JP7059966B2 - Refrigeration cycle device - Google Patents

Description

The present invention relates to a refrigeration cycle apparatus formed so that the circuit configuration of a refrigerant circuit can be switched.

Conventionally, Patent Document 1 discloses a refrigerating cycle device formed so that the circuit configuration of a refrigerant circuit can be switched. The refrigerating cycle device of Patent Document 1 is mounted on an electric vehicle to air-condition the interior of the vehicle and cool a battery or the like.

More specifically, the refrigerant circuit of the refrigeration cycle device of Patent Document 1 includes an indoor heat exchanger that exchanges heat between the refrigerant and the blown air blown into the vehicle interior, and a refrigerant circuit switching unit that switches the circuit configuration of the refrigerant circuit. Four-way valve etc. are arranged. Then, in the cooling mode for cooling the interior of the vehicle, the circuit configuration is switched to allow the low-pressure refrigerant to flow into the indoor heat exchanger. Further, in the heating mode for heating the interior of the vehicle, the circuit configuration is switched to allow the high-pressure refrigerant to flow into the indoor heat exchanger.

Further, the refrigerating cycle device of Patent Document 1 has a plurality of refrigerant supply paths for supplying a low-pressure refrigerant to a cooling device for cooling a battery or a traveling motor. Then, by switching the refrigerant supply path to be used according to the operation mode such as the cooling mode and the heating mode, the battery and the traveling motor can be reliably cooled.

Japanese Patent No. 5693495

By the way, in a refrigerating cycle device such as the refrigerating cycle device of Patent Document 1 in which a refrigerant flows into the same indoor heat exchanger regardless of the operation mode, the operating efficiency of the refrigerating cycle device is lowered in some operation modes. There is a possibility that it will end up. The reason is that in this type of refrigeration cycle device, the operating conditions such as the flow rate of the circulating refrigerant circulating in the refrigerant circuit and the air volume of the blown air that exchanges heat with the refrigerant in the indoor heat exchanger differ depending on the operation mode.

Therefore, for example, even if an indoor heat exchanger having appropriate specifications capable of exhibiting high heat exchange efficiency in the cooling mode is adopted, this indoor heat exchanger may not always be able to exhibit high heat exchange efficiency in the heating mode. .. Furthermore, there is a possibility that the operating efficiency of the refrigeration cycle device will decrease in the heating mode.

On the other hand, there are a plurality of indoor heat exchangers for cooling with appropriate specifications that can exhibit high heat exchange efficiency in the cooling mode, and indoor heat exchangers for heating with appropriate specifications that can exhibit high heat exchange efficiency in the heating mode. A means of adopting an indoor heat exchanger can be considered. According to this, by switching the indoor heat exchanger to be used according to the operation mode, it is possible to suppress a decrease in the operating efficiency of the refrigeration cycle device when the operation mode is switched.

However, in order to switch the indoor heat exchanger to be used according to the operation mode, a dedicated refrigerant circuit switching unit is required. Therefore, the cycle configuration is complicated and the control mode of the refrigerant circuit switching unit is complicated. Further, the refrigerating cycle device of Patent Document 1 also requires a dedicated refrigerant circuit switching unit for switching the refrigerant supply path to be used according to the operation mode. Therefore, the cycle configuration and the control mode of the switching unit become more complicated.

In view of the above points, it is an object of the present invention to provide a refrigerating cycle apparatus having a simple configuration and capable of switching the circuit configuration of a refrigerant circuit without causing a decrease in operating efficiency.

In order to achieve the above object, the refrigerating cycle apparatus according to claim 1 includes a compressor (11) that compresses and discharges the refrigerant, an outdoor heat exchanger (13) that exchanges heat between the refrigerant and the outside air, and a refrigerant. A water-refrigerant heat exchanger (14) that exchanges heat between the refrigerant and the heat medium, an indoor evaporator (15) that exchanges heat between the refrigerant and the blown air blown to the air-conditioned space, and a first expansion that reduces the pressure of the refrigerant. A valve (17a), a second expansion valve (17b) for reducing the pressure of the refrigerant flowing into the indoor evaporator, and a heating unit (24) for heating the blown air using the heat medium flowing out from the water-refrigerant heat exchanger as a heat source. , A refrigerant circuit switching unit (12, 18a, 18b) for switching the circuit configuration of the refrigerant circuit (10) for circulating the refrigerant is provided.

One refrigerant inlet / outlet (137b) of the outdoor heat exchanger is connected to a first merging / branching portion (16a) that merges or branches the flow of the refrigerant, and one refrigerant inlet / outlet (143b) of the water-refrigerant heat exchanger is connected. It is connected to a second merging branch (16b) that merges or branches the flow of the refrigerant, and the refrigerant inlet of the indoor evaporator is connected to a third merging branch (16c, 161a) that merges or branches the flow of the refrigerant. The first merging branch, the second merging branch, and the third merging branch are connected to each other.

The first expansion valve is arranged in the refrigerant passage (104) connecting the first merging branch portion and the second merging branch portion, and the second expansion valve is the third merging branch portion and the refrigerant inlet of the indoor evaporator. It is arranged in the refrigerant passage (103) connecting to and.

In the cooling mode for cooling the blown air, the refrigerant circuit switching unit causes the refrigerant discharged from the compressor to flow into the outdoor heat exchanger, and the refrigerant flowing out from the outdoor heat exchanger is depressurized by the second expansion valve. 2 In the heating mode in which the refrigerant decompressed by the expansion valve flows into the indoor evaporator and the blown air is heated, the refrigerant discharged from the compressor flows into the water-refrigerant heat exchanger and water-. The circuit configuration is switched so that the refrigerant flowing out of the refrigerant heat exchanger is decompressed by the first expansion valve and the decompressed refrigerant by the first expansion valve flows into the outdoor heat exchanger.

According to this, in the cooling mode, the blown air is cooled by the indoor evaporator (15). Further, in the heating mode, the blown air is heated by the heating unit (24). Therefore, as the indoor evaporator (15), one having appropriate specifications in the cooling mode can be adopted. Further, as the heating unit (24), one having appropriate specifications in the heating mode can be adopted. As a result, it is possible to suppress a decrease in the operating efficiency of the refrigerating cycle device when the operation mode is switched.

It also includes a first merging branch (16a), a second merging branch (16b), and a third merging branch (16c) connected to each other. Thereby, in a simple configuration, one refrigerant inlet / outlet (137b) of the outdoor heat exchanger (13), one refrigerant inlet / outlet (143b) of the water-refrigerant heat exchanger (14), and the indoor evaporator (15). The connection state between the refrigerant inlets can be freely and easily changed.

More specifically, one refrigerant inlet / outlet (137b) of the outdoor heat exchanger (13), one refrigerant inlet / outlet (143b) of the water-refrigerant heat exchanger (14), a refrigerant inlet / outlet of the indoor evaporator (15), and the like. An on-off valve or expansion valve is connected to the refrigerant passages (101 to 106) connecting any two of the 1-merging branch (16a), the 2nd confluence branch (16b), and the 3rd confluence branch (16c). Can be placed.

Then, by controlling the operation of the on-off valve and the expansion valve, the refrigerant passages of the outdoor heat exchanger (13), the water-refrigerant heat exchanger (14), and the indoor evaporator (15) are communicated with each other. And it is possible to switch to a state where communication is not possible. Further, the pressure difference between one refrigerant pressure and the other refrigerant pressure can be adjusted while communicating with each other.

That is, although it has a simple structure, the connection states of the outdoor heat exchanger (13), the water-refrigerant heat exchanger (14), and the indoor evaporator (15) can be freely and easily changed. can.

Further, specifically, the second expansion valve (17b) is arranged in the refrigerant passage connecting the third merging branch portion (16c) and the refrigerant inlet of the indoor evaporator (15). This makes it possible to easily switch to the circuit configuration of the cooling mode. Further, the first expansion valve (17a) is arranged in the refrigerant passage connecting the first merging branch portion (16a) and the second merging branch portion (16b). This makes it possible to easily switch to the circuit configuration of the heating mode.

Therefore, according to the refrigerating cycle apparatus according to claim 1, the circuit configuration of the refrigerant circuit (10) can be easily switched with a simple configuration without causing a decrease in operating efficiency.

The reference numerals in parentheses of each means described in this column and the scope of claims indicate the correspondence with the specific means described in the embodiments described later.

It is an overall block diagram which shows the refrigerant flow in the cooling mode and the like of the refrigerant circuit of 1st Embodiment. It is an overall block diagram which shows the refrigerant flow in the heating mode of the refrigerant circuit of 1st Embodiment. It is a schematic cross-sectional view which shows the refrigerant flow in the cooling mode of the outdoor heat exchanger of 1st Embodiment. It is a schematic cross-sectional view which shows the refrigerant flow in the heating mode and the like of the outdoor heat exchanger of 1st Embodiment. It is a schematic side view which shows the refrigerant flow and the like in the cooling mode of the water-refrigerant heat exchanger of 1st Embodiment. It is a schematic side view which shows the refrigerant flow and the like in the heating mode of the water-refrigerant heat exchanger of 1st Embodiment. It is an overall block diagram of the heat medium circuit of 1st Embodiment. It is a schematic whole block diagram of the room air-conditioning unit of 1st Embodiment. It is a block diagram which shows the electric control part of the refrigeration cycle apparatus of 1st Embodiment. It is explanatory drawing which shows an example of the heat medium flow in the heating mode of the heat medium circuit of 1st Embodiment. It is explanatory drawing which shows an example of the heat medium flow in the single cooling mode of the heat medium circuit of 1st Embodiment. It is explanatory drawing which shows the modification of the heat medium flow in the heating mode of the heat medium circuit of 1st Embodiment. It is explanatory drawing which shows another modification of the heat medium flow in the heating mode of the heat medium circuit of 1st Embodiment. It is explanatory drawing which shows the modification of the heat medium flow in the single cooling mode of the heat medium circuit of 1st Embodiment. It is explanatory drawing which shows another modification of the heat medium flow in the single cooling mode of the heat medium circuit of 1st Embodiment. It is an overall block diagram of the heat medium circuit of 2nd Embodiment. It is explanatory drawing which shows an example of the heat medium flow in the heating mode of the heat medium circuit of 2nd Embodiment. It is explanatory drawing which shows an example of the heat medium flow in the single cooling mode of the heat medium circuit of 2nd Embodiment. It is explanatory drawing which shows the modification of the heat medium flow in the heating mode of the heat medium circuit of 2nd Embodiment. It is an overall block diagram of the refrigerant circuit of 3rd Embodiment. It is a schematic sectional drawing of the three-way joint with a valve of 3rd Embodiment. It is explanatory drawing which shows the refrigerant circuit switching part of another embodiment. It is explanatory drawing which shows the other refrigerant circuit switching part of another embodiment. It is explanatory drawing which shows the heat medium flow in the warm-up mode of the heat medium circuit 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 matters described in the preceding embodiments, and duplicate explanations may be omitted. When only a part of the configuration is described in each embodiment, 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 problem in the combination. Is also possible.

(First Embodiment)
A first embodiment of the refrigeration cycle apparatus 1 according to the present invention will be described with reference to FIGS. 1 to 15. The refrigeration cycle device 1 is mounted on an electric vehicle that obtains driving force for traveling from a motor generator. In an electric vehicle, the refrigeration cycle device 1 air-conditions the interior of the vehicle, which is the space to be air-conditioned, and cools the in-vehicle device, which is the object to be cooled. That is, the refrigeration cycle device 1 of the present embodiment is used as a vehicle air conditioner with an in-vehicle device cooling function in an electric vehicle.

The in-vehicle device to be cooled by the refrigeration cycle device 1 is a battery 50 and a heat generating device 51 that generates heat during operation. Specific examples of the heat generating device 51 include a motor generator, a power control unit (so-called PCU), a control device for an advanced driver assistance system (so-called ADAS), and the like.

The battery 50 is a secondary battery (in this embodiment, a lithium ion battery) that stores electric power supplied to a motor generator or the like. The battery 50 is an assembled battery formed by connecting a plurality of battery cells in series or in parallel. The battery 50 generates heat during charging and discharging. The motor generator outputs the driving force for traveling by being supplied with electric power, and generates regenerative electric power when the vehicle is decelerating or the like. The PCU integrates a transformer, a frequency converter, and the like in order to appropriately control the electric power supplied to each in-vehicle device.

The refrigeration cycle device 1 includes a refrigerant circuit 10, a heat medium circuit 20, an indoor air conditioning unit 30, and the like. The refrigerant circuit 10 is a refrigerant circulation circuit that circulates the refrigerant. In the refrigerating cycle device 1, the circuit configuration of the refrigerant circuit 10 can be switched according to various operation modes described later in order to perform air conditioning in the vehicle interior and cooling of the vehicle-mounted equipment.

In the refrigerating cycle device 1, an HFO-based refrigerant (specifically, R1234yf) is used as the refrigerant for circulating the refrigerant circuit 10. The refrigerant circuit 10 constitutes a steam compression type subcritical refrigeration cycle in which the refrigerant pressure on the high pressure side does not exceed the critical pressure of the refrigerant. Refrigerant oil for lubricating the compressor 11 arranged in the refrigerant circuit 10 is mixed in the refrigerant. A part of the refrigerating machine oil circulates in the refrigerant circuit 10 together with the refrigerant.

As shown in FIGS. 1 and 2, the refrigerant circuit 10 includes a compressor 11, a four-way valve 12, an outdoor heat exchanger 13, a refrigerant passage 14a of the water-refrigerant heat exchanger 14, an indoor evaporator 15, and a first expansion. A valve 17a, a second expansion valve 17b, an evaporation pressure adjusting valve 19, and the like are arranged.

The compressor 11 sucks in the refrigerant, compresses it, and discharges it in the refrigerant circuit 10. The compressor 11 is arranged in the drive unit room. The drive unit room forms a space for accommodating a motor generator and the like. The drive unit is located on the front side of the vehicle interior. 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 40 described later.

One refrigerant inflow outlet of the four-way valve 12 is connected to the discharge port of the compressor 11. The four-way valve 12 is a refrigerant circuit switching unit that switches the circuit configuration of the refrigerant circuit 10. The operation of the four-way valve 12 is controlled by the control voltage output from the control device 40.

More specifically, as shown in FIG. 1, the four-way valve 12 connects the discharge port side of the compressor 11 and one refrigerant inlet / outlet side of the outdoor heat exchanger 13, and at the same time, at the same time, the suction port side of the compressor 11. It is possible to switch to a circuit configuration for connecting the water and one refrigerant inlet / outlet side of the water-refrigerant heat exchanger 14 and the refrigerant outlet side of the indoor evaporator 15.

Further, as shown in FIG. 2, the four-way valve 12 connects the discharge port side of the compressor 11 and one refrigerant inlet / outlet side of the water-refrigerant heat exchanger 14, and at the same time, connects the suction port side of the compressor 11 and the outdoor side. It is possible to switch to a circuit configuration that connects one refrigerant inlet side of the heat exchanger 13 and the refrigerant outlet side of the indoor evaporator 15.

One refrigerant inlet / outlet port 137a side of the outdoor heat exchanger 13 is connected to another refrigerant inflow port of the four-way valve 12. The outdoor heat exchanger 13 is a heat exchanger that exchanges heat between the refrigerant and the outside air blown from an outside air blower (not shown). The outdoor heat exchanger 13 is arranged on the front side in the drive unit room. Therefore, when the vehicle is running, the running wind that has flowed into the drive unit room through the outside air intake (so-called front grill) can be applied to the outdoor heat exchanger 13.

The detailed configuration of the outdoor heat exchanger 13 will be described with reference to FIGS. 3 and 4. The upper and lower arrows in FIGS. 3 and 4 indicate the upper and lower directions when the outdoor heat exchanger 13 is mounted on the vehicle. This also applies to other drawings. In this embodiment, a so-called tank-and-tube type heat exchanger is adopted as the outdoor heat exchanger 13.

The outdoor heat exchanger 13 has a plurality of tubes 131, a first tank 132, a second tank 133, a modulator 134, and the like. Each of these constituent members is made of the same type of metal (aluminum alloy in this embodiment) having excellent heat transfer properties. Further, each component is integrated by brazing joint.

The tube 131 is a tube for circulating a refrigerant inside. The tube 131 is a flat tube having a flat vertical cross section in the longitudinal direction. The tube 131 is arranged so as to extend in the horizontal direction. The plurality of tubes 131 are laminated in the vertical direction at regular intervals so that the flat surfaces (so-called flat surfaces) are parallel to each other.

An air passage for passing outside air is formed between adjacent tubes 131. That is, in the outdoor heat exchanger 13, since the plurality of tubes 131 are laminated and arranged at intervals, the refrigerant flowing inside the tube 131 and the outside air flowing through the air passage formed outside the tube 131. A heat exchange portion is formed to exchange heat with and.

Further, a corrugated fin 135 is arranged in an air passage formed between adjacent tubes 131. The corrugated fin 135 is a heat exchange fin that promotes heat exchange between the refrigerant and the outside air. The corrugated fin 135 is made by bending a thin metal plate of the same type as the tube 131 in a wavy shape. The corrugated fin 135 has a top formed by being bent in a wavy shape and is joined to both of adjacent tubes 131.

Although only a part of the tube 131 and the corrugated fin 135 is shown in FIGS. 3 and 4 for the sake of clarification, the tube 131 and the corrugated fin 135 are arranged over the entire area of the heat exchange section. Has been done.

A first tank 132 and a second tank 133 are connected to both ends of the plurality of tubes 131. The first tank 132 and the second tank 133 are bottomed cylindrical members extending in the stacking direction of the plurality of tubes 131.

Inside the first tank 132 and the second tank 133, a space serving as a distribution space or a collective space is formed. The distribution space is a space for distributing the refrigerant to the plurality of tubes 131. The collecting space is a space for collecting the refrigerant flowing out from the plurality of tubes 131.

More specifically, inside the first tank 132, a first separator 136a for the first tank and a second separator 136b for the first tank are arranged from the upper side. As a result, the internal space of the first tank 132 is divided into three spaces, the first space 132a, the second space 132b, and the third space 132c, from the upper side.

Further, a separator 136c for the second tank is arranged inside the second tank 133. As a result, the internal space of the second tank 133 is divided into the first space 133a and the second space 133b from the upper side. The second separator 136b for the first tank and the separator 136c for the second tank are positioned at the same height in the vertical direction.

Therefore, the plurality of tubes 131 of the present embodiment form a plurality of (specifically, three) paths. Here, the path in the tank-and-tube heat exchanger is the same direction as the refrigerant in the same distribution space formed in one tank toward the same collecting space formed in the other tank. It can be defined as a refrigerant flow path formed by a group of tubes flowing into.

Specifically, the tube group connecting the first space 132a of the first tank 132 and the first space 133a of the second tank 133 forms the first pass 13a. Further, the tube group connecting the first space 133a of the second tank 133 and the second space 132b of the first tank 132 forms the second pass 13b. Further, the tube group connecting the third space 132c of the first tank 132 and the second space 133b of the second tank 133 forms the third pass 13c.

The number of tube groups forming the first pass 13a is larger than the number of tube groups forming the second pass 13b. Therefore, the passage cross-section of the first pass 13a is larger than the passage cross-section of the second pass 13b. Further, the number of tube groups forming the second pass 13b is larger than the number of tube groups forming the third pass 13c. Therefore, the passage cross-section of the second pass 13b is larger than the passage cross-section of the third pass 13c.

Here, the passage cross-section of the path can be defined by the total value of the passage cross-sections of each tube 131 forming the path. Therefore, as the number of tubes increases, the cross-sectional area of the passage of the path also increases.

One refrigerant inlet / outlet port 137a connected to the four-way valve 12 side is provided on the upper side of the first tank 132 and at the portion forming the first space 132a. A portion below the second tank 133 that forms the second space 133b is provided with another refrigerant inlet / outlet 137b connected to one inlet / outlet side of the first three-way joint 16a, which will be described later. ..

Therefore, another refrigerant inlet / outlet 137b connected to the first three-way joint 16a side is arranged below one refrigerant inlet / outlet 137a connected to the four-way valve 12 side.

In the following description, for the sake of clarification, another refrigerant inlet / outlet 137b connected to the first three-way joint 16a side will be referred to as one refrigerant inlet / outlet 137b of the outdoor heat exchanger 13. Further, one refrigerant inlet / outlet 137a connected to the four-way valve 12 side is referred to as the other refrigerant inlet / outlet 137a of the outdoor heat exchanger 13.

A modulator 134 is connected to a portion of the first tank 132 in the vertical direction that forms the second space 132b, and a portion below the first tank 132 that forms the third space 132c. ..

The modulator 134 is an outside air side liquid storage unit that separates the air and liquid of the refrigerant that has flowed into the inside and stores the excess refrigerant of the cycle as a liquid phase refrigerant. The modulator 134 is a bottomed cylindrical member extending in the same direction as the first tank 132 and the second tank 133 (in the present embodiment, in the vertical direction).

Returning to FIGS. 1 and 2, one inflow of the first three-way joint 16a having three refrigerant inflow outlets communicating with each other through the first refrigerant passage 101 into one of the refrigerant inlets / outlets 137b of the outdoor heat exchanger 13. The exit side is connected.

The first three-way joint 16a is a first merging branch portion for merging or branching the flow of the refrigerant. As the first three-way joint 16a, 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, or the like can be adopted.

In the first three-way joint 16a, when two of the three inflow ports are used as inflow ports and the remaining one is used as an outflow port, the flows of the refrigerant flowing in from the two inflow ports are combined to form one outflow port. It becomes a confluence part that flows out from. Further, in the first three-way joint 16a, when one of the three inflow ports is used as the inflow port and the remaining two are used as the outflow ports, the flow of the refrigerant flowing in from one inflow port is branched into two. It is a branch that flows out from the outlet.

Further, the refrigerant circuit 10 of the present embodiment includes a second three-way joint 16b and a third three-way joint 16c. The basic configuration of the second three-way joint 16b and the third three-way joint 16c is the same as that of the first three-way joint 16a. As shown in FIGS. 1 and 2, in the first three-way joint 16a, the second three-way joint 16b, and the third three-way joint 16c, one inflow port is connected to each other.

One refrigerant inlet / outlet side of the water-refrigerant heat exchanger 14 is connected to the residual inflow / outlet of the second three-way joint 16b via the second refrigerant passage 102. Therefore, the second three-way joint 16b is the second merging branch portion. The refrigerant inlet side of the indoor evaporator 15 is connected to the residual inflow / outlet of the third three-way joint 16c via the third refrigerant passage 103. Therefore, the third three-way joint 16c is the third merging branch portion.

The first three-way joint 16a and the second three-way joint 16b are connected via a fourth refrigerant passage 104. The first three-way joint 16a and the third three-way joint 16c are connected via a fifth refrigerant passage 105. The second three-way joint 16b and the third three-way joint 16c are connected via the sixth refrigerant passage 106.

A first expansion valve 17a is arranged in the fourth refrigerant passage 104. The first expansion valve 17a reduces the pressure of the refrigerant flowing into the outdoor heat exchanger 13 through the second three-way joint 16b at least in the heating mode for heating the interior of the vehicle, and at least the refrigerant flowing into the outdoor heat exchanger 13 is depressurized. Adjust the flow rate (mass flow rate). Further, the first expansion valve 17a reduces the pressure of the refrigerant flowing into the water-refrigerant heat exchanger 14 at least in the cooling mode for cooling the in-vehicle equipment, and the flow rate of the refrigerant flowing into the water-refrigerant heat exchanger 14 ( Adjust the mass flow rate).

The first expansion valve 17a is an electric variable throttle having a valve body portion configured to change the throttle opening degree and an electric actuator (specifically, a stepping motor) for changing the opening degree of the valve body portion. It is a mechanism. The operation of the first expansion valve 17a is controlled by a control signal (control pulse) output from the control device 40.

The first expansion valve 17a has a fully open function that functions as a mere refrigerant passage without exerting a refrigerant decompression effect by fully opening the valve opening, and closes the refrigerant passage by fully closing the valve opening. It has a fully closed function. The first expansion valve 17a can switch the circuit configuration of the refrigerant circuit 10 by the fully open function and the fully closed function. Therefore, the first expansion valve 17a also has a function as a refrigerant circuit switching unit.

Further, a second expansion valve 17b is arranged in the third refrigerant passage 103. More specifically, the second expansion valve 17b is arranged at the end of the third refrigerant passage 103 on the indoor evaporator 15 side via a dedicated connector.

The second expansion valve 17b decompresses the refrigerant flowing into the indoor evaporator 15 at least in the cooling mode for cooling the interior of the vehicle, and adjusts the flow rate (mass flow rate) of the refrigerant flowing into the indoor evaporator 15. The basic configuration of the second expansion valve 17b is the same as that of the first expansion valve 17a. Therefore, the second expansion valve 17b also has a function as a refrigerant circuit switching unit.

Further, a first check valve 18a, which is a refrigerant circuit switching portion, is arranged in the fifth refrigerant passage 105. The first check valve 18a is a first opening / closing portion that opens / closes a fifth refrigerant passage 105 connecting the first three-way joint 16a and the third three-way joint 16c. The first check valve 18a allows the refrigerant to flow from the first three-way joint 16a side to the third three-way joint 16c side, and prohibits the refrigerant from flowing from the third three-way joint 16c side to the first three-way joint 16a side.

Further, a second check valve 18b, which is a refrigerant circuit switching portion, is arranged in the sixth refrigerant passage 106. The second check valve 18b is a second opening / closing portion that opens / closes the sixth refrigerant passage 106 that connects the second three-way joint 16b and the third three-way joint 16c. The second check valve 18b allows the refrigerant to flow from the second three-way joint 16b side to the third three-way joint 16c side, and prohibits the refrigerant from flowing from the third three-way joint 16c side to the second three-way joint 16b side.

The water-refrigerant heat exchanger 14 is a heat medium-refrigerant heat exchanger that exchanges heat between the refrigerant and the heat medium circulating in the heat medium circuit 20. The water-refrigerant heat exchanger 14 is arranged in the drive unit room. The detailed configuration of the water-refrigerant heat exchanger 14 will be described with reference to FIGS. 5 and 6. In this embodiment, a so-called laminated heat exchanger is adopted as the water-refrigerant heat exchanger 14.

The water-refrigerant heat exchanger 14 has a plurality of heat transfer plates 141, a liquid storage tank 142, and the like. Each of these constituent members is made of the same type of metal (aluminum alloy in this embodiment) having excellent heat transfer properties. Further, each component is integrated by brazing joint.

The heat transfer plate 141 is a rectangular plate-shaped member elongated in the vertical direction. The plurality of heat transfer plates 141 are stacked and arranged in the horizontal direction at intervals so that the flat surfaces are parallel to each other. A plurality of overhanging portions protruding in the stacking direction are formed on the outer peripheral edge portion and the flat surface of the heat transfer plate 141, respectively. In the plurality of heat transfer plates 141, the overhanging portions of the respective heat transfer plates 141 are joined to the adjacent heat transfer plates 141.

Therefore, a refrigerant passage 14a through which the refrigerant flows and a heat medium passage 14b through which the heat medium flows are formed in the portion where the overhanging portion between the adjacent heat transfer plates 141 is not formed. The refrigerant passages 14a and the heat medium passages 14b of the present embodiment are alternately formed in the stacking direction. As a result, the refrigerant flowing through the refrigerant passage 14a and the heat medium flowing through the heat medium passage 14b can exchange heat with each other via the heat transfer plate 141.

Refrigerant tank forming portions communicating with the refrigerant passage 14a are formed on both ends of the heat transfer plate 141 in the vertical direction by overhanging portions. The internal spaces of the refrigerant tank forming portions of the heat transfer plates 141 communicate with each other. Therefore, when the plurality of heat transfer plates 141 are stacked and arranged, a refrigerant tank space communicating with the plurality of refrigerant passages 14a is formed on the upper side and the lower side of the water-refrigerant heat exchanger 14.

Similarly, on both ends in the vertical direction of the heat transfer plate 141, heat medium tank forming portions communicating with the heat medium passage 14b are formed by overhanging portions. The internal spaces of the heat medium tanks of the heat transfer plates 141 communicate with each other. Therefore, when a plurality of heat transfer plates 141 are stacked and arranged, a heat medium tank space communicating with the plurality of heat medium passages 14b is formed on the upper side and the lower side of the water-refrigerant heat exchanger 14. There is.

In the refrigerant tank space formed on the upper side of the heat transfer plate 141, one refrigerant inlet / outlet 143a to which another refrigerant inflow / outlet side of the four-way valve 12 is connected is provided. A liquid storage tank 142 is connected to the refrigerant tank space formed on the lower side of the heat transfer plate 141.

The liquid storage tank 142 is a heat medium-side liquid storage unit that separates the gas and liquid of the refrigerant that has flowed into the inside and stores the excess refrigerant in the cycle as a liquid phase refrigerant. The liquid storage tank 142 is a bottomed tubular member extending in the vertical direction. The liquid storage tank 142 is provided with another refrigerant inlet / outlet 143b connected to one inflow / outlet side of the second three-way joint 16b.

In the following description, for the sake of clarification of the description, another refrigerant inlet / outlet 143b provided in the liquid storage tank 142 connected to the second three-way joint 16b side is referred to one of the water-refrigerant heat exchanger 14. It is described as a refrigerant inlet / outlet 143b. Further, one refrigerant inlet / outlet 143a connected to the four-way valve 12 side is referred to as the other refrigerant inlet / outlet 143a of the water-refrigerant heat exchanger 14.

A heat medium inlet 143c of the water-refrigerant heat exchanger 14 is provided in the heat medium tank space formed on the lower side of the heat transfer plate 141. A heat medium outlet 143d of the water-refrigerant heat exchanger 14 is provided in the heat medium tank space formed on the upper side of the heat transfer plate 141.

Therefore, in the water-refrigerant heat exchanger 14, the flow direction of the heat medium does not change even if the operation mode is switched. That is, in the water-hydrogen heat exchanger 14, the heat medium flowing into the lower heat medium tank space is a plurality of heat media as shown by the thick dashed arrows in FIGS. 5 and 6, regardless of the operation mode. It moves to the upper heat medium tank space through the passage 14b.

Returning to FIGS. 1 and 2, the indoor evaporator 15 is a heat exchanger that exchanges heat between the refrigerant decompressed by the second expansion valve 17b and the blown air blown from the indoor blower 32 toward the vehicle interior. .. In the indoor evaporator 15, the blown air can be cooled by evaporating the refrigerant decompressed by the second expansion valve 17b and causing the refrigerant to exert an endothermic action. The indoor blower 32 and the indoor evaporator 15 are arranged in the casing 31 of the indoor air conditioning unit 30, which will be described later.

The inlet side of the evaporation pressure adjusting valve 19 is connected to the refrigerant outlet of the indoor evaporator 15. The evaporation pressure regulating valve 19 is a pressure regulating valve that maintains the refrigerant evaporation pressure in the indoor evaporator 15 at a predetermined reference pressure or higher.

The evaporation pressure adjusting valve 19 is a mechanical variable throttle mechanism that increases the valve opening degree as the pressure of the refrigerant on the outlet side of the indoor evaporator 15 increases. As a result, the evaporation pressure adjusting valve 19 maintains the refrigerant evaporation temperature in the indoor evaporator 15 at a frost formation suppression temperature (1 ° C. in the present embodiment) that can suppress frost formation in the indoor evaporator 15. ..

The suction port side of the compressor 11 is connected to the outlet of the evaporation pressure adjusting valve 19 via the merging portion 16d. The basic configuration of the merging portion 16d is the same as that of the first three-way joint 16a and the like. Yet another refrigerant inflow / outlet side of the four-way valve 12 is connected to the other inlet of the merging portion 16d.

Further, in the refrigerant circuit 10, the refrigerant passages connecting the constituent devices are formed by refrigerant pipes having three types of diameters, a large diameter, an intermediate diameter, and a small diameter. Specifically, the refrigerant passage connecting the discharge port of the compressor 11 and one refrigerant inflow port of the four-way valve 12 is formed by a refrigerant pipe having an intermediate diameter. The first refrigerant passage 101 to the sixth refrigerant passage 106 are formed of a small-diameter refrigerant pipe. The remaining refrigerant passage is formed by a large-diameter refrigerant pipe.

Therefore, the passage cross-sectional area of the first refrigerant passage 101 to the sixth refrigerant passage 106 is from the passage cross-sectional area of the discharge side refrigerant passage 107 connecting the discharge port of the compressor 11 and one refrigerant inflow outlet of the four-way valve 12. Is also small.

Next, the heat medium circuit 20 will be described with reference to FIG. 7. The heat medium circuit 20 is a heat medium circulation circuit that circulates a heat medium. In the refrigeration cycle device 1, the circuit configuration of the heat medium circuit 20 can be switched according to various operation modes in order to perform air conditioning in the vehicle interior and appropriate cooling of the vehicle-mounted equipment. The refrigeration cycle apparatus 1 employs an ethylene glycol aqueous solution as a heat medium for circulating the heat medium circuit 20.

In the heat medium circuit 20, as shown in FIG. 7, in addition to the heat medium passage 14b of the water-refrigerator heat exchanger 14, the cooling water passage 50a of the battery 50, and the cooling water passage 51a of the heat generating device 51, the first water The pump 21a, the second water pump 21b, the first heat medium three-way valve 22a, the second heat medium three-way valve 22b, the third heat medium three-way valve 22c, the heating device 23, the heater core 24, the radiator 25, the heat medium on-off valve 26, etc. Have been placed.

The first water pump 21a pumps the heat medium toward the heat medium passage 14b of the water-refrigerant heat exchanger 14. The first water pump 21a is an electric pump whose rotation speed (that is, pumping capacity) is controlled by a control voltage output from the control device 40.

The inflow port side of the third heat medium three-way valve 22c is connected to the outlet of the heat medium passage 14b of the water-refrigerant heat exchanger 14. The third heat medium three-way valve 22c is a flow rate of the heat medium flowing out from the heat medium passage 14b to the cooling water passage 50a side of the battery 50 and the heat medium flow rate flowing out to the heating device 23 side. It is a three-type flow rate control valve that can continuously adjust the ratio. The operation of the third heat medium three-way valve 22c is controlled by a control signal output from the control device 40.

Further, the third heat medium three-way valve 22c can allow the entire flow rate of the heat medium flowing out from the heat medium passage 14b to flow out to either the cooling water passage 50a side or the heating device 23 side of the battery 50. As a result, the third heat medium three-way valve 22c can switch the circuit configuration of the heat medium circuit 20. Therefore, the third heat medium three-way valve 22c is a heat medium circuit switching unit that switches the circuit configuration of the heat medium circuit 20.

The cooling water passage 50a of the battery 50 is a heat medium passage for circulating a low temperature heat medium to cool the battery 50. In other words, the cooling water passage 50a of the battery 50 is a cooling unit that cools the battery 50 using a heat medium cooled by the water-refrigerant heat exchanger 14 as a cooling heat source. The cooling water passage 50a of the battery 50 is formed in a dedicated case of the battery 50.

The passage configuration of the cooling water passage 50a of the battery 50 is a passage configuration in which a plurality of passages are connected in parallel inside the dedicated case. As a result, the cooling water passage 50a is formed so that the waste heat of the battery 50 can be uniformly absorbed from the entire area of the battery 50. In other words, the cooling water passage 50a is formed so that the heat of all the battery cells can be uniformly absorbed and all the battery cells can be cooled evenly.

The suction port side of the first water pump 21a is connected to the outlet of the cooling water passage 50a of the battery 50 via the fourth heat medium check valve 27d. The fourth heat medium check valve 27d allows the heat medium to flow from the outlet side of the cooling water passage 50a of the battery 50 to the suction port side of the first water pump 21a, and from the suction port side of the first water pump 21a. It is prohibited to flow to the outlet side of the cooling water passage 50a.

The heating device 23 heats the heat medium flowing out of the third heat medium three-way valve 22c by the electric power supplied from the control device 40. The heating device 23 has a heating passage and a heat generating portion. The heating passage is a passage through which a heat medium is circulated. The heat generating unit heats the heat medium flowing through the heating passage by being supplied with electric power. Specifically, a PTC element or a nichrome wire can be adopted as the heat generating portion.

The heat medium inlet side of the heater core 24 is connected to the outlet of the heating device 23. The heater core 24 is a heat exchanger that exchanges heat between the heat medium and the blown air blown from the indoor blower 32. The heater core 24 is a heating unit that heats the blown air using the heat of the heated heat medium at least one of the water-refrigerant heat exchanger 14 and the heating device 23 as a heat source. The heater core 24 is arranged in the casing 31 of the indoor air conditioning unit 30.

The inlet side of the first heat medium three-way valve 22a is connected to the heat medium outlet of the heater core 24. The first heat medium three-way valve 22a includes the flow rate of the heat medium flowing out from the heater core 24 to the suction port side of the first water pump 21a, the one inlet / outlet side of the cooling water passage 51a of the heat generating device 51, and the like. It is a three-type flow rate adjusting valve that can continuously adjust the flow rate ratio with the flow rate of the heat medium flowing out to.

The basic configuration of the first heat medium three-way valve 22a is the same as that of the third heat medium three-way valve 22c. Therefore, the first heat medium three-way valve 22a is a heat medium circuit switching unit that switches the circuit configuration of the heat medium circuit 20.

The cooling water passage 51a of the heat generating device 51 is a heat medium passage for circulating a low temperature heat medium to cool the heat generating device 51. In other words, the cooling water passage 51a of the heat generating device 51 is a cooling unit that cools the heat generating device 51 using the heat medium cooled by the water-refrigerant heat exchanger 14 as a cooling heat source. The cooling water passage 51a of the heat generating device 51 is formed in a housing portion or the inside of a case forming the outer shell of the heat generating device 51.

The suction port side of the first water pump 21a is connected to the other inlet / outlet of the cooling water passage 51a of the heat generating device 51 via the third heat medium check valve 27c. The third heat medium check valve 27c allows the heat medium to flow from the cooling water passage 51a side of the heat generating device 51 to the suction port side of the first water pump 21a, and cools from the suction port side of the first water pump 21a. It is prohibited to flow to the water passage 51a side.

Further, the inlet side of the heating device 23 is connected to the outlet of the third heat medium check valve 27c via the first heat medium check valve 27a. The first heat medium check valve 27a allows the heat medium to flow from the outlet side of the third heat medium check valve 27c to the inlet side of the heating device 23, and reverses the third heat medium from the inlet side of the heating device 23. It is prohibited to flow to the outlet side of the check valve 27c.

The second water pump 21b pumps the heat medium toward the other inlet / outlet side of the cooling water passage 51a of the heat generating device 51 and the inlet side of the cooling water passage 50a of the battery 50. The basic configuration of the second water pump 21b is the same as that of the first water pump 21a.

A second heat medium check valve 27b is arranged in the heat medium passage from the discharge port of the second water pump 21b to the other inlet / outlet of the cooling water passage 51a of the heat generating device 51. The second heat medium check valve 27b allows the heat medium to flow from the discharge port side of the second water pump 21b to the other inlet / outlet side of the cooling water passage 51a of the heat generating device 51, and allows the heat medium to flow to the other inlet / outlet side of the cooling water passage 51a. It is prohibited to flow from the inlet / outlet side to the discharge port side of the second water pump 21b.

Further, a fifth heat medium check valve 27e is arranged in the heat medium passage from the discharge port of the second water pump 21b to the inlet of the cooling water passage 50a of the battery 50. The fifth heat medium check valve 27e allows the heat medium to flow from the discharge port side of the second water pump 21b to the inlet side of the cooling water passage 50a of the battery 50, and allows the heat medium to flow from the inlet side of the cooling water passage 50a to the second. It is prohibited to flow to the discharge port side of the water pump 21b.

A branch portion 28a for branching the flow of the heat medium is arranged between the first heat medium three-way valve 22a and the cooling water passage 51a of the heat generating device 51. The flow of the heat medium branched at the branch portion 28a is guided to the inlet side of the second heat medium three-way valve 22b.

The second heat medium three-way valve 22b has a heat medium flow rate that flows out to the suction port side of the second water pump 21b and heat that flows out to the heat medium inlet side of the radiator 25 among the heat media branched at the branch portion 28a. It is a three-type flow control valve that can continuously adjust the flow rate ratio with the medium flow rate. The basic configuration of the second heat medium three-way valve 22b is the same as that of the third heat medium three-way valve 22c. Therefore, the second heat medium three-way valve 22b is a heat medium circuit switching unit that switches the circuit configuration of the heat medium circuit 20.

The radiator 25 is an outside air heat exchange unit that exchanges heat between the heat medium circulating inside and the outside air. The radiator 25 is arranged on the front side in the drive unit room. Therefore, the radiator 25 may be integrally configured with the outdoor heat exchanger 13.

Further, the heat medium circuit 20 has a heat medium passage 26a that connects the heat medium inlet side of the radiator 25 and the outlet side of the cooling water passage 50a of the battery 50. A heat medium on-off valve 26 for opening and closing the connection passage is arranged in the heat medium passage 26a. The heat medium on-off valve 26 is a solenoid valve whose operation is controlled by a control voltage output from the control device 40. The heat medium on-off valve 26 is a heat medium circuit switching unit that switches the circuit configuration of the heat medium circuit 20.

That is, in the heat medium circuit 20 of the present embodiment, the heat medium passage 14b of the water-refrigerator heat exchanger 14 as a temperature adjusting unit for adjusting the temperature of the heat medium, the heat medium heated by the temperature adjusting unit, and the air blower. The heater core 24 as a heating unit that heats the blown air by exchanging heat with the air, and the cooling water of the object to be cooled (that is, the battery 50 and the heat generating device 51) that circulates the heat medium cooled by the temperature adjusting unit. The passages 50a and 51a are provided with a first heat medium three-way valve 22a to a third heat medium three-way valve 22c and a heat medium on-off valve 26 as a heat medium circuit switching unit for switching the circuit configuration of the heat medium circuit 20.

In the heating mode in which the compressor 11 is operated to heat the blown air in the heating unit, the heat medium circuit switching unit can be switched to a circuit configuration in which the heat medium is circulated between the temperature adjusting unit and the heating unit. Further, the heat medium circuit switching unit is a circuit that circulates the heat medium between the cooling water passages 50a and 51a and the heating unit in the waste heat heating mode in which the compressor 11 is stopped and the blown air is heated by the heating unit. You can switch to the configuration.

Further, the heat medium circuit switching unit switches to a circuit configuration in which the heat medium is circulated between the temperature adjusting unit and the cooling water passages 50a and 51a in the cooling mode in which the compressor 11 is operated to cool the object to be cooled. Can be done.

Further, the heat medium circuit 20 includes a radiator 25 as an outside air heat exchange unit that exchanges heat between the heat medium and the outside air. Then, in the outside air cooling mode in which the compressor 11 is stopped to cool the object to be cooled, the heat medium circuit switching unit has a circuit configuration in which the heat medium is circulated between the outside air heat exchange unit and the cooling water passages 50a and 51a. You can switch.

Next, the indoor air conditioning unit 30 will be described with reference to FIG. The indoor air-conditioning unit 30 is a unit in which a plurality of constituent devices are integrated in order to blow out blown air adjusted to an appropriate temperature for air-conditioning in 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 front of the vehicle interior.

As shown in FIG. 8, the indoor air conditioning unit 30 accommodates an indoor blower 32, an indoor evaporator 15 of a refrigerant circuit 10, a heater core 24 of a heat medium circuit 20, and the like in a casing 31 forming an air passage for blown air. It is a thing. 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 blast 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 40.

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 rotation speed (that is, the blowing capacity) of the indoor blower 32 is controlled by the control voltage output from the control device 40.

On the downstream side of the blown air flow of the indoor blower 32, the indoor evaporator 15 and the heater core 24 are arranged in this order with respect to the blown air flow. That is, the indoor evaporator 15 is arranged on the upstream side of the blown air flow with respect to the heater core 24. Further, a cold air bypass passage 35 is formed in the casing 31 to allow the blown air after passing through the indoor evaporator 15 to bypass the heater core 24 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 15 and on the upstream side of the blown air flow of the heater core 24.

The air mix door 34 is an air volume ratio adjusting unit that adjusts the air volume ratio between the air volume passing through the heater core 24 and the air volume passing through the cold air bypass passage 35 in the air blown air after passing through the indoor evaporator 15. The operation of the electric actuator for driving the air mix door is controlled by the control signal output from the control device 40.

A mixing space 36 is provided on the downstream side of the blown air flow of the heater core 24 and the cold air bypass passage 35. The mixing space 36 is a space for mixing the blown air heated by the heater core 24 and the blown air that has not been heated through the cold air bypass passage 35. Further, in the downstream portion of the blown air flow of the casing 31, a plurality of opening holes for blowing out the blown air mixed in the mixing space 36 and having its temperature adjusted into the vehicle interior are arranged.

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 24 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 40 has a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof. The control device 40 performs various operations and processes based on the control program stored in the ROM. Then, the control device 40 operates various controlled target devices 11, 12, 17a, 17b, 21a, 21b, 22a to 22c, 23, 26, 32, etc. connected to the output side based on the calculation and processing results. Control.

Further, on the input side of the control device 40, as shown in the block diagram of FIG. 9, an inside temperature sensor 41, an outside temperature sensor 42, a solar radiation sensor 43, an intake refrigerant temperature sensor 44a, a heat exchanger temperature sensor 44b, and an evaporator A temperature sensor 44f, an intake refrigerant pressure sensor 45, a first heat medium temperature sensor 46a, a second heat medium temperature sensor 46b, a battery temperature sensor 47a, a heat generating device temperature sensor 47b, an air conditioning air temperature sensor 49, and the like are connected. The detection signals of these sensor groups are input to the control device 40.

The internal air temperature sensor 41 is an internal air temperature detection unit that detects the vehicle interior temperature (internal air temperature) Tr. The outside air temperature sensor 42 is an outside air temperature detection unit that detects the outside air temperature (outside air temperature) Tam. The solar radiation sensor 43 is a solar radiation amount detection unit that detects the solar radiation amount As irradiated to the vehicle interior.

The suction refrigerant temperature sensor 44a is a suction refrigerant temperature detection unit that detects the suction refrigerant temperature Ts of the refrigerant sucked into the compressor 11. The heat exchanger temperature sensor 44b is a heat exchanger temperature detection unit that detects the temperature (heat exchanger temperature) TC of the refrigerant passing through the water-refrigerator heat exchanger 14. The heat exchanger temperature sensor 44b specifically detects the temperature of the outer surface of the water-refrigerant heat exchanger 14.

The evaporator temperature sensor 44f is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 15. The evaporator temperature sensor 44f specifically detects the temperature of the heat exchange fins of the indoor evaporator 15. The suction refrigerant pressure sensor 45 is a suction refrigerant pressure detecting unit that detects the suction refrigerant pressure Ps of the refrigerant sucked into the compressor 11.

The first heat medium temperature sensor 46a is a first heat medium temperature detection unit that detects the temperature TW1 of the heat medium flowing into the heater core 24. The second heat medium temperature sensor 46b is a second heat medium temperature detection unit that detects the temperature TW2 of the heat medium flowing into the cooling water passage 50a of the battery 50. The conditioned air temperature sensor 49 is an conditioned air temperature detecting unit that detects the blast air temperature TAV blown from the mixed space to the vehicle interior.

The battery temperature sensor 47a is a battery temperature detection unit that detects the battery temperature TBA, which is the temperature of the battery 50. The battery temperature sensor 47a has a plurality of temperature detection units, and detects the temperature of a plurality of points of the battery 50. Therefore, the control device 40 can also detect the temperature difference of each part of the battery 50. Further, as the battery temperature TBA, the average value of the detected values of a plurality of temperature sensors is adopted.

The heat generation device temperature sensor 47b is a heat generation device temperature detection unit that detects the heat generation device temperature TMG, which is the temperature of the heat generation device 51. The heat generating device temperature sensor 47b detects the temperature of the outer surface of the housing forming the outer shell of the heat generating device 51.

Further, as shown in FIG. 9, an operation panel 401 arranged near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device 40, and various operation switches provided on the operation panel 401 are used. The operation signal is input.

As various operation switches provided on the operation panel 401, specifically, an auto switch that sets or cancels the automatic control operation of the refrigeration cycle device 1, and an air conditioner switch that requires the indoor evaporator 15 to cool the blown air. , There is an air volume setting switch for manually setting the air volume of the indoor blower 32, a temperature setting switch for setting the target temperature Tset in the vehicle interior, and the like.

The control device 40 of the present embodiment is integrally configured with a control unit that controls various controlled devices connected to the output side of the control device 40. Therefore, the configuration (hardware and software) that controls the operation of each control target device constitutes the control unit that controls the operation of each control target device.

For example, in the control device 40, the configuration for controlling the refrigerant discharge capacity of the compressor 11 (specifically, the rotation speed of the compressor 11) constitutes the discharge capacity control unit 60a. Further, the configuration for controlling the operation of the four-way valve 12 which is the refrigerant circuit switching unit constitutes the refrigerant circuit control unit 60b. Further, the configuration for controlling the operation of the first heat medium three-way valve 22a to the third heat medium three-way valve 22c and the heat medium on-off valve 26, which are the heat medium circuit switching units, constitutes the heat medium circuit control unit 60c.

Next, the operation of the refrigeration cycle device 1 of the present embodiment in the above configuration will be described. As described above, the refrigerating cycle device 1 of the present embodiment can switch various operation modes for air conditioning in the vehicle interior and cooling of the vehicle-mounted equipment.

Specifically, the refrigerating cycle device 1 can switch between a cooling mode, a heating mode, and a dehumidifying heating mode as an air conditioning mode for air conditioning the interior of the vehicle. Further, as the cooling mode for cooling the in-vehicle device, the independent cooling mode and the cooling cooling mode can be switched.

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. The heating mode is an operation mode in which the inside of the vehicle is heated by blowing out the heated blown air into the vehicle interior. The dehumidifying / heating mode is an operation mode in which the dehumidifying / heating of the vehicle interior is performed by reheating the cooled and dehumidified blown air and blowing it into the vehicle interior.

The single cooling mode is an operation mode in which at least one of the battery 50 and the heat generating device 51 is cooled without air conditioning in the vehicle interior. The cooling cooling mode is an operation mode in which the inside of the vehicle is cooled by blowing the cooled blown air into the vehicle interior, and at the same time, at least one of the battery 50 and the heat generating device 51 is cooled.

Switching of each operation mode of the refrigeration cycle device 1 is performed by executing a control program. The control program is executed when the auto switch of the operation panel 401 is turned on (ON) and the automatic control operation is set.

In the main routine of the control program, the detection signal of the sensor group for air conditioning control described above and the operation signal from various air conditioning operation switches are read. Then, based on the values of the read detection signal and the operation signal, the target blowing temperature TAO, which is the target temperature of the blowing air blown into the vehicle interior, is calculated based on the following mathematical formula F1.

Specifically, 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 As + C ... (F1)
In addition, Tset is the target temperature in the vehicle interior (vehicle interior set temperature) set by the temperature setting switch, Tr is the internal air temperature detected by the internal air temperature sensor 41, Tam is the outside air temperature detected by the outside air temperature sensor 42, and As. Is the amount of solar radiation detected by the solar radiation sensor 43. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

Then, in the control program, when the target blowing temperature TAO is lower than the predetermined cooling reference temperature α with the air conditioner switch of the operation panel 401 turned on, the operation mode is switched to the cooling mode.

Further, in the control program, when the target outlet temperature TAO is equal to or higher than the cooling reference temperature α with the air conditioner switch of the operation panel 401 turned on, the operation mode is switched to the dehumidifying / heating mode. Further, when the target outlet temperature TAO is equal to or higher than the cooling reference temperature α when the air conditioner switch is not turned on, the operation mode is switched to the heating mode.

Further, in the control program, even if the vehicle interior is not air-conditioned, when the battery temperature TBA becomes the reference battery temperature KTBA or higher, or when the heat generating device temperature TMG becomes the standard heating device temperature KTMG or higher. Switches the operation mode to the independent cooling mode.

Further, in the control program, when the cooling mode is executed, when the battery temperature TBA becomes equal to or higher than the reference battery temperature KTBA, or when the heating device temperature TMG becomes equal to or higher than the reference heating device temperature KTMG. Switches the operation mode to the cooling / cooling mode. Each operation mode will be described below.

(A) Cooling mode In the cooling mode, the control device 40 connects the discharge port side of the compressor 11 and the refrigerant inlet / outlet side of one of the outdoor heat exchangers 13, and at the same time, connects the suction port side of the compressor 11 and the water-refrigerant side. The four-way valve 12 is operated so as to connect one refrigerant inlet / outlet side of the heat exchanger 14 and a refrigerant outlet side of the indoor evaporator 15. Further, the control device 40 puts the first expansion valve 17a in a fully closed state and the second expansion valve 17b in a throttle state in which the refrigerant depressurizing action is exerted.

Therefore, in the cooling mode refrigerant circuit 10, as shown by the white arrow in FIG. 1, the discharge port of the compressor 11 → the four-way valve 12 → the outdoor heat exchanger 13 → the first check valve 18a → the second expansion valve. A steam compression type refrigeration cycle is configured in which the refrigerant is circulated in the order of 17b → indoor evaporator 15 → evaporation pressure adjusting valve 19 → compressor 11 suction port.

With this circuit configuration, the control device 40 appropriately controls the operation of other controlled devices. For example, for the compressor 11, the number of revolutions (that is, the refrigerant discharge capacity) is controlled so that the evaporator temperature Tefin detected by the evaporator temperature sensor 44f approaches the target evaporator temperature TEO for the cooling mode.

The target evaporator temperature TEO is determined based on the target blowout temperature TAO with reference to a control map stored in advance in the control device 40. In this control map, it is determined that the target evaporator temperature TEO decreases as the target outlet temperature TAO decreases.

Further, regarding the second expansion valve 17b, the throttle opening is controlled so that the superheat degree SH of the intake refrigerant sucked into the compressor 11 approaches a predetermined standard superheat degree KSH. The degree of superheat SH is calculated based on the suction refrigerant temperature Ts detected by the suction refrigerant temperature sensor 44a and the suction refrigerant pressure Ps detected by the suction refrigerant pressure sensor 45.

Further, for the indoor blower 32, the rotation speed (that is, the amount of blown air) is determined with reference to the control map stored in advance in the control device 40 based on the target blowout temperature TAO. In this control map, the amount of air blown by the indoor blower 32 is maximized in the extremely low temperature region (that is, the maximum cooling region) and the extremely high temperature region (that is, the maximum heating region) of the target blowout temperature TAO, and as the temperature approaches the intermediate temperature region. Reduce the amount of air blown.

Further, regarding the air mix door 34, the operation of the electric actuator for driving the air mix door is controlled so that the cold air bypass passage 35 is fully opened and the ventilation path on the heater core 24 side is fully closed.

Therefore, in the cooling mode refrigerant circuit 10, the high-pressure refrigerant discharged from the compressor 11 flows into the other refrigerant inlet / outlet 137a of the outdoor heat exchanger 13 via the four-way valve 12. The refrigerant flowing into the outdoor heat exchanger 13 flows in the order of the first pass 13a → the second pass 13b → the modulator 134 → the third pass 13c, as shown by the thick solid line arrow in FIG.

The refrigerant flowing into the outdoor heat exchanger 13 exchanges heat with the outside air blown from the outside air blower and condenses when flowing through the first pass 13a and the second pass 13b. The refrigerant condensed in the first pass 13a and the second pass 13b flows into the modulator 134. In the modulator 134, the excess refrigerant of the cycle is stored as a liquid phase refrigerant.

The refrigerant flowing out of the modulator 134 flows into the third pass 13c. The refrigerant flowing into the third pass 13c exchanges heat with the outside air blown from the outside air blower and is supercooled. The refrigerant supercooled when flowing through the third pass 13c flows out from one of the refrigerant inlets / outlets 137b.

The refrigerant flowing out from one of the refrigerant inlets / outlets 137b of the outdoor heat exchanger 13 flows into the second expansion valve 17b via the first three-way joint 16a, the first check valve 18a, and the third three-way joint 16c to reduce the pressure. Will be done. At this time, the throttle opening of the second expansion valve 17b is adjusted so that the superheat degree SH of the intake refrigerant approaches the reference superheat degree KSH.

The low-pressure refrigerant decompressed by the second expansion valve 17b flows into the indoor evaporator 15. The low-pressure refrigerant flowing into the indoor evaporator 15 absorbs heat from the blown air blown from the indoor blower 32 and evaporates. As a result, the blown air is cooled. The refrigerant flowing out of the indoor evaporator 15 is sucked into the compressor 11 via the evaporation pressure adjusting valve 19 and the merging portion 16d, and is compressed again.

Further, in the indoor air conditioning unit 30 in the cooling mode, the blown air cooled by the indoor evaporator 15 is blown into the vehicle interior. As a result, in the cooling mode, the interior of the vehicle can be cooled.

(B) Heating mode In the heating mode, the control device 40 connects the discharge port side of the compressor 11 and one refrigerant inlet / outlet side of the water-refrigerant heat exchanger 14, and at the same time, the suction port side of the compressor 11 and the outdoor side. The four-way valve 12 is operated so as to connect one refrigerant inlet side of the heat exchanger 13 and the refrigerant outlet side of the indoor evaporator 15. Further, the control device 40 puts the first expansion valve 17a in the throttled state and the second expansion valve 17b in the fully closed state.

Further, the control device 40 operates the first water pump 21a so as to exert a reference pumping capacity for a predetermined heating mode. Further, the control device 40 operates the third heat medium three-way valve 22c so that the heat medium flowing out from the heat medium passage 14b of the water-refrigerant heat exchanger 14 flows out to the heating device 23 side. Further, the control device 40 operates the first heat medium three-way valve 22a so that the heat medium flowing out from the heater core 24 flows out to the suction port side of the first water pump 21a. Further, the control device 40 closes the heat medium on-off valve 26.

Therefore, in the refrigerant circuit 10 in the heating mode, as shown by the black arrow in FIG. 2, the discharge port of the compressor 11 → the four-way valve 12 → the water-refrigerant heat exchanger 14 → the first expansion valve 17a → the outdoor heat exchange. A steam compression type refrigeration cycle is configured in which the refrigerant is circulated in the order of the vessel 13 → the four-way valve 12 → the suction port of the compressor 11.

Further, in the heat medium circuit 20 in the heating mode, as shown by the thick line in FIG. 10, the discharge port of the first water pump 21a → the water-hydrogen heat exchanger 14 → the third heat medium three-way valve 22c → the heating device 23 → the heater core. A circuit for circulating the heat medium is configured in the order of 24 → the first heat medium three-way valve 22a → the suction port of the first water pump 21a.

With this circuit configuration, the control device 40 appropriately controls the operation of other controlled devices. For example, for the compressor 11, the rotation speed is controlled so that the heat exchanger temperature TC detected by the heat exchanger temperature sensor 44b approaches the target heat exchanger temperature TCO1 for the heating mode.

The target heat exchanger temperature TCO1 is determined based on the target outlet temperature TAO with reference to a control map stored in advance in the control device 40. In this control map, it is determined that the target heat exchanger temperature TCO1 increases as the target outlet temperature TAO increases.

Further, with respect to the first expansion valve 17a, the throttle opening is controlled so that the superheat degree SH of the intake refrigerant sucked into the compressor 11 approaches the reference superheat degree KSH. Further, for the indoor blower 32, the rotation speed is determined in the same manner as in the cooling mode.

Further, regarding the air mix door 34, the operation of the electric actuator for driving the air mix door is controlled so that the blown air temperature TAV detected by the air conditioning air temperature sensor 49 approaches the target blowing temperature TAO.

Further, the control device 40 energizes the heating device 23 when the blown air temperature TAV does not reach the target blowing temperature TAO even if the air mix door 34 fully opens the ventilation path on the heater core 24 side. Alternatively, when the temperature TW1 detected by the first heat medium temperature sensor 46a is lower than the predetermined reference temperature KTW1, the heating device 23 is energized.

Therefore, in the refrigerant circuit 10 in the heating mode, the high-pressure refrigerant discharged from the compressor 11 flows into the other refrigerant inlet / outlet 143a of the refrigerant passage 14a of the water-refrigerant heat exchanger 14 via the four-way valve 12. The refrigerant flowing into the water-refrigerant heat exchanger 14 exchanges heat with the heat medium flowing through the heat medium passage 14b and condenses when flowing through the refrigerant passage 14a. As a result, the heat medium flowing through the heat medium passage 14b is heated.

In the water-refrigerant heat exchanger 14 in the heating mode, the refrigerant flows from the upper side to the lower side in the refrigerant passage 14a as shown by the thick solid line arrow in FIG. Further, in the water-refrigerant heat exchanger 14, as shown by the thick dashed arrow in FIG. 6, the heat medium flows from the lower side to the upper side in the heat medium passage 14b regardless of the operation mode.

Therefore, in the water-refrigerant heat exchanger 14 in the heating mode, the flow direction of the refrigerant flowing through the refrigerant passage 14a and the flow direction of the heat medium flowing through the heat medium passage 14b face each other. That is, in the water-refrigerant heat exchanger 14 in the heating mode, the flow of the refrigerant flowing through the refrigerant passage 14a and the flow of the heat medium flowing through the heat medium passage 14b are opposite flows.

The refrigerant condensed in the refrigerant passage 14a flows into the liquid storage tank 142. In the liquid storage tank 142, the excess refrigerant of the cycle is stored as the liquid phase refrigerant. The refrigerant flowing out from one of the refrigerant inlets / outlets 143b provided in the liquid storage tank 142 flows into the first expansion valve 17a via the second three-way joint 16b and is depressurized. At this time, the throttle opening of the first expansion valve 17a is adjusted so that the superheat degree SH of the intake refrigerant approaches the reference superheat degree KSH.

The low-pressure refrigerant decompressed by the first expansion valve 17a flows into one of the refrigerant inlets / outlets 137b of the outdoor heat exchanger 13 via the first three-way joint 16a. The low-pressure refrigerant flowing into the outdoor heat exchanger 13 flows in the order of the third pass 13c → the modulator 134 → the second pass 13b → the first pass 13a, as shown by the thick solid line arrow in FIG. The low-pressure refrigerant flowing into the outdoor heat exchanger 13 absorbs heat from the outside air and evaporates.

Here, in the heating mode, the excess refrigerant in the cycle is stored in the liquid storage tank 142 of the water-refrigerant heat exchanger 14, so that the liquid phase refrigerant is not stored in the modulator 134. Therefore, the modulator 134 in the heating mode is merely a refrigerant passage. The refrigerant flowing out from the other refrigerant inlet / outlet 137a of the outdoor heat exchanger 13 is sucked into the compressor 11 via the four-way valve 12 and the merging portion 16d and compressed again.

Further, in the heat medium circuit 20 in the heating mode, the heat medium pressure-fed from the first water pump 21a flows into the heat medium inlet 143c of the heat medium passage 14b of the water-refrigerant heat exchanger 14. The heat medium flowing into the heat medium passage 14b exchanges heat with the refrigerant flowing through the refrigerant passage 14a and is heated.

The heat medium flowing out from the heat medium outlet 143d of the heat medium passage 14b flows into the heating passage of the heating device 23 via the third heat medium three-way valve 22c. At this time, if the control device 40 supplies electric power to the heating device 23, the heat medium is further heated. The heat medium flowing out of the heating passage of the heating device 23 flows into the heater core 24.

The heat medium flowing into the heater core 24 exchanges heat with the blown air blown from the indoor blower 32 and dissipates heat. As a result, the blown air is heated. The refrigerant flowing out of the heater core 24 is sucked into the first water pump 21a via the first heat medium three-way valve 22a and pumped again.

Further, in the indoor air conditioning unit 30 in the heating mode, the blown air heated by the heater core 24 is blown into the vehicle interior. This makes it possible to heat the interior of the vehicle in the heating mode.

(C) Dehumidifying / heating mode In the dehumidifying / heating mode, the control device 40 operates the four-way valve 12 in the same manner as in the heating mode. Further, the control device 40 puts the first expansion valve 17a in the throttled state and the second expansion valve 17b in the throttled state.

Further, the control device 40 operates the first water pump 21a, the first heat medium three-way valve 22a, the third heat medium three-way valve 22c, and the heat medium on-off valve 26, as in the heating mode.

Therefore, in the refrigerant circuit 10 in the dehumidifying / heating mode, as shown by the diagonal hatched arrow in FIG. 2, the discharge port of the compressor 11 → the four-way valve 12 → the water-refrigerant heat exchanger 14 → the second check valve 18b → The refrigerant is circulated in the order of the second expansion valve 17b → the indoor evaporator 15 → the evaporation pressure adjusting valve 19 → the suction port of the compressor 11, and the discharge port of the compressor 11 → the four-way valve 12 → the water-refrigerant heat exchanger 14 →. A steam compression type refrigeration cycle is configured in which the refrigerant is circulated in the order of the first expansion valve 17a → the outdoor heat exchanger 13 → the four-way valve 12 → the suction port of the compressor 11.

That is, in the refrigerant circuit 10 in the dehumidifying / heating mode, a refrigerating cycle in which the outdoor heat exchanger 13 and the indoor evaporator 15 are connected in parallel to the flow of the refrigerant flowing out from the water-refrigerant heat exchanger 14 is configured. To.

Further, in the heat medium circuit 20 in the heating mode, a circuit for circulating the heat medium is configured as in the heating mode.

With this circuit configuration, the control device 40 appropriately controls the operation of other controlled devices. For example, for the compressor 11, the rotation speed is controlled so that the heat exchanger temperature TC approaches the target heat exchanger temperature TCO1 as in the heating mode.

Further, for the first expansion valve 17a, the throttle opening is controlled so as to be the throttle opening for the dehumidifying / heating mode defined in advance. Further, the second expansion valve 17b is controlled so that the superheat degree SH of the intake refrigerant sucked into the compressor 11 approaches the reference superheat degree KSH, as in the heating mode. Further, for the indoor blower 32, the rotation speed is determined in the same manner as in the cooling mode.

As for the air mix door 34, the operation of the electric actuator for driving the air mix door is controlled so that the blown air temperature TAV detected by the air conditioning air temperature sensor 49 approaches the target blowing temperature TAO, as in the heating mode. do.

Further, as in the heating mode, the control device 40 energizes the heating device 23 when the blown air temperature TAV does not reach the target blowing temperature TAO even if the air mix door 34 fully opens the ventilation path on the heater core 24 side. .. Alternatively, when the temperature TW1 detected by the first heat medium temperature sensor 46a is lower than the reference temperature KTW1, the heating device 23 is energized.

Therefore, in the refrigerant circuit 10 in the dehumidifying / heating mode, the high-pressure refrigerant discharged from the compressor 11 flows into the refrigerant passage 14a of the water-refrigerant heat exchanger 14 as in the heating mode. The refrigerant flowing into the water-refrigerant heat exchanger 14 exchanges heat with the heat medium flowing through the heat medium passage 14b and condenses when flowing through the refrigerant passage 14a. As a result, the heat medium flowing through the heat medium passage 14b is heated.

In the water-refrigerant heat exchanger 14 in the dehumidifying and heating mode, as shown in FIG. 6, in the water-refrigerant heat exchanger 14, the flow of the refrigerant flowing through the refrigerant passage 14a and the flow of the heat medium flowing through the heat medium passage 14b face each other, as shown in FIG. It becomes a flow. Further, in the liquid storage tank 142 in the dehumidifying / heating mode, the excess refrigerant in the cycle is stored as the liquid phase refrigerant. The flow of the refrigerant flowing out from one of the refrigerant inlets / outlets 143b of the water-refrigerant heat exchanger 14 is branched at the second three-way joint 16b.

One of the refrigerants branched at the second three-way joint 16b flows into the second expansion valve 17b via the second check valve 18b and the third three-way joint 16c and is depressurized. The low-pressure refrigerant decompressed by the second expansion valve 17b flows into the indoor evaporator 15 as in the cooling mode. The low-pressure refrigerant flowing into the indoor evaporator 15 absorbs heat from the blown air blown from the indoor blower 32 and evaporates. As a result, the blown air is cooled and dehumidified.

The refrigerant flowing out of the indoor evaporator 15 flows into the confluence portion 16d via the evaporation pressure adjusting valve 19. At this time, the valve opening degree of the evaporation pressure adjusting valve 19 is adjusted so that the refrigerant evaporation temperature in the indoor evaporator 15 becomes equal to or higher than the frost formation suppression temperature.

Further, the other refrigerant branched at the second three-way joint 16b flows into the first expansion valve 17a and is depressurized as in the heating mode. At this time, the opening degree of the first expansion valve 17a is adjusted so that the superheat degree SH of the intake refrigerant approaches the reference superheat degree KSH. The low-pressure refrigerant decompressed by the first expansion valve 17a flows into the outdoor heat exchanger 13 as in the heating mode.

The low-pressure refrigerant flowing into the outdoor heat exchanger 13 passes in the order of the third pass 13c → the modulator 134 → the second pass 13b → the first pass 13a, as shown by the thick solid arrow in FIG. 4, as in the heating mode. .. The low-pressure refrigerant flowing into the outdoor heat exchanger 13 absorbs heat from the outside air and evaporates. Further, the liquid phase refrigerant is not stored in the modulator 134, and the modulator 134 is merely a refrigerant passage.

The refrigerant flowing out from the other refrigerant inlet / outlet 137a of the outdoor heat exchanger 13 flows into the merging portion 16d via the four-way valve 12. At the merging portion 16d, the refrigerant flowing out from the evaporation pressure adjusting valve 19 and the refrigerant flowing out from the other refrigerant inlet / outlet port 137a of the outdoor heat exchanger 13 merge. The refrigerant merged at the merging portion 16d is sucked into the compressor 11 and compressed again.

Further, in the heat medium circuit 20 in the dehumidifying / heating mode, the heat medium heated when passing through the heat medium passage 14b of the water-refrigerant heat exchanger 14 flows into the heater core 24, as in the heating mode. As a result, the blown air is heated.

Further, in the indoor air conditioning unit 30 in the dehumidifying / heating mode, the blown air cooled by the indoor evaporator 15 and dehumidified is reheated by the heater core 24 and blown into the vehicle interior. Thereby, in the dehumidifying / heating mode, the dehumidifying / heating of the vehicle interior can be performed.

(D) Single cooling mode In the single cooling mode, the control device 40 operates the four-way valve 12 in the same manner as in the cooling mode. Further, the control device 40 puts the first expansion valve 17a in the throttled state and the second expansion valve 17b in the fully closed state.

Further, the control device 40 operates the first water pump 21a so as to exert a reference pressure feeding capacity for a predetermined single cooling mode. Further, the control device 40 causes the heat medium flowing out from the heat medium passage 14b of the water-refrigerant heat exchanger 14 to flow out to both the cooling water passage 50a side and the heating device 23 side of the battery 50. Operate the three-way valve 22c. Further, the control device 40 operates the first heat medium three-way valve 22a so that the heat medium flowing out from the heater core 24 flows out to one of the inlet / outlet sides of the cooling water passage 51a of the heat generating device 51. Further, the control device 40 operates the second heat medium three-way valve 22b so that the heat medium flowing out from the first heat medium three-way valve 22a does not flow out to the second heat medium three-way valve 22b side. Further, the control device 40 closes the heat medium on-off valve 26.

Therefore, in the refrigerant circuit 10 in the independent cooling mode, as shown by the shaded arrow in FIG. 1, the discharge port of the compressor 11 → the four-way valve 12 → the outdoor heat exchanger 13 → the first expansion valve 17a → water-. A steam compression type refrigeration cycle is configured in which the refrigerant is circulated in the order of the refrigerant heat exchanger 14 → the four-way valve 12 → the suction port of the compressor 11.

Further, in the heat medium circuit 20 in the single cooling mode, as shown by the thick line in FIG. 11, the discharge port of the first water pump 21a → the water-hydrogen heat exchanger 14 → the third heat medium three-way valve 22c → cooling the battery 50. The heat medium is circulated in the order of the water passage 50a → the suction port of the first water pump 21a, and the discharge port of the first water pump 21a → the water-refrigerator heat exchanger 14 → the third heat medium three-way valve 22c → the heating device 23 →. A circuit is configured in which the heat medium is circulated in the order of the heater core 24 → the first heat medium three-way valve 22a → the cooling water passage 51a of the heat generating device 51 → the suction port of the first water pump 21a.

That is, in the heat medium circuit 20 in the independent cooling mode, the cooling water passage 50a of the battery 50 and the heating device 23 are parallel to the flow of the heat medium flowing out from the heat medium passage 14b of the water-refrigerant heat exchanger 14. The connected circuit is configured.

With this circuit configuration, the control device 40 appropriately controls the operation of other controlled devices. For example, for the compressor 11, the rotation speed is controlled so that the heat exchanger temperature TC approaches the target heat exchanger temperature TCO2 for the single cooling mode defined in advance.

Further, with respect to the first expansion valve 17a, the throttle opening is controlled so that the superheat degree SH of the intake refrigerant sucked into the compressor 11 approaches a predetermined standard superheat degree KSH. Further, for the indoor blower 32, the rotation speed is determined in the same manner as in the cooling mode. Further, regarding the air mix door 34, the operation of the electric actuator for driving the air mix door is controlled so that the cold air bypass passage 35 is fully opened and the ventilation path on the heater core 24 side is fully closed.

Therefore, in the refrigerant circuit 10 in the single cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the other refrigerant inlet / outlet 137a of the outdoor heat exchanger 13 as in the cooling mode. The refrigerant flowing into the outdoor heat exchanger 13 passes in the order of the first pass 13a → the second pass 13b → the modulator 134 → the third pass 13c, as shown by the thick solid line arrow in FIG. 3, as in the cooling mode.

The refrigerant flowing into the outdoor heat exchanger 13 exchanges heat with the outside air and condenses when flowing through the first pass 13a and the second pass 13b. In the modulator 134, the excess refrigerant of the cycle is stored as a liquid phase refrigerant. The refrigerant flowing out of the modulator 134 exchanges heat with the outside air when flowing through the third pass 13c and is supercooled.

The refrigerant flowing out of the outdoor heat exchanger 13 flows into the first expansion valve 17a via the first three-way joint 16a and is depressurized. At this time, the opening degree of the first expansion valve 17a is adjusted so that the superheat degree SH of the intake refrigerant approaches the reference superheat degree KSH.

The low-pressure refrigerant decompressed by the first expansion valve 17a flows into one of the refrigerant inlets / outlets 143b of the water-refrigerant heat exchanger 14 via the second three-way joint 16b. The low-pressure refrigerant flowing into the water-refrigerant heat exchanger 14 exchanges heat with the heat medium flowing through the heat medium passage 14b and evaporates when flowing through the refrigerant passage 14a. As a result, the heat medium flowing through the heat medium passage 14b is cooled.

In the water-refrigerant heat exchanger 14 in the single cooling mode, the refrigerant flows from the lower side to the upper side in the refrigerant passage 14a as shown by the thick solid line arrow in FIG. Further, in the water-refrigerant heat exchanger 14, the heat medium flows from the lower side to the upper side in the heat medium passage 14b regardless of the operation mode.

Therefore, in the water-refrigerant heat exchanger 14 in the single cooling mode, the flow direction of the refrigerant flowing through the refrigerant passage 14a and the flow direction of the heat medium flowing through the heat medium passage 14b are the same. That is, in the water-refrigerant heat exchanger 14 in the single cooling mode, the flow of the refrigerant flowing through the refrigerant passage 14a and the flow of the heat medium flowing through the heat medium passage 14b are parallel flows.

Here, in the single cooling mode, since the excess refrigerant of the cycle is stored in the modulator 134 of the outdoor heat exchanger 13, the liquid phase refrigerant is not stored in the liquid storage tank 142 of the water-refrigerant heat exchanger 14. Therefore, the liquid storage tank 142 is merely a refrigerant passage. The refrigerant flowing out from the other refrigerant inlet / outlet 143a of the water-refrigerant heat exchanger 14 is sucked into the compressor 11 via the four-way valve 12 and the confluence portion 16d and compressed again.

Further, in the heat medium circuit 20 in the single cooling mode, the heat medium pressure-fed from the first water pump 21a flows into the heat medium inlet 143c of the heat medium passage 14b of the water-refrigerant heat exchanger 14. The heat medium flowing into the heat medium passage 14b exchanges heat with the refrigerant flowing through the refrigerant passage 14a and is cooled. The flow of the heat medium flowing out from the heat medium outlet 143d of the heat medium passage 14b is branched by the third heat medium three-way valve 22c.

The flow of one of the heat media branched by the third heat medium three-way valve 22c flows into the cooling water passage 50a of the battery 50. The heat medium flowing into the cooling water passage 50a absorbs the waste heat of the battery 50. This cools the battery 50. The heat medium flowing out of the cooling water passage 50a is sucked into the first water pump 21a via the fourth heat medium check valve 27d and pumped again.

The flow of one of the heat media branched by the third heat medium three-way valve 22c flows into the cooling water passage 51a of the heat generating device 51 via the heating device 23, the heater core 24, and the first heat medium three-way valve 22a. The heat medium flowing into the cooling water passage 51a absorbs the waste heat of the heat generating device 51. As a result, the heat generating device 51 is cooled. The heat medium flowing out of the cooling water passage 51a is sucked into the first water pump 21a via the third heat medium check valve 27c and pumped again.

Here, in the single cooling mode, the control device 40 does not supply electric power to the heating device 23. Therefore, the heating device 23 is merely a heat medium passage. Further, in the single cooling mode, the air mix door 34 completely closes the ventilation passage on the heater core 24 side. Therefore, in the heater core 24 in the single cooling mode, heat exchange between the heat medium and the blown air is not performed. Therefore, the heater core 24 is merely a heat medium passage.

As a result, in the single cooling mode, both the battery 50 and the heat generating device 51 can be cooled without air conditioning in the vehicle interior.

(E) Cooling cooling mode In the cooling cooling mode, the control device 40 operates the four-way valve 12 in the same manner as in the cooling mode. Further, the control device 40 puts the first expansion valve 17a in the throttled state and the second expansion valve 17b in the throttled state.

Further, the control device 40 operates the first water pump 21a, the third heat medium three-way valve 22c, the first heat medium three-way valve 22a, and the heat medium on-off valve 26, as in the single cooling mode.

Therefore, in the refrigerant circuit 10 in the cooling / cooling mode, as shown by both the white arrow and the shaded arrow in FIG. 1, the discharge port of the compressor 11 → the four-way valve 12 → the outdoor heat exchanger 13 → the first. The check valve 18a → the second expansion valve 17b → the indoor evaporator 15 → the evaporation pressure adjusting valve 19 → the suction port of the compressor 11 circulates the refrigerant in this order, and the discharge port of the compressor 11 → the four-way valve 12 → the outdoor heat exchange. A steam compression type refrigerating cycle is configured in which the refrigerant is circulated in the order of the vessel 13 → the first expansion valve 17a → the water-refrigerant heat exchanger 14 → the four-way valve 12 → the suction port of the compressor 11.

That is, in the refrigerant circuit 10 in the cooling / cooling mode, a refrigeration cycle in which the indoor evaporator 15 and the water-refrigerant heat exchanger 14 are connected in parallel to the flow of the refrigerant flowing out from the outdoor heat exchanger 13 is configured. To.

Further, in the heat medium circuit 20 in the cooling cooling mode, a circuit for circulating the heat medium is configured as in the single cooling mode.

With this circuit configuration, the control device 40 appropriately controls the operation of other controlled devices. For example, for the compressor 11, the rotation speed is controlled so that the evaporator temperature Tefien approaches the target evaporator temperature TEO, as in the cooling mode.

Further, for the first expansion valve 17a, the throttle opening is controlled so as to have a throttle opening for a predetermined cooling cooling mode. Further, the second expansion valve 17b is controlled so that the superheat degree SH of the intake refrigerant sucked into the compressor 11 approaches the reference superheat degree KSH, as in the cooling mode. Further, for the indoor blower 32, the rotation speed is determined in the same manner as in the cooling mode.

As for the air mix door 34, as in the cooling mode and the cooling mode, the electric actuator for driving the air mix door is operated so that the cold air bypass passage 35 is fully opened and the ventilation path on the heater core 24 side is fully closed. To control.

Therefore, in the refrigerant circuit 10 in the single cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the other refrigerant inlet / outlet 137a of the outdoor heat exchanger 13 as in the cooling mode. The refrigerant flowing into the outdoor heat exchanger 13 passes in the order of the first pass 13a → the second pass 13b → the modulator 134 → the third pass 13c, as shown by the thick solid line arrow in FIG. 3, as in the cooling mode.

The refrigerant flowing into the outdoor heat exchanger 13 exchanges heat with the outside air and condenses when flowing through the first pass 13a and the second pass 13b. In the modulator 134, the excess refrigerant of the cycle is stored as a liquid phase refrigerant. The refrigerant flowing out of the modulator 134 exchanges heat with the outside air when flowing through the third pass 13c and is supercooled.

The flow of the refrigerant flowing out of the outdoor heat exchanger 13 is branched at the first three-way joint 16a. One of the refrigerants branched at the first three-way joint 16a flows into the second expansion valve 17b via the first check valve 18a and the third three-way joint 16c and is depressurized. At this time, the opening degree of the second expansion valve 17b is adjusted so that the superheat degree SH of the intake refrigerant approaches the reference superheat degree KSH. The refrigerant flowing out of the indoor evaporator 15 flows into the confluence portion 16d via the evaporation pressure adjusting valve 19.

The other refrigerant branched at the first three-way joint 16a flows into the first expansion valve 17a and is depressurized. The low-pressure refrigerant decompressed by the first expansion valve 17a flows into one of the refrigerant inlets / outlets 143b of the water-refrigerant heat exchanger 14, as in the single cooling mode. The low-pressure refrigerant flowing into the water-refrigerant heat exchanger 14 exchanges heat with the heat medium flowing through the heat medium passage 14b and evaporates when flowing through the refrigerant passage 14a. As a result, the heat medium flowing through the heat medium passage 14b is cooled.

In the water-refrigerant heat exchanger 14 in the cooling cooling mode, as shown by the thick solid line arrow in FIG. 5, the flow of the refrigerant flowing through the refrigerant passage 14a and the heat flowing through the heat medium passage 14b are the same as in the single cooling mode. The flow of the medium becomes a parallel flow. Further, the liquid phase refrigerant is not stored in the liquid storage tank 142 of the water-refrigerant heat exchanger 14, and the liquid storage tank 142 is merely a refrigerant passage.

The refrigerant flowing out from the other refrigerant inlet / outlet 143a of the water-refrigerant heat exchanger 14 flows into the confluence portion 16d via the four-way valve 12. At the merging portion 16d, the refrigerant flowing out from the evaporation pressure adjusting valve 19 and the refrigerant flowing out from the other refrigerant inlet / outlet port 137a of the outdoor heat exchanger 13 merge. The refrigerant merged at the merging portion 16d is sucked into the compressor 11 and compressed again.

Further, in the heat medium circuit 20 in the cooling cooling mode, the heat medium cooled when passing through the heat medium passage 14b of the water-refrigerator heat exchanger 14 is the cooling water passage 50a of the battery 50, as in the single cooling mode. And flows into the cooling water passage 51a of the heat generating device 51. As a result, the battery 50 and the heat generating device 51 are cooled.

Further, in the indoor air conditioning unit 30 in the cooling / cooling mode, the blown air cooled by the indoor evaporator 15 is blown into the vehicle interior. As a result, in the cooling / cooling mode, both the battery 50 and the heat generating device 51 can be cooled at the same time as cooling the vehicle interior.

As described above, according to the refrigerating cycle device 1 of the present embodiment, by switching the circuit configuration of the refrigerant circuit 10 and the circuit configuration of the heat medium circuit 20, it is possible to perform air conditioning in the vehicle interior and temperature adjustment of the in-vehicle device. ..

In the refrigeration cycle device 1 of the present embodiment, when cooling the blown air, the indoor evaporator 15 exchanges heat between the refrigerant and the blown air to cool the blown air. Further, when heating the blown air, the heater core 24 heats the blown air by exchanging heat between the heat medium and the blown air.

According to this, as the indoor evaporator 15, one having appropriate specifications for cooling the blown air can be adopted. Further, as the heater core 24, one having appropriate specifications for heating the blown air can be adopted. As a result, it is possible to prevent the operating efficiency of the refrigerating cycle device 1 from being lowered when the operation mode is switched.

Further, the refrigerant circuit 10 of the refrigeration cycle device 1 of the present embodiment includes a first three-way joint 16a, a second three-way joint 16b, and a third three-way joint 16c connected to each other. This makes it possible to easily switch the connection state between the refrigerant passages of the outdoor heat exchanger 13, the water-refrigerant heat exchanger 14, and the indoor evaporator 15 in spite of the simple configuration.

To explain this in more detail, in the refrigerant circuit 10 of the present embodiment, the first three-way joint 16a, the second three-way joint 16b, and the third three-way joint 16c are connected to each other. Therefore, in the refrigerant circuit 10 of the present embodiment, there is a high degree of freedom in arranging the on-off valve, the expansion valve, and the like, which are relatively easy to control the operation.

That is, the first refrigerant passage 101 connecting the one refrigerant inlet / outlet 137b of the outdoor heat exchanger 13 and the first three-way joint 16a, the second three-way joint 16b, and the one refrigerant inlet / outlet 143b of the water-refrigerant heat exchanger 14. The second refrigerant passage 102, the third refrigerant passage 103 that connects the third three-way joint 16c and the refrigerant inlet of the indoor evaporator 15, the fourth refrigerant passage that connects the first three-way joint 16a and the second three-way joint 16b. 104, any of the six refrigerant passages 105, the fifth refrigerant passage 105 connecting the first three-way joint 16a and the third three-way joint 16c, and the sixth refrigerant passage 106 connecting the second three-way joint 16b and the third three-way joint 16c. An on-off valve or expansion valve can be placed in the refrigerant.

Then, by controlling the operation of the on-off valve and the expansion valve, the refrigerant passages of the outdoor heat exchanger 13, the water-refrigerant heat exchanger 14, and the indoor evaporator 15 are made to communicate with each other or not to communicate with each other. It can be easily switched. Further, the pressure difference between one refrigerant pressure and the other refrigerant pressure can be easily adjusted in a state of communicating with each other.

That is, although the configuration is simple, the connection states of the outdoor heat exchanger 13, the water-refrigerant heat exchanger 14, and the indoor evaporator 15 can be freely and easily changed.

Further, in the refrigerating cycle device 1 of the present embodiment, specifically, the second expansion valve 17b is arranged in the refrigerant passage connecting the third three-way joint 16c and the refrigerant inlet of the indoor evaporator 15.

According to this, as described in the cooling mode, the refrigerant flowing out of the outdoor heat exchanger 13 flows into the second expansion valve 17b via the first three-way joint 16a and the third three-way joint 16c to reduce the pressure. Further, it is possible to easily switch to a circuit configuration in which the refrigerant decompressed by the second expansion valve 17b flows into the indoor evaporator 15.

In addition to this, as described in the dehumidifying and heating mode, at least a part of the refrigerant flowing out of the water-refrigerant heat exchanger 14 is passed through the second three-way joint 16b and the third three-way joint 16c to the second expansion valve 17b. To reduce the pressure. Further, it is possible to easily switch to a circuit configuration in which the refrigerant decompressed by the second expansion valve 17b flows into the indoor evaporator 15.

Further, in the refrigerating cycle device 1 of the present embodiment, specifically, the first expansion valve 17a is arranged in the refrigerant passage connecting the first three-way joint 16a and the second three-way joint 16b.

According to this, as described in the heating mode, the refrigerant flowing out of the water-refrigerant heat exchanger 14 flows into the first expansion valve 17a via the second three-way joint 16b to reduce the pressure. Further, it is possible to easily switch to a circuit configuration in which the refrigerant decompressed by the first expansion valve 17a flows into the outdoor heat exchanger 13 via the first three-way joint 16a.

In addition to this, as described in the cooling mode (ie, single cooling mode and cooling cooling mode), the refrigerant flowing out of the outdoor heat exchanger 13 flows into the first expansion valve 17a via the first three-way joint 16a. Let it reduce the pressure. Further, it is possible to easily switch to a circuit configuration in which the refrigerant decompressed by the first expansion valve 17a flows into the water-refrigerant heat exchanger 14.

Therefore, according to the refrigerating cycle apparatus 1 of the present embodiment, the circuit configuration of the refrigerant circuit 10 can be easily switched with a simple configuration without causing a decrease in operating efficiency.

Further, in the refrigerating cycle device 1 of the present embodiment, specifically, the first expansion valve 17a is arranged in the fourth refrigerant passage 104 connecting the first three-way joint 16a and the second three-way joint 16b. A first check valve 18a as a first on-off valve is arranged in a fifth refrigerant passage 105 connecting the first three-way joint 16a and the third three-way joint 16c. A second check valve 18b as a second on-off valve is arranged in the sixth refrigerant passage 106 connecting the second three-way joint 16b and the third three-way joint 16c.

According to this, when the first expansion valve 17a is in the throttled state, the high-pressure side refrigerant can flow to the third three-way joint 16c side, and the low-pressure side refrigerant flows to the third three-way joint 16c side. It is possible to easily realize a circuit configuration that suppresses the flow. Further, since the first check valve 18a is adopted as the first on-off valve and the second check valve 18b is adopted as the second on-off valve, the first and first check valves do not require electrical control. 2 The on-off valve can be opened and closed.

Further, in the refrigerating cycle device 1 of the present embodiment, the outdoor heat exchanger 13 having the modulator 134 is adopted. According to this, the excess refrigerant of the cycle can be stored in the modulator 134 as a liquid phase refrigerant in the cooling mode, the single cooling mode, and the cooling cooling mode. Therefore, the refrigeration cycle can be operated properly.

Further, in the outdoor heat exchanger 13 of the present embodiment, the passage cross section is from the other refrigerant inlet / outlet 137a toward the one refrigerant inlet / outlet 137b, that is, in the order of the first pass 13a → the second pass 13b → the third pass 13c. Is shrinking.

According to this, in the operation mode in which the refrigerant is condensed by the outdoor heat exchanger 13, such as the cooling mode, the independent cooling mode, and the cooling cooling mode, the passage cross-sectional area is reduced as the volume of the refrigerant decreases. Can be done. Further, in the operation mode in which the refrigerant is evaporated by the outdoor heat exchanger 13 as in the heating mode and the dehumidifying heating mode, the passage cross-sectional area can be expanded as the volume of the refrigerant increases.

Therefore, it is possible to suppress an increase in pressure loss that occurs in the refrigerant flowing through the outdoor heat exchanger 13 in any of the operation modes.

Further, in the outdoor heat exchanger 13 of the present embodiment, the other refrigerant inlet / outlet 137a is arranged above the one refrigerant inlet / outlet 137b.

According to this, when a high-pressure refrigerant flows in from the other refrigerant inlet / outlet 137a as in the cooling mode, the independent cooling mode, and the cooling cooling mode, the condensed refrigerant is moved to one refrigerant inlet / outlet 137b side by the action of gravity. Easy to move to. Further, when the low-pressure refrigerant flows in from one of the refrigerant inlets / outlets 137b as in the heating mode and the dehumidifying / heating mode, the low-pressure refrigerant can be easily distributed evenly to the plurality of tubes 131 due to the inertial force of the refrigerant.

Further, in the refrigerating cycle device 1 of the present embodiment, a water-refrigerant heat exchanger 14 having a liquid storage tank 142 is adopted. According to this, the excess refrigerant of the cycle can be stored in the liquid storage tank 142 in the heating mode and the dehumidifying heating mode. Therefore, the refrigeration cycle can be operated properly.

Further, in the water-refrigerator heat exchanger 14 of the present embodiment, in the operation mode in which the heat medium is heated by the water-refrigerator heat exchanger 14, as in the heating mode and the dehumidifying heating mode, the water-refrigerator heat exchanger is used. The flow of the refrigerant and the flow of the heat medium in No. 14 are opposite flows. Further, in the operation mode in which the heat medium is cooled by the water-refrigerant heat exchanger 14, such as the single cooling mode and the cooling cooling mode, the flow of the refrigerant and the flow of the heat medium in the water-refrigerant heat exchanger 14 are parallel. It becomes a flow.

Here, in the refrigeration cycle device 1 of the present embodiment, the heat load (that is, corresponding to the heating capacity of the heat medium) in the operation mode in which the heat medium is heated by the water-hydrogen heat exchanger 14 is the water-hydrogen heat. It becomes larger than the heat load (that is, corresponding to the cooling capacity of the heat medium) in the operation mode in which the heat medium is cooled by the exchanger 14. This is because the flow rate of the circulating refrigerant circulating in the refrigerant circuit 10 in the operation mode in which the heat medium is heated by the water-refrigerant heat exchanger 14 increases.

Therefore, in the water-refrigerant heat exchanger 14 of the present embodiment, in the operation mode in which the heat load is large, the countercurrent has high heat exchange efficiency, and the operating efficiency of the refrigeration cycle device 1 can be improved.

Further, in the refrigerating cycle device 1 of the present embodiment, one of the refrigerants of the fourth refrigerant passage 104, the second three-way joint 16b, and the water-refrigerant heat exchanger 14 connecting the first three-way joint 16a and the second three-way joint 16b. The third refrigerant passage 103 or the like connecting to the entrance / exit 143b is formed by a small-diameter refrigerant pipe. Therefore, the degree of freedom in handling these pipes can be improved. As a result, the refrigerating cycle device 1 can be downsized, the amount of refrigerant charged can be reduced, and the mountability can be improved.

Here, in the single cooling mode or the like, the refrigerant decompressed by the first expansion valve 17a is flowed into one of the refrigerant inlets / outlets 143b of the water-refrigerant heat exchanger 14 via the second three-way joint 16b. Therefore, the cross-sectional area of the refrigerant pipe from the first expansion valve 17a to the one refrigerant inlet / outlet 143b of the water-refrigerant heat exchanger 14 is larger than that of the refrigerant pipe from the first three-way joint 16a to the first expansion valve 17a. It is desirable that the cross-sectional area is large.

On the other hand, in the refrigerating cycle device 1 of the present embodiment, as described above, in the single cooling mode or the like, the heat load is reduced and the refrigerant circulation flow rate circulating in the cycle is also reduced. Therefore, even if the refrigerant passage from the first expansion valve 17a to one of the refrigerant inlets / outlets 143b of the water-refrigerant heat exchanger 14 is formed by a small-diameter refrigerant pipe, the pressure loss of the refrigerant does not increase significantly.

The switching of the circuit configuration of the heat medium circuit 20 in each operation mode is not limited to the above-mentioned example.

For example, in the heating mode and the dehumidifying heating mode, if at least the heat medium flowing out from the heat medium passage 14b of the water-refrigerant heat exchanger 14 can flow into the heater core 24, the circuit configuration may be switched to another.

As an example, the control device 40 further operates the second water pump 21b in the heating mode or the dehumidifying heating mode. The control device 40 operates the second heat medium three-way valve 22b so that the refrigerant flowing out from the cooling water passage 51a of the heat generating device 51 flows out to the heat medium inlet side of the radiator 25. Further, the control device 40 opens the heat medium on-off valve 26.

As a result, in the heat medium circuit 20, as shown by the thick line in FIG. 12, the discharge port of the first water pump 21a → the water-refrigerant heat exchanger 14 → the third heat medium three-way valve 22c → the heating device 23 → the heater core 24 → A main circuit for circulating the heat medium is configured in the order of the first heat medium three-way valve 22a → the suction port of the first water pump 21a.

Further, in the heat medium circuit 20, the heat medium is connected in the order of the discharge port of the second water pump 21b → the cooling water passage 51a of the heat generating device 51 → the second heat medium three-way valve 22b → the radiator 25 → the suction port of the second water pump 21b. A sub circuit is configured to circulate the heat medium in the order of the discharge port of the second water pump 21b → the cooling water passage 50a of the battery 50 → the heat medium on-off valve 26 → the radiator 25 → the suction port of the second water pump 21b. To.

That is, in the sub circuit, a circuit is configured in which the cooling water passage 51a of the heat generating device 51 and the cooling water passage 50a of the battery 50 are connected in parallel to the flow of the heat medium pumped from the second water pump 21b. To.

In the sub-circuit, the heat absorbed from the battery 50 when the heat medium flows through the cooling water passage 50a of the battery 50, and the heat absorbed from the heat generating device 51 when the heat medium flows through the cooling water passage 51a of the heat generating device 51. Can be dissipated to the outside air by the radiator 25.

Therefore, in the heating mode or the dehumidifying heating mode, the heating or dehumidifying heating of the vehicle interior can be performed by switching the circuit configuration of the heat medium circuit 20 as shown in FIG. Further, an outside air cooling mode in which the battery 50 and the heat generating device 51 are cooled by the outside air can be executed.

Further, by closing the heat medium on-off valve 26 with respect to the heat medium circuit 20 shown in FIG. 12, the heat medium pumped from the second water pump 21b is placed between the cooling water passage 51a of the heat generating device 51 and the radiator 25. It is possible to configure a sub-circuit that circulates in. According to this, the heat generating device 51 can be cooled without unnecessarily cooling the battery 50.

As another example, in the heating mode or the dehumidifying heating mode, the control device 40 causes the heat medium flowing out from the heat medium passage 14b of the water-refrigerator heat exchanger 14 to flow out to the heating device 23 side. The heat medium three-way valve 22c is operated. Further, the control device 40 operates the first heat medium three-way valve 22a so that the heat medium flowing out from the heater core 24 flows out to one of the inlet / outlet sides of the cooling water passage 51a of the heat generating device 51. Further, the control device 40 operates the second water pump 21b. Further, the control device 40 opens the heat medium on-off valve 26.

As a result, in the heat medium circuit 20, as shown by the thick line in FIG. 13, the discharge port of the first water pump 21a → the water-coolant heat exchanger 14 → the third heat medium three-way valve 22c → the heating device 23 → the heater core 24 → A main circuit for circulating the heat medium is configured in the order of the first heat medium three-way valve 22a → the cooling water passage 51a of the heat generating device 51 → the suction port of the first water pump 21a.

Further, in the heat medium circuit 20, the secondary water medium is circulated in the order of the discharge port of the second water pump 21b → the cooling water passage 50a of the battery 50 → the heat medium on-off valve 26 → the radiator 25 → the suction port of the second water pump 21b. The circuit is configured.

In the main circuit, the first water pump 21a sucks in the heat medium heated by the waste heat of the heat generating device 51 and pumps it to the heat medium passage 14b of the water-refrigerant heat exchanger 14. The heat medium flowing into the heat medium passage 14b of the water-refrigerant heat exchanger 14 exchanges heat with the refrigerant flowing through the refrigerant passage 14a and is further heated. Therefore, in the heater core 24, in addition to the high-pressure refrigerant of the refrigerant circuit 10, the waste heat of the heat generating device 51 can be used as a heat source to heat the blown air.

Further, in the sub circuit, the heat absorbed from the battery 50 when the heat medium flows through the cooling water passage 50a of the battery 50 can be dissipated to the outside air by the radiator 25.

Therefore, in the heating mode or the dehumidifying heating mode, the heating or dehumidifying heating of the vehicle interior can be performed by switching the circuit configuration of the heat medium circuit 20 as shown in FIG. Further, by switching the circuit configuration of the heat medium circuit 20 as shown in FIG. 13, the waste heat of the heat generating device 51 can be used as a heat source for heating the blown air. Therefore, the refrigerant discharge capacity of the compressor 11 can be reduced to obtain an energy saving effect.

Further, by switching the circuit configuration of the heat medium circuit 20 as shown in FIG. 13, the outside air cooling mode in which the battery 50 is cooled by the outside air can be executed. At this time, if it is not necessary to cool the battery 50, the second water pump 21b may be stopped in the heat medium circuit 20 shown in FIG.

Further, for example, in the cooling mode and the cooling cooling mode, at least the heat medium flowing out from the heat medium passage 14b of the water-refrigerator heat exchanger 14 is used as the cooling water passage 50a of the battery 50 and the heat medium is the cooling water passage 51a of the heat generating device 51. If it can flow into either one of them, it may be switched to the other circuit configuration.

As an example, in the cooling mode or the cooling cooling mode, the control device 40 causes the heat medium flowing out from the heat medium passage 14b of the water-refrigerator heat exchanger 14 to flow out to the cooling water passage 50a side of the battery 50. , The third heat medium three-way valve 22c is operated.

Further, the control device 40 operates the second water pump 21b. Further, the control device 40 operates the first heat medium three-way valve 22a so that the heat medium flowing out from the heater core 24 flows out to the second heat medium three-way valve 22b side. Further, the control device 40 operates the second heat medium three-way valve 22b so that the heat medium flowing out from the first heat medium three-way valve 22a flows out to the heat medium inlet side of the radiator 25.

As a result, in the heat medium circuit 20, as shown by the thick line in FIG. 14, the discharge port of the first water pump 21a → the water-refrigerant heat exchanger 14 → the third heat medium three-way valve 22c → the cooling water passage 50a of the battery 50. → A main circuit that circulates the heat medium in the order of the suction port of the first water pump 21a is configured.

Further, in the heat medium circuit 20, the discharge port of the second water pump 21b → the heating device 23 → the heater core 24 → the first heat medium three-way valve 22a → the second heat medium three-way valve 22b → the radiator 25 → the suction of the second water pump 21b. While circulating the heat medium in the order of the mouth, heat is circulated in the order of the discharge port of the second water pump 21b → the cooling water passage 51a of the heat generating device 51 → the second heat medium three-way valve 22b → the radiator 25 → the suction port of the second water pump 21b. A sub-circuit that circulates the medium is configured.

That is, in the sub circuit, a circuit is configured in which the cooling water passage 51a of the heating device 23 and the heat generating device 51 is connected in parallel to the flow of the heat medium pressure-fed from the second water pump 21b. In the sub-circuit, the heat absorbed from the heat generating device 51 when the heat medium flows through the cooling water passage 51a of the heat generating device 51 can be dissipated to the outside air by the radiator 25.

Therefore, by switching the circuit configuration of the heat medium circuit 20 as shown in FIG. 14 in the cooling mode or the cooling cooling mode, the outside air cooling mode in which the heat generating device 51 is cooled by the outside air can be executed. In this operating mode, the battery 50 and the heating device 51 can be cooled in different temperature zones.

As another example, in the cooling mode or the cooling cooling mode, the control device 40 causes the heat medium flowing out from the heat medium passage 14b of the water-refrigerator heat exchanger 14 to flow out to the cooling water passage 50a side of the battery 50. In addition, the third heat medium three-way valve 22c is operated.

Further, the control device 40 operates the second water pump 21b. Further, the control device 40 operates the first heat medium three-way valve 22a so as to connect the outlet side of the heater core 24 and the suction port side of the first water pump 21a. Further, the control device 40 operates the second heat medium three-way valve 22b so that the heat medium flowing out from the cooling water passage 51a of the heat generating device 51 flows out to the heat medium inlet side of the radiator 25.

As a result, in the heat medium circuit 20, as shown by the thick line in FIG. 15, the discharge port of the first water pump 21a → the water-refrigerant heat exchanger 14 → the third heat medium three-way valve 22c → the cooling water passage 50a of the battery 50. → A main circuit that circulates the heat medium in the order of the suction port of the first water pump 21a is configured.

Further, in the heat medium circuit 20, the heat medium is connected in the order of the discharge port of the second water pump 21b → the cooling water passage 51a of the heat generating device 51 → the second heat medium three-way valve 22b → the radiator 25 → the suction port of the second water pump 21b. A circulating sub-circuit is configured. In the sub-circuit, the heat absorbed from the heat generating device 51 when the heat medium flows through the cooling water passage 51a of the heat generating device 51 can be dissipated to the outside air by the radiator 25.

Therefore, by switching the circuit configuration of the heat medium circuit 20 as shown in FIG. 15 in the cooling mode or the cooling cooling mode, the outside air cooling mode in which the heat generating device 51 is cooled by the outside air can be executed. Further, in this operation mode, the battery 50 and the heat generating device 51 can be cooled in different temperature zones.

Further, in the cooling mode or the cooling cooling mode, the circuit configuration of the heat medium circuit 20 described with reference to FIG. 11 may be changed. Specifically, the heat medium flowing out from the heat medium passage 14b of the water-refrigerant heat exchanger 14 is made to flow out to either one of the cooling water passage 50a of the battery 50 and the cooling water passage 51a of the heat generating device 51. , The operation of the third heat medium three-way valve 22c may be controlled. As a result, either the battery 50 or the heat generating device 51 may be cooled by using the heat medium cooled by the water-refrigerant heat exchanger 14 as a cooling heat source.

(Second Embodiment)
In this embodiment, an example in which the heat medium circuit 20a is adopted will be described. As shown in FIG. 16, in the heat medium circuit 20a, the cooling water passage 50a of the battery 50 is not connected to the heat medium circuit 20 described in the first embodiment. Therefore, the object to be cooled in the refrigeration cycle device 1 of the present embodiment is the heat generating device 51.

Further, in the heat medium circuit 20a, with the abolition of the cooling water passage 50a of the battery 50, the third heat medium three-way valve 22c, the heat medium passage 26a, the heat medium on-off valve 26, and the third heat medium on-off valve 26, which have been described in the first embodiment. The heat medium check valve 27c, the fourth heat medium check valve 27d, the fifth heat medium check valve 27e, and the like have also been abolished. The other configurations of the refrigeration cycle device 1 are the same as those of the first embodiment.

Next, the operation of the refrigeration cycle device 1 of the present embodiment will be described. Also in the refrigerating cycle device 1 of the present embodiment, various operation modes are switched as in the first embodiment. Further, the operation of the refrigerant circuit 10 is basically the same as that of the first embodiment. Therefore, in the following description, the operation of the heat medium circuit 20a will be mainly described.

(A) Cooling mode In the cooling mode, the control device 40 controls the operation of various controlled devices of the refrigerant circuit 10 as in the first embodiment. Therefore, in the cooling mode, the interior of the vehicle can be cooled as in the first embodiment. Further, in the cooling mode, the refrigerant does not flow into the refrigerant passage 14a of the water-refrigerant heat exchanger 14. Therefore, the heat medium is not cooled or heated in the heat medium passage 14b of the water-refrigerant heat exchanger 14.

(B) Heating mode In the heating mode, the control device 40 controls the operation of various controlled devices of the refrigerant circuit 10 as in the first embodiment. Further, the control device 40 operates the first water pump 21a so as to exhibit the reference pumping capacity for the heating mode. Further, the control device 40 operates the first heat medium three-way valve 22a so that the heat medium flowing out from the heater core 24 flows out to the suction port side of the first water pump 21a.

Therefore, in the heat medium circuit 20a in the heating mode, as shown by the thick line in FIG. 17, the discharge port of the first water pump 21a → the water-refrigerant heat exchanger 14 → the heating device 23 → the heater core 24 → the first heat medium three-way. A circuit for circulating the heat medium is configured in the order of the valve 22a → the suction port of the first water pump 21a.

Therefore, in the heating mode, the vehicle interior can be heated by operating substantially in the same manner as in the first embodiment.

(C) Dehumidifying / heating mode In the dehumidifying / heating mode, the control device 40 controls the operation of various controlled devices of the refrigerant circuit 10 as in the first embodiment. Further, the control device 40 operates the first water pump 21a and the first heat medium three-way valve 22a in the same manner as in the heating mode. Therefore, in the heat medium circuit 20a in the dehumidifying and heating mode, a circuit for circulating the heat medium is configured as in the heating mode.

Therefore, in the dehumidifying / heating mode, the dehumidifying / heating of the vehicle interior can be performed by operating substantially in the same manner as in the first embodiment.

(D) Single cooling mode In the single cooling mode, the control device 40 controls the operation of various controlled devices of the refrigerant circuit 10 as in the first embodiment.

Further, the control device 40 operates the first water pump 21a so as to exhibit the reference pumping capacity for the independent cooling mode. Further, the control device 40 operates the first heat medium three-way valve 22a so that the heat medium flowing out from the heater core 24 flows out to one of the inlet / outlet sides of the cooling water passage 51a of the heat generating device 51. The control device 40 operates the second heat medium three-way valve 22b so that the heat medium flowing out from the first heat medium three-way valve 22a does not flow out to the second heat medium three-way valve 22b side.

Therefore, in the heat medium circuit 20a in the heating mode, as shown by the thick line in FIG. 18, the discharge port of the first water pump 21a → the water-refrigerant heat exchanger 14 → the heating device 23 → the heater core 24 → the first heat medium three-way. A circuit is configured in which the heat medium is circulated in the order of the valve 22a → the cooling water passage 51a of the heating device 51 → the suction port of the first water pump 21a.

Therefore, in the single cooling mode, the heat medium cooled in the heat medium passage 14b of the water-refrigerant heat exchanger 14 can flow into the cooling water passage 51a of the heat generating device 51. As a result, in the single cooling mode of the present embodiment, the heat generating device 51 can be cooled without air conditioning in the vehicle interior.

(E) Cooling / Cooling Mode In the cooling / cooling mode, the control device 40 controls the operation of various controlled devices of the refrigerant circuit 10 as in the first embodiment. Further, the control device 40 operates the first water pump 21a, the first heat medium three-way valve 22a, and the second heat medium three-way valve 22b in the same manner as in the single cooling mode. Therefore, in the heat medium circuit 20a in the cooling cooling mode, a circuit for circulating the heat medium is configured as in the single cooling mode.

Therefore, in the cooling cooling mode, it is possible to cool the vehicle interior in the same manner as in the cooling mode, and at the same time, cool the heat generating device 51 in the same manner as in the single cooling mode.

As described above, according to the refrigerating cycle device 1 of the present embodiment, by switching the circuit configuration of the refrigerant circuit 10 and the circuit configuration of the heat medium circuit 20a, it is possible to perform air conditioning in the vehicle interior and temperature adjustment of the in-vehicle device. ..

Further, since the refrigerant circuit 10 of the present embodiment operates in the same manner as in the first embodiment, the same effect as in the first embodiment can be obtained. That is, according to the refrigerating cycle device 1 of the present embodiment, the circuit configuration of the refrigerant circuit 10 can be easily switched with a simple configuration without causing a decrease in operating efficiency.

Also in this embodiment, the switching of the circuit configuration of the heat medium circuit 20a in each operation mode is not limited to the above-mentioned example.

For example, in the heating mode and the dehumidifying heating mode, if at least the heat medium flowing out from the heat medium passage 14b of the water-refrigerant heat exchanger 14 can flow into the heater core 24, the circuit configuration may be switched to another.

Specifically, in the heating mode or the dehumidifying heating mode, the control device 40 further operates the second water pump 21b. Further, the control device 40 operates the second heat medium three-way valve 22b so that the refrigerant flowing out from the cooling water passage 51a of the heat generating device 51 flows out to the heat medium inlet side of the radiator 25.

As a result, in the heat medium circuit 20a, as shown by the thick line in FIG. 19, the discharge port of the first water pump 21a → the water-refrigerant heat exchanger 14 → the heating device 23 → the heater core 24 → the first heat medium three-way valve 22a → A main circuit for circulating the heat medium is configured in the order of the suction port of the first water pump 21a.

Further, in the heat medium circuit 20a, the heat medium is connected in the order of the discharge port of the second water pump 21b → the cooling water passage 51a of the heat generating device 51 → the second heat medium three-way valve 22b → the radiator 25 → the suction port of the second water pump 21b. A circulating sub-circuit is configured. In the sub-circuit, the heat absorbed from the heat generating device 51 when the heat medium flows through the cooling water passage 51a of the heat generating device 51 can be dissipated to the outside air by the radiator 25.

Therefore, by switching the circuit configuration of the heat medium circuit 20a as shown in FIG. 19 in the heating mode or the dehumidifying heating mode, it is possible to heat the interior of the vehicle or dehumidify and heat the heating device 51, and the heat generating device 51 is cooled by the outside air. The outside air cooling mode can be executed.

Further, in the above description, the heat in which the heat medium passage connecting the second heat medium three-way valve 22b of the heat medium circuit 20a and the suction port of the second water pump 21b and the first heat medium check valve 27a are arranged is provided. No heat medium is flowing through the medium passage. Therefore, these heat medium passages may be abolished.

On the other hand, when these heat medium passages are not abolished, the heat medium circuit 20a can be easily eliminated by abolishing the cooling water passage 50a of the battery 50 from the heat medium circuit 20 described in the first embodiment. Can be formed. That is, the productivity of the heat medium circuit 20a can be improved by sharing the constituent equipment with the heat medium circuit 20 described in the first embodiment.

(Third Embodiment)
In this embodiment, an example in which the configuration of the refrigerant circuit 10 is changed with respect to the first embodiment will be described. In the refrigerant circuit 10 of the present embodiment, the first check valve 18a and the second check valve 18b are abolished as shown in the overall configuration diagram of FIG. Then, instead of the third three-way joint 16c, a three-way joint 161 with a valve is adopted.

The detailed configuration of the valved three-way joint 161 will be described with reference to the schematic cross-sectional view of FIG. The valved three-way joint 161 has a cylindrical body portion 161a whose both ends are narrowed into a conical shape. A valve body is housed in the internal space of the body portion 161a. In the present embodiment, a ball valve 161b formed in a spherical shape is adopted as the valve body.

The outer diameter of the ball valve 161b is smaller than the inner diameter of the body 161a. Therefore, the ball valve 161b is housed so as to be displaceable in the axial direction of the internal space 161c.

A first inflow port 161d connected to a first merging / branching portion side (that is, a fifth refrigerant passage 105) is formed on one end side in the axial direction of the internal space 161c. The maximum diameter of the first inflow port 161d is smaller than the outer diameter of the ball valve 161b. Therefore, when the ball valve 161b is displaced toward one end and comes into contact with the conical inner wall surface of the body portion 161a, the first inflow port 161d is closed by the ball valve 161b.

Further, a second inflow port 161e connected to the second merging / branching portion side (that is, the sixth refrigerant passage 106) is formed on the other end side in the axial direction of the body portion 161a. The maximum diameter of the second inflow port 161e is smaller than the outer diameter of the ball valve 161b. Therefore, when the ball valve 161b is displaced toward the other end and comes into contact with the conical inner wall surface of the body portion 161a, the second inflow port 161e is closed by the ball valve 161b.

A third inflow port 161f connected to the second expansion valve 17b side (that is, the third refrigerant passage 103) is formed in the central portion of the tubular wall surface of the body portion 161a.

Therefore, in the three-way joint with a valve 161, it is shown by the solid line in FIG. 21 that the refrigerant pressure on the first inflow port 161d side is higher than the refrigerant pressure on the second inflow port 161e side as in the cooling mode and the cooling cooling mode. As described above, the ball valve 161b is displaced toward the second inflow port 161e. Then, the ball valve 161b closes the second inflow port 161e.

As a result, the fifth refrigerant passage 105 can be opened and the sixth refrigerant passage 106 can be closed. Then, the high-pressure refrigerant that has flowed into the internal space from the first inflow port 161d side can be discharged from the third inflow port 161f.

Further, in the three-way joint 161 with a valve, when the refrigerant pressure on the second inflow port 161e side is higher than the refrigerant pressure on the first inflow port 161d side as in the heating mode and the dehumidifying heating mode, as shown by the broken line in FIG. In addition, the ball valve 161b is displaced toward the first inflow port 161d. Then, the ball valve 161b closes the first inflow port 161d.

As a result, the sixth refrigerant passage 106 can be opened and the fifth refrigerant passage 105 can be closed. Then, the high-pressure refrigerant that has flowed into the internal space from the second inflow port 161e side can be discharged from the third inflow port 161f.

That is, the valved three-way joint 161 of the present embodiment integrates the body portion 161a which is the third merging branch portion and the ball valve 161b which is the refrigerant circuit switching portion.

The ball valve 161b is arranged so that one of the first inflow port 161d and the second inflow port 161e formed in the body portion 161a can be opened and the other can be closed at the same time. In other words, the ball valve 161b is arranged so that any one of the first inflow port 161d and the second inflow port 161e can be selectively closed.

In this embodiment, an example in which a spherically formed ball valve 161b is used as the valve body has been described, but either one of the first inflow port 161d and the second inflow port 161e can be selectively closed. If so, the shape of the valve body is not limited. For example, a cylindrical valve body, a valve body having a shape obtained by combining two conical shapes, or a long spherical (so-called rugby ball-shaped) valve body may be adopted.

Other configurations and operations of the refrigeration cycle device 1 are the same as those of the first embodiment. That is, according to the refrigerating cycle device 1 of the present embodiment, the circuit configuration of the refrigerant circuit 10 can be easily switched with a simple configuration without causing a decrease in operating efficiency.

Further, in the present embodiment, a three-way joint with a valve 161 is adopted as the third merging branch portion and the refrigerant circuit switching portion. According to this, when the first expansion valve 17a is in the throttled state, the high-pressure side refrigerant can flow into the valve-equipped three-way joint 161 and the low-pressure side refrigerant flows into the valve-equipped three-way joint 161. It is possible to easily realize a circuit configuration that does not allow the circuit configuration to occur.

Further, as the valve body, a ball valve 161b that is displaced by the pressure difference between the pressure of the refrigerant on the high pressure side and the pressure of the refrigerant on the low pressure side is adopted, so that the circuit configuration of the refrigerant circuit 10 does not require electrical control. Can be easily switched.

(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 refrigerating cycle device 1 according to the present invention is applied to a vehicle air-conditioning device having an in-vehicle device cooling function has been described, but the application of the refrigerating cycle device 1 is not limited to this. The application is not limited to that for vehicles, and may be applied to stationary air conditioners and the like. For example, it may be applied to an air conditioner having a server cooling function that air-conditions the room in which the server is housed while appropriately adjusting the temperature of the server (computer).

(2) Each configuration of the refrigerant circuit 10 is not limited to that disclosed in the above-described embodiment.

For example, in the above-described embodiment, the example in which the outdoor heat exchanger 13 having the modulator 134 is adopted has been described, but the modulator 134 may be abolished from the outdoor heat exchanger 13. Similarly, in the above-described embodiment, the example in which the water-refrigerant heat exchanger 14 having the liquid storage tank 142 is adopted has been described, but the liquid storage tank 142 may be abolished from the water-refrigerant heat exchanger 14.

When either the modulator 134 or the liquid storage tank 142 is abolished, the liquid storage unit on the side that becomes the heat exchanger that evaporates the low-pressure refrigerant in the operation mode in which the flow rate of the circulating refrigerant circulating in the refrigerant circuit 10 increases is abolished. Is desirable. For example, in the refrigeration cycle device in which the flow rate of the circulating refrigerant increases in the cooling mode, the liquid storage tank 142 may be abolished. In the refrigeration cycle device in which the flow rate of the circulating refrigerant increases in the heating mode, the modulator 134 may be abolished.

Further, in the above-described embodiment, the example in which the evaporation pressure adjusting valve 19 is adopted has been described, but the evaporation pressure adjusting valve 19 is not an indispensable configuration. For example, in the refrigerating cycle device in which the refrigerant evaporation temperature in the water-refrigerant heat exchanger 14 does not become 0 ° C. or lower in the cooling cooling mode, the evaporation pressure adjusting valve 19 may be abolished.

Further, in the above-described embodiment, the example in which the four-way valve 12 is adopted as the refrigerant circuit switching unit has been described. However, if the circuit configuration of the refrigerant circuit 10 can be switched in the same manner as the four-way valve 12, the refrigerant circuit switching unit can be used. Not limited.

For example, as shown in FIG. 22, two refrigerant three-way valves, a first refrigerant three-way valve 12a and a second refrigerant three-way valve 12b, may be combined to form a refrigerant circuit switching portion. As each refrigerant three-way valve, a three-type flow rate adjusting valve for a refrigerant having the same configuration as the first heat medium three-way valve 22a adopted in the heat medium circuit 20 can be adopted.

For example, as shown in FIG. 23, a refrigerant circuit switching unit may be formed by combining four refrigerant on-off valves of the first refrigerant on-off valve 121 to the fourth refrigerant on-off valve 124. As each refrigerant on-off valve, an on-off valve for a refrigerant having the same configuration as the heat medium on-off valve 26 adopted in the heat medium circuit 20 can be adopted.

Further, in the above-described embodiment, an example in which a three-way joint is adopted as the first to third merging branch portions 16a to 16c has been described, but the first to third merging branch portions 16a to 16c are the first heat medium three-way. Three types of flow rate adjusting valves for the refrigerant having the same configuration as the valve 22a and the like can be adopted.

Further, in the above-described embodiment, in each operation mode, the first expansion valve 17a or the second expansion valve 17b so that the superheat degree SH of the intake refrigerant sucked into the compressor 11 approaches the predetermined reference superheat degree KSH. The example of controlling the operation of the above has been described, but the present invention is not limited to this. In order to adjust the flow rate of the circulating refrigerant circulating in the refrigerant circuit 10 more accurately, the following may be changed.

For example, an evaporator outlet side temperature detection unit that detects the temperature of the outlet side refrigerant of the indoor evaporator 15 and an evaporator outlet side pressure detection unit that detects the pressure are added. Then, in the cooling mode, the operation of the second expansion valve 17b is controlled so that the superheat degree of the outlet-side refrigerant of the indoor evaporator 15 calculated based on the detection values of these detection units approaches the reference superheat degree KSH. May be good.

For example, a heat exchanger outlet side temperature detection unit for detecting the temperature of the refrigerant flowing out from the other refrigerant inlet / outlet 143a of the water-refrigerant heat exchanger 14 and a heat exchanger outlet side pressure detection unit for detecting the pressure are added. Then, in the single cooling mode, the operation of the first expansion valve 17b is controlled so that the superheat degree of the refrigerant flowing out from the refrigerant inlet / outlet port 143a calculated based on the detection values of these detection units approaches the reference superheat degree KSH. May be good.

For example, an outdoor unit outlet side temperature detecting unit for detecting the temperature of the refrigerant flowing out from the other refrigerant inlet / outlet port 137a of the outdoor heat exchanger 13 and an outdoor unit outlet side pressure detecting unit for detecting the pressure are added. Then, even if the operation of the first expansion valve 17b is controlled so that the superheat degree of the refrigerant flowing out from the refrigerant inlet / outlet 137a calculated based on the detection values of these detection units approaches the reference superheat degree KSH in the heating mode. good.

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

(3) The heat medium circuits 20 and 20a are not limited to those disclosed in the above-described embodiment.

Any heat medium circuit may be used as long as it can be switched to a circuit configuration in which the heat medium is circulated between the heat medium passage 14b of the water-refrigerant heat exchanger 14 and the heater core 24 at least in the heating mode or the dehumidifying heating mode. Further, the circuit configuration is such that the heat medium is circulated between the heat medium passage 14b of the water-refrigerant heat exchanger 14 and the cooling water passages 50a and 51a of the in-vehicle devices 50 and 51 at least in the single cooling mode or the cooling cooling mode. Any switchable heat medium circuit may be used.

Further, the arrangement of the battery 50 and the heat generating device 51 in the heat medium circuits 20 and 20a is not limited to those disclosed in the above-described embodiment. For example, in the heat medium circuit 20, the arrangement of the battery 50 and the heat generating device 51 may be reversed. Further, in the second embodiment, the battery 50 may be arranged instead of the heat generating device 51.

Further, the heat generating device 51 is not limited to a single number. There may be a plurality of heat generating devices 51. At this time, the cooling water passages 51a of each heat generating device 51 may be directly connected in series with each other or may be connected in parallel. Of course, the cooling water passage 51a of some of the heat generating devices 51 may be directly connected in series to the cooling water passage 50a of the battery 50, or may be connected in parallel.

Further, in the above-described embodiment, an example in which each component device arranged in the heat medium circuit 20 is operated when the refrigerating cycle is configured in the refrigerant circuit 10 has been described, but the example is described, in which the components are arranged in the heat medium circuit 20. The operation of each component is not limited to this.

For example, in the heat medium circuit 20 described in the first embodiment, a warm-up mode for warming up the heat-generating device 51 can be executed.

In the warm-up mode of the heat medium circuit 20, the control device 40 stops the compressor 11 of the refrigerant circuit 10. Further, the control device 40 operates the first water pump 21a so as to exhibit a predetermined reference pressure feeding capacity for the warm-up mode. Further, the control device 40 operates the third heat medium three-way valve 22c so that the heat medium flowing out from the heat medium passage 14b of the water-refrigerant heat exchanger 14 flows out to both sides of the heating device 23. Further, the control device 40 operates the second heat medium three-way valve 22b so that the heat medium flowing out from the first heat medium three-way valve 22a does not flow out to the second heat medium three-way valve 22b side. Further, the control device 40 energizes the heating device 23.

Therefore, in the heat medium circuit 20 in the warm-up mode, as shown by the thick line in FIG. 24, the discharge port of the first water pump 21a → the water-refrigerant heat exchanger 14 → the third heat medium three-way valve 22c → the heating device 23. → A circuit for circulating the heat medium is configured in the order of the heater core 24 → the first heat medium three-way valve 22a → the cooling water passage 51a of the heat generating device 51 → the suction port of the first water pump 21a.

As a result, in the heat medium circuit 20 in the warm-up mode, the heat medium heated by the heating device 23 can flow into the cooling water passage 51a of the heat-generating device 51 to warm the heat-generating device 51.

Further, when the warming of the heat generating device 51 is completed and the temperature of the heat medium has risen to a temperature sufficient for heating the interior of the vehicle, the waste heat heating has the same circuit configuration as the warming mode. The mode may be operated. In the waste heat heating mode, the control device 40 stops the power supply to the heating device 23. Other operations are the same as in the warm-up mode.

As a result, in the heat medium circuit 20 in the waste heat heating mode, the heat of the heat medium heated when flowing through the cooling water passage 51a of the heat generating device 51 is dissipated to the blown air by the heater core 24, and is radiated to the passenger interior. Can be heated. That is, it is possible to execute the operation of the waste heat heating mode in which the compressor 11 is stopped and the blown air is heated by the heater core 24.

In the waste heat heating mode, the compressor 11 can be stopped, so that a high energy saving effect can be obtained for the refrigeration cycle device 1 as a whole.

Similarly, in the heat medium circuit 20a described in the second embodiment, there is a warm-up mode for warming up the heat generating device 51 and a waste heat heating mode for stopping the compressor 11 to heat the interior of the vehicle. It can be carried out.

In the warm-up mode of the heat medium circuit 20a, the control device 40 stops the compressor 11 of the refrigerant circuit 10. Further, the control device 40 switches the circuit configuration of the heat medium circuit 20a in the same manner as in the single cooling mode or the cooling cooling mode. Further, the control device 40 energizes the heating device 23. As a result, in the heat medium circuit 20a in the warm-up mode, the heat medium heated by the heating device 23 can flow into the cooling water passage 51a of the heat-generating device 51 to warm the heat-generating device 51.

Further, when the warming up of the heat generating device 51 is completed and the temperature of the heat medium has risen to a temperature sufficient for heating the interior of the vehicle, the control device 40 supplies electric power to the heating device 23. To stop. Other operations are the same as in the warm-up mode. As a result, in the heat medium circuit 20a in the waste heat heating mode, the heat of the heat medium heated when flowing through the cooling water passage 51a of the heat generating device 51 is dissipated to the blown air by the heater core 24, and is radiated to the passenger interior. Can be heated.

Further, in the above-described embodiment, an example in which an ethylene glycol aqueous solution is used as a heat medium has been described, but the heat medium is not limited to this. For example, dimethylpolysiloxane, a solution containing nanofluid or the like, an antifreeze solution, an aqueous liquid medium containing alcohol or the like, a liquid medium containing oil or the like, or the like can be adopted.

10 Refrigerant circuit 13 Outdoor heat exchanger 14 Water-refrigerant heat exchanger 15 Indoor evaporator 16a to 16c 1st three-way joint (1st confluence branch) to 3rd three-way joint (3rd confluence branch)
161 Three-way joint with valve 17a, 17b First expansion valve, second expansion valve 18a, 18b First check valve (first check valve), second check valve (second check valve)
101 to 106 1st refrigerant passage to 6th refrigerant passage 20, 20a Heat medium circuit 24 Heater core 50, 51 Battery (cooling object), heat generating equipment (cooling object)

Claims (10)

A compressor (11) that compresses and discharges the refrigerant,
An outdoor heat exchanger (13) that exchanges heat between the refrigerant and the outside air,
A heat medium-refrigerant heat exchanger (14) that exchanges heat between the refrigerant and the heat medium.
An indoor evaporator (15) that exchanges heat between the refrigerant and the blown air blown to the air-conditioned space.
The first expansion valve (17a) for reducing the pressure of the refrigerant and
A second expansion valve (17b) for reducing the pressure of the refrigerant flowing into the indoor evaporator, and
A heating unit (24) that heats the blown air using the heat medium flowing out of the heat medium-refrigerant heat exchanger as a heat source.
A refrigerant circuit switching unit (12, 18a, 18b, 12a, 12b, 121 to 124) for switching the circuit configuration of the refrigerant circuit (10) for circulating the refrigerant is provided.
One refrigerant inlet / outlet (137b) of the outdoor heat exchanger is connected to a first merging / branching portion (16a) that merges or branches the flow of the refrigerant.
One refrigerant inlet / outlet (143b) of the heat medium-refrigerant heat exchanger is connected to a second merging / branching portion (16b) that merges or branches the flow of the refrigerant.
The refrigerant inlet of the indoor evaporator is connected to a third merging branch portion (16c) that merges or branches the flow of the refrigerant.
The first merging branch, the second merging branch, and the third merging branch are connected to each other.
The first expansion valve is arranged in a refrigerant passage (104) connecting the first merging branch portion and the second merging branch portion.
The second expansion valve is arranged in a refrigerant passage (103) connecting the third merging branch portion and the refrigerant inlet of the indoor evaporator.
The refrigerant circuit switching unit is
In the cooling mode for cooling the blown air, the refrigerant discharged from the compressor is made to flow into the outdoor heat exchanger, and the refrigerant flowing out of the outdoor heat exchanger is depressurized by the second expansion valve. Switching to a circuit configuration in which the refrigerant decompressed by the second expansion valve flows into the indoor evaporator,
In the heating mode for heating the blown air, the refrigerant discharged from the compressor is made to flow into the heat medium-refrigerant heat exchanger, and the refrigerant flowing out of the heat medium-refrigerant heat exchanger is expanded to the first. A refrigeration cycle device that switches to a circuit configuration in which the pressure is reduced by a valve and the refrigerant reduced by the first expansion valve flows into the outdoor heat exchanger. A cooling unit (50a, 51a) for cooling an object to be cooled (50, 51) using the heat medium flowing out of the heat medium-refrigerant heat exchanger as a cooling heat source is provided.
In the cooling mode for cooling the object to be cooled, the refrigerant circuit switching unit causes the refrigerant discharged from the compressor to flow into the outdoor heat exchanger, and the refrigerant flowing out of the outdoor heat exchanger is the first. 1. The refrigerating cycle apparatus according to claim 1, wherein the pressure is reduced by the expansion valve, and the refrigerant reduced by the first expansion valve is switched to a circuit configuration for flowing into the heat medium-refrigerant heat exchanger. In the dehumidifying / heating mode in which the blown air is dehumidified and reheated, the refrigerant circuit switching unit causes the refrigerant discharged from the compressor to flow into the heat medium-refrigerant heat exchanger to heat the heat medium-refrigerant. 1. 2. The refrigeration cycle apparatus according to 2. The refrigerant circuit switching portion includes a first switching portion (18a) that opens and closes a refrigerant passage (105) connecting the first merging branch portion and the third merging branch portion, and the second merging branch portion and the first. 3. The refrigerating cycle apparatus according to any one of claims 1 to 3, further comprising a second opening / closing portion (18b) that opens / closes a refrigerant passage (106) connecting the merging / branching portion. The first opening / closing portion is a first check valve (18a) that allows the refrigerant to flow from the first merging branch side to the third merging branch side.
The refrigeration cycle apparatus according to claim 4, wherein the second opening / closing portion is a second check valve (18b) that allows the refrigerant to flow from the second merging branch side to the third merging branch side. .. The refrigerant circuit switching portion includes a valve body (161b) displaceably arranged in the third merging / branching portion (161a).
The valve body is formed at the first merging branch portion and connected to the first merging branch portion side at the first inflow port (161c), and is formed at the third merging branch portion and the second merging branch. The refrigerating cycle apparatus according to any one of claims 1 to 3, wherein one of the second inflow outlets (161d) connected to the unit side is selectively arranged so as to be able to be closed. The heat medium-refrigerant heat exchanger has a heat medium side liquid storage unit (142) for storing the refrigerant condensed by heat exchange with the heat medium at least in the heating mode, according to claims 1 to 6. The refrigeration cycle apparatus according to any one. In the heat medium-refrigerant heat exchanger, at least in the heating mode, the flow of the refrigerant and the flow of the heat medium are opposite flows, and at least in the cooling mode, the flow of the refrigerant and the flow of the heat medium are parallel flows. The refrigerating cycle apparatus according to any one of claims 1 to 7. The outdoor heat exchanger has at least one of claims 1 to 8 having an outside air side liquid storage unit (134) for storing the refrigerant condensed by heat exchange with the outside air in the cooling mode. The refrigeration cycle device described. The passage cross-sectional area of the refrigerant passage (102) connecting the second merging branch and the one refrigerant inlet / outlet of the heat medium-refrigerant heat exchanger, connecting the second merging branch and the third merging branch. The cross-sectional area of the refrigerant passage (106) and the cross-sectional area of the refrigerant passage (103) connecting the third merging branch and the second expansion valve are both connected to the discharge port of the compressor. The refrigerating cycle apparatus according to any one of claims 1 to 9, which is set to be smaller than the passage cross-sectional area of the refrigerant passage (107).

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