor evaporator 18 can be provided with a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and the heating capacity of the blown air can be improved. Further, the amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased, and the cooling capacity of the blown air can be improved.

(5) Outside air heating mode In the outside air heating mode, the control device 60 closes the first high-pressure on-off valve 15c, opens the second high-pressure on-off valve 15d, and opens the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the fully closed state, and the cooling expansion valve 14c in the fully closed state.

Therefore, in the refrigeration cycle device 10a in the outside air heating mode, the compressor 11 → water-refrigerant heat exchanger 12 → inlet side passage 22c → receiver 23 → outlet side passage 22d → heating expansion valve 14a → outdoor heat exchanger 16 → It is switched to the refrigerant circuit in which the refrigerant circulates in the order of the heating passage 22b → the integrated evaporative pressure regulating valve 20 → the compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the throttle opening degree of the heating expansion valve 14a so that the superheat degree SHAO of the refrigerant on the outlet side of the outdoor heat exchanger 16 approaches a predetermined target superheat degree SHAO. The degree of superheat SHA is determined using the second temperature T2 and the second pressure P2.

The control of the other controlled devices is the same as that of the outside air heating mode of the first embodiment. Therefore, the interior of the vehicle can be heated as in the first embodiment.

Further, in the refrigeration cycle device 10a in the outside air heating mode, the outlet-side refrigerant of the outdoor heat exchanger 16 can have a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and the heating capacity of the blown air can be improved.

(6) Outside air heating waste heat recovery mode In the outside air heating waste heat recovery mode, the control device 60 closes the first high-pressure on-off valve 15c, opens the second high-pressure on-off valve 15d, and opens the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in the throttled state, the cooling expansion valve 14b in the fully closed state, and the cooling expansion valve 14c in the throttled state.

Therefore, in the refrigeration cycle device 10a in the outside air heating waste heat recovery mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the inlet side passage 22c → the receiver 23 → the sixth three-way joint 13f of the outlet side passage 22d → expansion for heating. Refrigerant circulates in the order of valve 14a → outdoor heat exchanger 16 → heating passage 22b → integrated evaporation pressure regulating valve 20 → compressor 11. Further, the compressor 11 → the water-refrigerant heat exchanger 12 → the inlet side passage 22c → the receiver 23 → the sixth three-way joint 13f of the outlet side passage 22d → the cooling expansion valve 14c → the chiller 19 → the integrated evaporation pressure adjusting valve 20 → The refrigerant circulates in the order of the compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, in the control device 60, for the heating expansion valve 14a and the cooling expansion valve 14c, the heating expansion valve 14a is throttled so that the superheat degree SHC of the refrigerant on the outlet side of the chiller 19 approaches the same target superheat degree SHCO. The opening ratio between the opening degree and the throttle opening degree of the cooling expansion valve 14c is adjusted.

The control of the other controlled devices is the same as that of the outside air heating waste heat recovery mode of the first embodiment. Therefore, as in the first embodiment, the vehicle interior can be heated and the battery 80 can be cooled. At this time, by the action of the integrated evaporation pressure adjusting valve 20, the heating capacity of the blown air in the heater core 42 is adjusted in a wide range according to the required heating capacity of the blown air while appropriately cooling the battery 80. be able to.

Further, in the refrigeration cycle device 10a in the parallel dehumidification mode, the outlet-side refrigerant of the outdoor heat exchanger 16 and the outlet-side refrigerant of the indoor evaporator 18 can be provided with a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and the heating capacity of the blown air can be improved. Further, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased, and the cooling capacity of the battery 80 can be improved.

(8) Battery cooling mode In the battery cooling mode, the control device 60 opens the first high-pressure on-off valve 15c, closes the second high-pressure on-off valve 15d, and closes the low-pressure on-off valve 15b. Further, the control device 60 sets the heating expansion valve 14a in a fully open state, the cooling expansion valve 14b in a fully closed state, and the cooling expansion valve 14c in a throttled state.

Therefore, in the refrigerating cycle device 10a in the battery cooling mode, the compressor 11 (→ water-refrigerant heat exchanger 12) → the heating expansion valve 14a that is fully open → the outdoor heat exchanger 16 → the receiver 23 → the cooling expansion. Refrigerant circulates in the order of valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, with respect to the cooling expansion valve 14c, the throttle opening of the cooling expansion valve 14c is adjusted so that the superheat degree SHC of the refrigerant on the outlet side of the chiller 19 approaches the target superheat degree SHCO.

The control of the other controlled devices is the same as the battery cooling mode of the first embodiment. Therefore, the battery 80 can be cooled as in the first embodiment.

Further, in the refrigerating cycle device 10a in the battery cooling mode, the refrigerant on the outlet side of the chiller 19 can have a degree of superheat. Therefore, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased, and the cooling capacity of the battery 80 can be improved.

(9) Parallel dehumidifying waste heat recovery mode In the parallel dehumidifying waste heat recovery mode, the control device 60 closes the first high-pressure on-off valve 15c, opens the second high-pressure on-off valve 15d, and opens the low-pressure on-off valve 15b. Further, in the control device 60, the heating expansion valve 14a is in the throttle state, the cooling expansion valve 14b is in the throttle state, and the cooling expansion valve 14c is in the throttle state.

Therefore, in the refrigeration cycle device 10a in the parallel dehumidification waste heat recovery mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the inlet side passage 22c → the receiver 23 → the sixth three-way joint 13f of the outlet side passage 22d → expansion for heating. Refrigerant circulates in the order of valve 14a → outdoor heat exchanger 16 → heating passage 22b → integrated evaporation pressure regulating valve 20 → compressor 11. Further, the compressor 11 → the water-refrigerant heat exchanger 12 → the inlet side passage 22c → the receiver 23 → the sixth three-way joint 13f of the outlet side passage 22d → the fourth three-way joint 13d → the cooling expansion valve 14b → the indoor evaporator 18 → The refrigerant circulates in the order of the integrated evaporation pressure regulating valve 20 → the compressor 11. Further, the compressor 11 → the water-refrigerant heat exchanger 12 → the inlet side passage 22c → the receiver 23 → the sixth three-way joint 13f of the outlet side passage 22d → the fourth three-way joint 13d → the cooling expansion valve 14c → the chiller 19 → the integrated type. The refrigerant circulates in the order of the evaporation pressure adjusting valve 20 → the compressor 11.

In the above-mentioned refrigerant circuit, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the throttle opening degree of the cooling expansion valve 14c so as to have a predetermined reference opening degree. Further, the control device 60 controls the heating expansion valve 14a, the cooling expansion valve 14b, and the integrated evaporation pressure adjusting valve 20 in the same manner as in the parallel dehumidification mode.

The control of the other controlled devices is the same as the parallel dehumidifying waste heat recovery mode of the first embodiment. Therefore, as in the first embodiment, dehumidifying and heating of the vehicle interior and cooling of the battery 80 can be performed. At this time, by the action of the integrated evaporation pressure adjusting valve 20, the heating capacity of the blown air in the heater core 42 can be adjusted in a wide range according to the target blowing temperature TAO.

Further, in the refrigeration cycle device 10a in the parallel dehumidifying waste heat recovery mode, the outlet side refrigerant of the outdoor heat exchanger 16, the outlet side refrigerant of the indoor evaporator 18, and the outlet side refrigerant of the chiller 19 can be provided with a degree of superheat. ..

Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 16 can be increased, and the heating capacity of the blown air can be improved. The amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased, and the cooling capacity of the blown air can be improved. Further, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased, and the cooling capacity of the battery 80 can be improved.

As described above, the refrigeration cycle device 10a of the present embodiment can switch various operation modes. As a result, the vehicle air conditioner 1 can realize comfortable air conditioning in the vehicle interior while appropriately adjusting the temperature of the battery 80. Further, the refrigerating cycle apparatus 10a of the present embodiment can also obtain the same effect as that of the first embodiment.

That is, among a plurality of evaporation parts connected in parallel to each other with respect to the refrigerant flow, the refrigerant evaporation temperature in one evaporation part is appropriately adjusted without being affected by the refrigerant evaporation temperature in another evaporation part. Can be done. Further, it is possible to appropriately adjust the refrigerant evaporation temperature in a plurality of evaporation units connected in parallel with each other without causing the circuit configuration to become complicated or large.

Further, in the refrigerating cycle device 10a of the present embodiment, as described above, the refrigerant on the outlet side of the heat exchanger functioning as the evaporator can have a degree of superheat, so that the refrigerant in the heat exchanger functioning as the evaporator can have a degree of superheat. The amount of heat absorption can be increased. Thereby, the coefficient of performance of the cycle can be improved, and the heating capacity of the blown air, the cooling capacity of the blown air, and the cooling and cooling of the battery 80 can be improved.

(Fourth Embodiment)
In the present embodiment, the refrigeration cycle device 10b applied to the vehicle air conditioner 1b will be described as shown in the overall configuration diagram of FIG. In the refrigeration cycle apparatus 10b, the outdoor heat exchanger 16, the high temperature side heat medium circuit 40, and the low temperature side heat medium circuit 50 are abolished, and the heat medium circuit 90 is adopted. In the refrigeration cycle apparatus 10b, the water-refrigerant heat exchanger 12 and the chiller 19 are connected to the heat medium circuit 90.

The inlet side of the receiver 23 is connected to the outlet of the refrigerant passage of the refrigeration cycle device 10b. The inlet side of the fourth three-way joint 13d is connected to the outlet of the receiver 23. Further, in the refrigeration cycle device 10b, since the outdoor heat exchanger 16 is abolished, the first inlet 201a of the integrated evaporation pressure regulating valve 20 is closed.

As described in the first embodiment, a reed valve (not shown) is arranged at each inlet of the integrated evaporative pressure regulating valve 20. Therefore, in the integrated evaporation pressure regulating valve 20, if nothing is connected to the first inlet 201a, the first inlet 201a can be closed. Of course, a plug or the like may be attached to the first inlet 201a to close the first inlet 201a.

Next, the heat medium circuit 90 is a heat medium circulation circuit that circulates the heat medium. As the heat medium, the same fluid as the high temperature side heat medium or the low temperature side heat medium described in the first embodiment can be adopted.

In the heat medium circuit 90, the water passage of the water-refrigerant heat exchanger 12, the high temperature side heat medium pump 41, the heater core 42, the water passage of the chiller 19, the low temperature side heat medium pump 51, the cooling water passage 80a of the battery 80, and the like. 1 Three-way valve 91a, second three-way valve 91b, radiator 92, first heat medium three-way joint 93a to fourth heat medium three-way joint 93d and the like are arranged. The basic configuration of the first heat medium three-way joint 93a to the fourth heat medium three-way joint 93d is the same as that of the first three-way joint 13a and the like.

In the heat medium circuit 90, the high temperature side heat medium pump 41 sucks in the heat medium flowing out from the water passage of the water-refrigerant heat exchanger 12 and pumps it to the inflow port side of the first three-way valve 91a. The first three-way valve 91a is a three-type switching valve that switches between a flow path for causing the heat medium pumped from the high-temperature side heat medium pump 41 to flow out to the heater core 42 side and a flow path for flowing out to the radiator 92 side. The operation of the first three-way valve 91a is controlled by the control voltage output from the control device 60.

The heat medium inlet side of the heater core 42 is connected to one outlet of the first three-way valve 91a. One inflow port side of the first heat medium three-way joint 93a is connected to the other outflow port of the first three-way valve 91a.

In the heat medium circuit 90, the low temperature side heat medium pump 51 sucks in the heat medium flowing out from the water passage of the chiller 19 and pumps it to the inflow port side of the second three-way valve 91b. The second three-way valve 91b is a three-type switching valve that switches between a flow path for causing the heat medium pumped from the low-temperature side heat medium pump 51 to flow out to the heater core 42 side and a flow path for flowing out to the radiator 92 side. The basic configuration of the second three-way valve 91b is the same as that of the first three-way valve 91a.

The inlet side of the cooling water passage 80a of the battery 80 is connected to one outlet of the second three-way valve 91b. The other inlet side of the first heat medium three-way joint 93a is connected to the other outlet of the second three-way valve 91b. The refrigerant inlet side of the radiator 92 is connected to the outlet of the first heat medium three-way joint 93a.

The radiator 92 is a heat exchanger that exchanges heat between a heat medium and the outside air blown by a cooling fan (not shown). The radiator 92 is arranged on the front side in the drive unit room, similarly to the outdoor heat exchanger 16 described in the first embodiment. The inlet side of the second heat medium three-way joint 93b is connected to the refrigerant outlet of the radiator 92.

One inflow port side of the third heat medium three-way joint 93c is connected to one outflow port of the second heat medium three-way joint 93b. The heat medium outlet side of the heater core 42 is connected to the other inflow port of the third heat medium three-way joint 93c. The inlet side of the water passage of the water-refrigerant heat exchanger 12 is connected to the outlet of the third heat medium three-way joint 93c.

One inlet side of the fourth heat medium three-way joint 93d is connected to the other outlet of the second heat medium three-way joint 93b. The outlet side of the cooling water passage 80a of the battery 80 is connected to the other inflow port of the fourth heat medium three-way joint 93d. The inlet side of the water passage of the chiller 19 is connected to the outlet of the fourth heat medium three-way joint 93d.

Therefore, when the first three-way valve 91a causes the heat medium to flow out to the heater core 42 side while the high temperature side heat medium pump 41 is operated, the heat medium is circulated between the water-refrigerant heat exchanger 12 and the heater core 42. Can be made to. Therefore, the heater core 42 can exchange heat between the heat medium and the blown air. That is, the heater core 42 can heat the blown air by radiating the heat of the heat medium to the blown air.

On the other hand, when the first three-way valve 91a causes the heat medium to flow out to the radiator 92 side while the high temperature side heat medium pump 41 is operated, the heat medium is circulated between the water-refrigerant heat exchanger 12 and the radiator 92. Can be made to. Therefore, the radiator 92 can exchange heat between the heat medium and the outside air. More specifically, the radiator 92 can dissipate the heat of the heat medium to the outside air.

Further, when the second three-way valve 91b causes the heat medium to flow out to the cooling water passage 80a side of the battery 80 while the low temperature side heat medium pump 51 is operated, between the chiller 19 and the cooling water passage 80a of the battery 80. The heat medium can be circulated with. Therefore, the heat medium and the battery 80 can be exchanged for heat in the cooling water passage 80a of the battery 80. More specifically, the battery can be cooled by the heat medium cooled by the chiller 19.

On the other hand, when the second three-way valve 91b causes the heat medium to flow out to the radiator 92 side while the low temperature side heat medium pump 51 is operated, the heat medium can be circulated between the chiller 19 and the radiator 92. Therefore, the radiator 92 can exchange heat between the heat medium and the outside air. More specifically, the radiator 92 can allow the heat medium cooled by the chiller 19 to absorb the heat of the outside air.

Here, in the control device 60 of the present embodiment, the heat medium discharged from the high temperature side heat medium pump 41 and the heat medium discharged from the low temperature side heat medium pump 51 are first flowed into the radiator 92 at the same time. It does not control the operation of the three-way valve 91a and the second three-way valve 91b.

The other configurations of the refrigeration cycle device 10b and the vehicle air conditioner 1b are the same as those of the refrigeration cycle device 10 and the vehicle air conditioner 1 described in the first embodiment. Further, in the vehicle air conditioner 1b of the present embodiment, (1) cooling mode, (2) cooling battery cooling mode, (3) series dehumidification mode, (4) parallel dehumidification mode, and (5) described in the first embodiment. It is possible to execute seven operation modes: (7) waste heat recovery heating mode, and (8) operation mode corresponding to the battery cooling mode. The detailed operation of each operation mode will be described below.

(1) Cooling mode In the cooling mode, the control device 60 sets the cooling expansion valve 14b in the throttled state and the cooling expansion valve 14c in the fully closed state. Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity. Further, the control device 60 controls the operation of the first three-way valve 91a so that the heat medium discharged from the high temperature side heat medium pump 41 flows into the radiator 92.

Therefore, in the refrigeration cycle device 10b in the cooling mode, the compressor 11 → the water-refrigerant heat exchanger 12 → the receiver 23 → the expansion valve 14b for cooling → the indoor evaporator 18 → the integrated evaporation pressure regulating valve 20 → the compressor 11. It is switched to the refrigerant circuit in which the refrigerant circulates in order. In the heat medium circuit 90 in the cooling mode, the circuit is switched to a circuit in which the heat medium circulates in the order of the high temperature side heat medium pump 41 → the radiator 92 → the water passage of the water-refrigerant heat exchanger 12 → the high temperature side heat medium pump 41.

With the above circuit configuration, the control device 60 appropriately controls the operation of various controlled devices, as in the cooling mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b in the cooling mode, a steam compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the indoor evaporator 18 functions as an evaporation unit. As a result, in the refrigerating cycle device 10b in the cooling mode, the heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18.

In the heat medium circuit 90 in the cooling mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air and dissipates heat to the outside air.

In the indoor air conditioning unit 30 in the cooling mode, the blown air cooled by the indoor evaporator 18 can be blown out into the vehicle interior. As a result, the interior of the vehicle can be cooled.

Further, in the cooling mode refrigeration cycle device 10b, since the excess refrigerant of the cycle is stored in the receiver 23, the cooling capacity of the blown air can be improved as in the third embodiment.

(2) Cooling Battery Cooling Mode In the cooling battery cooling mode, the control device 60 sets the cooling expansion valve 14b in the throttled state and the cooling expansion valve 14c in the throttled state. Further, the control device 60 operates the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Further, the control device 60 controls the operation of the first three-way valve 91a so that the heat medium discharged from the high temperature side heat medium pump 41 flows into the radiator 92. Further, the control device 60 controls the operation of the second three-way valve 91b so that the heat medium discharged from the low temperature side heat medium pump 51 flows into the cooling water passage 80a of the battery 80.

Therefore, in the refrigerating cycle device 10b in the cooling battery cooling mode, the compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → fourth three-way joint 13d → cooling expansion valve 14b → indoor evaporator 18 → integrated evaporation pressure. The refrigerant circulates in the order of the regulating valve 20 → the compressor 11. Further, the refrigerant circulates in the order of compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → fourth three-way joint 13d → cooling expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → compressor 11.

That is, in the refrigerating cycle device 10b in the cooling battery cooling mode, the indoor evaporator 18 and the chiller 19 are switched to the refrigerant circuit connected in parallel with the refrigerant flow.

In the heat medium circuit 90 in the cooling battery cooling mode, the heat medium circulates in the order of the high temperature side heat medium pump 41 → the radiator 92 → the water passage of the water-refrigerant heat exchanger 12 → the high temperature side heat medium pump 41. Further, the circuit is switched to a circuit in which the heat medium circulates in the order of the low temperature side heat medium pump 51 → the cooling water passage 80a of the battery 80 → the chiller 19 → the low temperature side heat medium pump 51.

With the above circuit configuration, the control device 60 appropriately controls the operation of various controlled devices, as in the cooling battery cooling mode of the third embodiment.

Therefore, in the refrigerating cycle device 10b in the cooling battery cooling mode, a steam compression type refrigerating cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the indoor evaporator 18 and the chiller 19 function as evaporating units. .. As a result, in the refrigerating cycle device 10b in the cooling battery cooling mode, the heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18. The heat medium can be cooled by the chiller 19.

In the heat medium circuit 90 in the cooling battery cooling mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air and dissipates heat to the outside air. The heat medium cooled by the chiller 19 circulates in the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled.

In the indoor air conditioning unit 30 in the cooling battery cooling mode, the blown air cooled by the indoor evaporator 18 can be blown out into the vehicle interior. As a result, the interior of the vehicle can be cooled.

Further, in the cooling battery cooling mode, the refrigerant evaporation pressure in the chiller 19 can be adjusted to a value higher or lower than the refrigerant evaporation pressure in the indoor evaporator 18 by the action of the integrated evaporation pressure adjusting valve 20. can. Therefore, the temperature of the heat medium flowing into the cooling water passage 80a can be adjusted in a wide range of temperatures according to the amount of heat generated by the battery 80 and the like.

Further, in the refrigerating cycle device 10b in the cooling battery cooling mode, since the excess refrigerant of the cycle is stored in the receiver 23, the cooling capacity of the blown air and the cooling capacity of the battery 80 can be improved as in the third embodiment.

(3) First Dehumidifying / Heating Mode In the first dehumidifying / heating mode, the control device 60 sets the cooling expansion valve 14b in a throttled state and the cooling expansion valve 14c in a fully closed state. Further, the control device 60 operates the high temperature side heat medium pump 41 so as to exert a predetermined pumping capacity. Further, the control device 60 controls the operation of the first three-way valve 91a so that the heat medium discharged from the high temperature side heat medium pump 41 flows into the heater core 42.

Therefore, in the refrigeration cycle device 10b in the first dehumidification / heating mode, the compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → cooling expansion valve 14b → indoor evaporator 18 → integrated evaporation pressure regulating valve 20 → compression. It is switched to the refrigerant circuit in which the refrigerant circulates in the order of the machine 11. In the heat medium circuit 90 of the first dehumidifying / heating mode, the circuit is switched to a circuit in which the heat medium circulates in the order of the high temperature side heat medium pump 41 → the heater core 42 → the water passage of the water-refrigerant heat exchanger 12 → the high temperature side heat medium pump 41. ..

With the above circuit configuration, the control device 60 appropriately controls the operation of various controlled devices, as in the cooling mode of the third embodiment.

Therefore, in the refrigerating cycle device 10b in the first dehumidifying / heating mode, a steam compression type refrigerating cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the indoor evaporator 18 functions as an evaporating unit. As a result, in the refrigeration cycle device 10b in the first dehumidification / heating mode, the heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18.

In the heat medium circuit 90 in the first dehumidifying and heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42.

In the indoor air conditioning unit 30 in the first dehumidifying and heating mode, a part of the blown air cooled by the indoor evaporator 18 is reheated by the heater core 42, and the temperature of the blown air is adjusted so as to approach the target blowing temperature TAO. Can be blown into the passenger compartment. This makes it possible to perform dehumidifying and heating in the vehicle interior.

Further, in the refrigerating cycle device 10b in the first dehumidifying and heating mode, the excess refrigerant of the cycle is stored in the receiver 23, so that the cooling capacity of the blown air can be improved as in the third embodiment.

(4) Second parallel dehumidification mode (corresponding to the parallel dehumidification mode of the first embodiment)
In the second dehumidifying / heating mode, the control device 60 puts the cooling expansion valve 14b in the throttled state and the cooling expansion valve 14c in the throttled state. Further, the control device 60 operates the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Further, the control device 60 controls the operation of the first three-way valve 91a so that the heat medium discharged from the high temperature side heat medium pump 41 flows into the heater core 42. Further, the control device 60 controls the operation of the second three-way valve 91b so that the heat medium discharged from the low temperature side heat medium pump 51 flows into the radiator 92.

Therefore, in the refrigeration cycle device 10b in the second parallel dehumidification mode, the compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → fourth three-way joint 13d → cooling expansion valve 14b → indoor evaporator 18 → integrated evaporation. The refrigerant circulates in the order of the pressure regulating valve 20 → the compressor 11. Further, the refrigerant circulates in the order of compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → fourth three-way joint 13d → cooling expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → compressor 11.

That is, in the refrigeration cycle device 10b in the second parallel dehumidification mode, the indoor evaporator 18 and the chiller 19 are switched to the refrigerant circuit connected in parallel with the refrigerant flow.

In the heat medium circuit 90 in the second parallel dehumidification mode, the heat medium circulates in the order of the high temperature side heat medium pump 41 → the heater core 42 → the water passage of the water-refrigerant heat exchanger 12 → the high temperature side heat medium pump 41. Further, the circuit is switched to a circuit in which the heat medium circulates in the order of the low temperature side heat medium pump 51 → radiator 92 → chiller 19 → low temperature side heat medium pump 51.

With the above circuit configuration, the control device 60 appropriately controls the operation of various controlled devices. For example, the control device 60 controls the compressor 11 in the same manner as in the parallel dehumidification mode of the third embodiment. The control of the other controlled devices is the same as that of the cooling battery cooling mode of the third embodiment.

Therefore, in the refrigerating cycle device 10b in the second dehumidifying / heating mode, a steam compression type refrigerating cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the indoor evaporator 18 and the chiller 19 function as an evaporating unit. NS. As a result, in the refrigeration cycle device 10b in the second dehumidification / heating mode, the heat medium can be heated by the water-refrigerant heat exchanger 12. The blown air can be cooled by the indoor evaporator 18. The heat medium can be cooled by the chiller 19.

In the heat medium circuit 90 in the second dehumidifying and heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42. The heat medium cooled by the chiller 19 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air and absorbs heat from the outside air.

In the indoor air conditioning unit 30 in the second dehumidifying / heating mode, the blown air cooled by the indoor evaporator 18 is reheated by the heater core 42, and the blown air whose temperature is adjusted so as to approach the target blowing temperature TAO is supplied to the passenger compartment. Can be blown out to. This makes it possible to perform dehumidifying and heating in the vehicle interior.

Further, in the second dehumidifying / heating mode, the refrigerant evaporation pressure in the chiller 19 is adjusted to a value higher or lower than the refrigerant evaporation pressure in the indoor evaporator 18 by the action of the integrated evaporation pressure adjusting valve 20. Can be done. Therefore, the amount of heat absorbed from the outside air of the heat medium in the radiator 92 can be adjusted according to the target blowing temperature TAO, and the heating capacity of the blown air in the heater core 42 can be adjusted in a wide range.

Further, in the refrigeration cycle device 10b in the second parallel dehumidification mode, since the excess refrigerant of the cycle is stored in the receiver 23, the heat absorption amount in the chiller 19 can be increased, and the heating capacity of the blown air can be improved. Further, the amount of heat absorbed by the refrigerant in the indoor evaporator 18 can be increased, and the cooling capacity of the blown air can be improved.

(5) Outside air heating mode In the outside air heating mode, the control device 60 sets the cooling expansion valve 14b in a fully closed state and the cooling expansion valve 14c in a throttled state. Further, the control device 60 operates the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Further, the control device 60 controls the operation of the first three-way valve 91a so that the heat medium discharged from the high temperature side heat medium pump 41 flows into the heater core 42. Further, the control device 60 controls the operation of the second three-way valve 91b so that the heat medium discharged from the low temperature side heat medium pump 51 flows into the radiator 92.

Therefore, in the refrigerating cycle device 10b in the outside air heating mode, the compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → cooling expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → compressor 11 in this order. Refrigerant circulates.

In the heat medium circuit 90 in the outside air heating mode, the heat medium circulates in the order of the high temperature side heat medium pump 41 → the radiator 92 → the water passage of the water-refrigerant heat exchanger 12 → the high temperature side heat medium pump 41. Further, the circuit is switched to a circuit in which the heat medium circulates in the order of the low temperature side heat medium pump 51 → radiator 92 → chiller 19 → low temperature side heat medium pump 51.

With the above circuit configuration, the control device 60 appropriately controls the operation of various controlled devices. For example, with respect to the cooling expansion valve 14c, the throttle opening of the cooling expansion valve 14c is adjusted so that the superheat degree SHC of the refrigerant on the outlet side of the chiller 19 approaches the target superheat degree SHCO. The control of the other controlled devices is the same as that of the outside air heating mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b in the outside air heating mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the chiller 19 functions as an evaporation unit. As a result, in the refrigeration cycle device 10b in the outside air heating mode, the heat medium can be heated by the water-refrigerant heat exchanger 12. The heat medium can be cooled by the chiller 19. In other words, the refrigerant can endothermic the heat of the heat medium.

In the heat medium circuit 90 in the outside air heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42. The heat medium cooled by the chiller 19 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air and absorbs heat from the outside air.

In the indoor air conditioning unit 30 in the outside air heating mode, the blown air heated by the heater core 42 can be blown out into the vehicle interior. As a result, the interior of the vehicle can be heated by using the heat absorbed from the outside air as a heat source.

Further, in the refrigerating cycle device 10b in the outside air heating mode, the refrigerant on the outlet side of the chiller 19 can have a degree of superheat. Therefore, as in the third embodiment, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased, and the heating capacity of the blown air can be improved.

(7) Waste Heat Recovery and Heating Mode In the waste heat recovery and heating mode, the control device 60 sets the cooling expansion valve 14b in a fully closed state and the cooling expansion valve 14c in a throttled state. Further, the control device 60 operates the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Further, the control device 60 controls the operation of the first three-way valve 91a so that the heat medium discharged from the high temperature side heat medium pump 41 flows into the heater core 42. Further, the control device 60 controls the operation of the second three-way valve 91b so that the heat medium discharged from the low temperature side heat medium pump 51 flows into the cooling water passage 80a of the battery 80.

Therefore, in the refrigerating cycle device 10b in the waste heat recovery heating mode, the compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → cooling expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → compressor 11 The refrigerant circulates in this order.

In the heat medium circuit 90 in the waste heat recovery heating mode, the heat medium circulates in the order of the high temperature side heat medium pump 41 → the heater core 42 → the water passage of the water-refrigerant heat exchanger 12 → the high temperature side heat medium pump 41. Further, the circuit is switched to a circuit in which the heat medium circulates in the order of the low temperature side heat medium pump 51 → the cooling water passage 80a of the battery 80 → the chiller 19 → the low temperature side heat medium pump 51.

With the above circuit configuration, the control device 60 appropriately controls the operation of various controlled devices as in the outside air heating mode.

Therefore, in the refrigeration cycle device 10b in the waste heat recovery heating mode, a steam compression type refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the chiller 19 functions as an evaporation unit. As a result, in the refrigeration cycle device 10b in the waste heat recovery heating mode, the heat medium can be heated by the water-refrigerant heat exchanger 12. The heat medium can be cooled by the chiller 19.

In the heat medium circuit 90 in the waste heat recovery heating mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 42. The heat medium cooled by the chiller 19 circulates in the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled. In other words, the heat medium can absorb the waste heat of the battery 80.

In the indoor air conditioning unit 30 in the waste heat recovery heating mode, the blown air heated by the heater core 42 can be blown out into the vehicle interior. As a result, the interior of the vehicle can be heated using the heat absorbed from the battery 80 as a heat source.

Further, in the refrigerating cycle device 10b in the waste heat recovery heating mode, the outlet-side refrigerant of the chiller 19 can have a degree of superheat. Therefore, similarly to the outside air heating mode, the amount of heat absorbed by the refrigerant in the chiller 19 can be increased, and the heating capacity of the blown air can be improved.

(8) Battery cooling mode In the battery cooling mode, the control device 60 sets the cooling expansion valve 14b in a fully closed state and the cooling expansion valve 14c in a throttled state. Further, the control device 60 operates the high temperature side heat medium pump 41 and the low temperature side heat medium pump 51 so as to exert a predetermined pumping capacity.

Further, the control device 60 controls the operation of the first three-way valve 91a so that the heat medium discharged from the high temperature side heat medium pump 41 flows into the radiator 92. Further, the control device 60 controls the operation of the second three-way valve 91b so that the heat medium discharged from the low temperature side heat medium pump 51 flows into the cooling water passage 80a of the battery 80.

Therefore, in the refrigerating cycle device 10b in the battery cooling mode, the order is compressor 11 → water-refrigerant heat exchanger 12 → receiver 23 → cooling expansion valve 14c → chiller 19 → integrated evaporation pressure regulating valve 20 → compressor 11. Refrigerant circulates.

In the heat medium circuit 90 in the battery cooling mode, the heat medium circulates in the order of the high temperature side heat medium pump 41 → the radiator 92 → the water passage of the water-refrigerant heat exchanger 12 → the high temperature side heat medium pump 41. Further, the circuit is switched to a circuit in which the heat medium circulates in the order of the low temperature side heat medium pump 51 → the cooling water passage 80a of the battery 80 → the chiller 19 → the low temperature side heat medium pump 51.

With the above circuit configuration, the control device 60 appropriately controls the operation of various controlled devices, as in the battery cooling mode of the third embodiment.

Therefore, in the refrigeration cycle device 10b in the battery cooling mode, a vapor compression refrigeration cycle is configured in which the water-refrigerant heat exchanger 12 functions as a condensing unit and the chiller 19 functions as an evaporation unit. As a result, in the refrigeration cycle device 10b in the outside air heating mode, the heat medium can be heated by the water-refrigerant heat exchanger 12. The heat medium can be cooled by the chiller 19.

In the heat medium circuit 90 in the battery cooling mode, the heat medium heated by the water-refrigerant heat exchanger 12 flows into the radiator 92. The heat medium flowing into the radiator 92 exchanges heat with the outside air and dissipates heat to the outside air. The heat medium cooled by the chiller 19 circulates in the cooling water passage 80a of the battery 80. As a result, the battery 80 can be cooled.

Further, in the refrigerating cycle device 10b in the battery cooling mode, since the excess refrigerant of the cycle is stored in the receiver 23, the amount of heat absorbed by the chiller 19 can be increased, and the heating capacity of the blown air can be improved.

As described above, the refrigeration cycle device 10b of the present embodiment can switch various operation modes. As a result, the vehicle air conditioner 1 can realize comfortable air conditioning in the vehicle interior while appropriately adjusting the temperature of the battery 80.

Further, even in the refrigeration cycle device 10b provided with two heat exchangers functioning as evaporation units as in the present embodiment, by adopting the integrated evaporation pressure adjusting valve 20, the same as in the first embodiment. The effect can be obtained.

That is, among a plurality of evaporation parts connected in parallel to each other with respect to the refrigerant flow, the refrigerant evaporation temperature in one evaporation part is appropriately adjusted without being affected by the refrigerant evaporation temperature in another evaporation part. Can be done. Further, it is possible to appropriately adjust the refrigerant evaporation temperature in a plurality of evaporation units connected in parallel with each other without causing the circuit configuration to become complicated or large.

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

(1) In the above-described embodiment, an example in which the refrigeration cycle devices 10 to 10b according to the present invention are applied to a vehicle air conditioner mounted on an electric vehicle has been described, but the present invention is not limited thereto. For example, it may be applied to a vehicle air conditioner mounted on a so-called hybrid vehicle that obtains a driving force for vehicle traveling from both an internal combustion engine and a traveling electric motor.

Further, in the above-described embodiment, an example of cooling the battery 80 as a cooling object has been described, but the present invention is not limited to this. For example, an in-vehicle device that generates heat during operation, such as an electric motor for traveling that outputs a driving force for traveling, an inverter that supplies electric power to the electric motor, and a transformer accrus that is a power transmission mechanism, may be objects to be cooled.

Further, the application of the refrigeration cycle devices 10 to 10b is not limited to that for vehicles. For example, in the above-described embodiment, it may be applied to a stationary air conditioner that air-conditions a computer server room. In this case, the computer server may be the object to be cooled.

(2) The configuration of the refrigeration cycle apparatus 10 to 10b is not limited to that disclosed in the above-described embodiment.

For example, in the above-mentioned first to third embodiments, an example in which a heating unit for heating the blown air is configured by each component device of the water-refrigerant heat exchanger 12 and the high temperature side heat medium circuit 40 has been described. Not limited to. For example, as shown in FIG. 13, the high temperature side heat medium circuit 40 may be abolished and the indoor condenser 121 may be adopted.

The indoor condenser 121 is a heating heat exchanger that heats the blown air by exchanging heat between the refrigerant discharged from the compressor 11 and the blown air blown into the vehicle interior. The indoor condenser 121 may be arranged in the casing 31 of the indoor air conditioning unit 30 in the same manner as the heater core 42.

Further, in the first to third embodiments described above, an example in which a cooling unit for cooling an object to be cooled is configured by each component device of the chiller 19 and the low temperature side heat medium circuit 50 has been described, but the present invention is not limited to this. For example, as shown in FIG. 13, the high-temperature side heat medium circuit 40 may be abolished so that the low-pressure refrigerant decompressed by the cooling expansion valve 14c is directly circulated through the cooling water passage 80a of the battery 80. In this case, the cooling water passage 80a serves as a cooling heat exchange section.

In addition to this, a cooling evaporator may be adopted as the evaporation unit. The cooling evaporator is a cooling heat exchanger that cools the cooling blast air by exchanging heat between the low-pressure refrigerant decompressed by the cooling expansion valve 14c and the cooling blast air blown on the object to be cooled. be.

Further, in the above-described first embodiment, the low temperature side heat medium is cooled by the chiller 19 to simultaneously cool the battery 80 and recover the waste heat of the battery 80, but the present invention is not limited to this. For example, a cooling heat exchanger that evaporates the low-pressure refrigerant exclusively for cooling the battery 80 and a heat absorption heat exchanger that evaporates the refrigerant exclusively for recovering the waste heat of the battery 80 may be provided.

Further, in the above-described embodiment, an example in which R1234yf is adopted as the refrigerant of the refrigeration cycle device 10 has been described, but the present invention is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C and the like may be adopted. Alternatively, a mixed refrigerant or the like in which a plurality of these refrigerants are mixed may be adopted.

Further, in the above-described embodiment, an example in which an ethylene glycol aqueous solution is used as the heat medium of the high temperature side heat medium circuit 40, the low temperature side heat medium circuit 50, and the heat medium circuit 90 has been described, but the present invention is not limited thereto. For example, dimethylpolysiloxane, a solution containing nanofluid or the like, an antifreeze liquid, an aqueous liquid refrigerant containing alcohol or the like, a liquid medium containing oil or the like may be adopted.

(3) The evaporation pressure adjusting unit is not limited to the integrated evaporation pressure adjusting valves 20 and 210 disclosed in the above-described embodiment. For example, in the above-described embodiment, the example having three inlets has been described, but the evaporation pressure adjusting unit having four or more inlets may be used.

Further, the integrated evaporation pressure adjusting valves 20 and 210 may have a mounting portion for mounting a sensor for air conditioning control. Specifically, even if it has a mounting portion for mounting the second refrigerant temperature sensor 64b, the third refrigerant temperature sensor 64c, the second refrigerant temperature sensor 64b, the third refrigerant pressure sensor 65c, the fourth refrigerant pressure sensor 65d, and the like. good.

(4) The means disclosed in each of the above-described embodiments may be appropriately combined to the extent practicable.

For example, the integrated evaporation pressure regulating valve 210 described in the second embodiment may be applied to the refrigeration cycle devices 10a and 10b described in the third and fourth embodiments.

For example, the indoor condenser 121 and the cooling evaporator described above may be applied to the refrigeration cycle apparatus 10a described in the third embodiment.

11 Compressors 14a-14c Expansion valve for heating, expansion valve for cooling, expansion valve for cooling (blocking part)
15a to 15d High-pressure on-off valve, low-pressure on-off valve, first high-pressure on-off valve, second high-pressure on-off valve 16 Outdoor heat exchanger (evaporation part)
18 Indoor evaporator (evaporator)
19 chiller (evaporation part, heat exchange part for cooling)
20, 210 Integrated evaporation pressure adjustment valve (evaporation pressure adjustment unit)
80 battery (cooling object)
80a Cooling water passage (evaporation part)

Claims (7)

Multiple evaporators (16, 18, 19) that evaporate the refrigerant,
Evaporation pressure adjusting units (20, 210) arranged on the downstream side of the refrigerant flow of the plurality of evaporation units and adjusting the refrigerant evaporation pressure in the plurality of evaporation units,
A refrigerant circuit switching unit (15a, 15b) for switching the refrigerant circuit is provided.
There are at least three or more of the plurality of evaporation parts, and there are three or more.
When any one of the plurality of evaporation parts is defined as the first evaporation part and the other one is defined as the second evaporation part,
The refrigerant circuit switching unit connects the first evaporation unit and the second evaporation unit in parallel to the refrigerant flow when the refrigerant is evaporated by the first evaporation unit and the second evaporation unit. Switch to the circuit,
The evaporating pressure adjusting unit is a refrigerating cycle apparatus capable of adjusting the refrigerant evaporation pressure in the first evaporating unit to a value higher or lower than the refrigerant evaporating pressure in the second evaporating unit. Further, when one of the plurality of evaporation parts different from the first evaporation part and the second evaporation part is defined as the third evaporation part,
When the refrigerant is evaporated by the first evaporating unit, the second evaporating unit, and the third evaporating unit, the refrigerant circuit switching unit includes the first evaporating unit, the second evaporating unit, and the third evaporating unit. In parallel with the refrigerant flow
The claim that the evaporation pressure adjusting section adjusts the refrigerant evaporation pressure in the third evaporation section to be equal to the lower of the refrigerant evaporation pressure in the first evaporation section and the refrigerant evaporation pressure in the second evaporation section. The refrigeration cycle apparatus according to 1. The refrigerant circuit switching unit has a blocking unit (14a to 14c) that blocks the inflow of the refrigerant into the third evaporation unit when the refrigerant is evaporated by the first evaporation unit and the second evaporation unit. The refrigeration cycle apparatus according to claim 2. The plurality of evaporative units include an outdoor heat exchanger (16) that exchanges heat between the refrigerant and the outside air, an indoor evaporator (18) that exchanges heat between the refrigerant and the blown air blown to the air-conditioned space, and cooling. The refrigeration cycle apparatus according to any one of claims 1 to 3, further comprising a cooling heat exchange unit (19, 80a) that evaporates the refrigerant to cool the object (80). The evaporation pressure adjusting unit is a single opening degree adjusting unit that adjusts the passage cross-sectional area of a plurality of refrigerant passages (201a to 201c, 211a to 211c) through which the refrigerant flowing out from the plurality of evaporation units is circulated. 202, 212), and the refrigeration cycle apparatus according to any one of claims 1 to 4, which has a drive unit (203, 213) for displacing the opening degree adjusting unit. Multiple evaporators (16, 18, 19) that evaporate the refrigerant,
Evaporation pressure adjusting units (20, 210), which are arranged on the downstream side of the refrigerant flow of the plurality of evaporation units and adjust the refrigerant evaporation pressure in the plurality of evaporation units, are provided.
The plurality of evaporation units are connected in parallel with each other with respect to the refrigerant flow.
When any one of the plurality of evaporation parts is defined as the first evaporation part and the other one is defined as the second evaporation part,
The evaporation pressure adjusting unit is configured so that the refrigerant evaporation pressure in the first evaporation unit can be adjusted to either a value higher or lower than the refrigerant evaporation pressure in the second evaporation unit.
The evaporation pressure adjusting unit is a single opening degree adjusting unit that adjusts the passage cross-sectional area of a plurality of refrigerant passages (201a to 201c, 211a to 211c) through which the refrigerant flowing out from the plurality of evaporation units is circulated. 202, 212), and a refrigeration cycle apparatus having a drive unit (203, 213) that displaces the opening degree adjusting unit. A compressor (11) for compressing and discharging the refrigerant flowing out from the evaporation pressure adjusting unit is provided.
The invention according to any one of claims 1 to 6, wherein the evaporation pressure adjusting unit has a backflow prevention function for prohibiting the flow of the refrigerant from the suction port side of the compressor to the plurality of evaporation units. Refrigeration cycle equipment.

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