JP6075058B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a vapor compression refrigeration cycle apparatus configured to be able to switch a refrigerant flow path for circulating a refrigerant.

  2. Description of the Related Art Conventionally, in an electric vehicle such as an electric vehicle or a hybrid vehicle, electric power stored in a power storage means such as a secondary battery is supplied to an electric motor via an inverter or the like to output a driving force for traveling the vehicle. When these electric devices such as secondary batteries, inverters, and electric motors are heated to high temperatures due to self-heating or the like, malfunctions may occur or the devices may be damaged. Therefore, the electric vehicle needs a temperature adjusting means for adjusting the temperature of these electric devices.

  On the other hand, Patent Document 1 discloses a vapor compression refrigeration cycle apparatus that adjusts the temperature of blown air that is blown into the passenger compartment of a vehicle air conditioner, and a temperature adjustment for adjusting the temperature of a secondary battery. An example used as a means is disclosed. Specifically, the refrigeration cycle apparatus of Patent Document 1 includes two evaporators connected in parallel, cools the air blown into the passenger compartment by one evaporator, The cooling medium for cooling the secondary battery is cooled.

  Furthermore, the refrigeration cycle apparatus of Patent Document 1 includes a refrigerant flow path switching unit that switches a refrigerant flow path of the refrigerant circulating in the cycle. This refrigerant flow switching means switches to a refrigerant flow channel that allows the refrigerant to flow only into the air conditioning evaporator in the single operation mode in which only the vehicle interior air conditioning is performed, and the temperature of the secondary battery is controlled simultaneously with the vehicle interior air conditioning. In the operation mode, the refrigerant flow path is switched to allow the refrigerant to flow into both the air conditioning evaporator and the temperature adjusting evaporator.

JP 2002-31441 A

  By the way, in the refrigeration cycle apparatus configured to be able to switch the refrigerant flow path, the internal volume of the cycle changes by switching the refrigerant flow path, so that it is enclosed in the cycle in order to exhibit the desired refrigeration capacity in the cycle The necessary amount of refrigerant that needs to be changed also changes. For this reason, in a general refrigeration cycle apparatus configured to be able to switch the refrigerant flow path, an accumulator that stores surplus refrigerant that is excessive with respect to the required refrigerant quantity is provided, and the required refrigerant quantity when the refrigerant flow path is switched is set. Absorbs fluctuations.

  However, in the refrigeration cycle apparatus of Patent Document 1, the internal volume of the cycle in the refrigerant flow path in the single operation mode and the internal volume of the cycle in the refrigerant flow path in the combined operation mode are greatly different. The difference (variation amount) from the required refrigerant amount in the operation mode is also likely to increase.

  The reason is that in a refrigeration cycle apparatus applied to a general vehicle air conditioner, a cycle component device such as a compressor is disposed in a hood in front of the vehicle, and an air conditioning evaporator is disposed in front of the vehicle interior. Furthermore, because the secondary battery is disposed on the rear side of the vehicle interior and the lower side (vehicle bottom side) of the luggage room (trunk room), the temperature adjustment evaporator is disposed on the vehicle rear side.

  That is, in the refrigeration cycle apparatus of Patent Document 1, as the amount of change in the internal volume of the cycle when the refrigerant flow path is switched, the cycle constituent device arranged in the hood and the temperature adjusting evaporator arranged on the vehicle rear side A large volume fluctuation corresponding to the internal volume of the refrigerant pipe for connecting the two can occur. For this reason, the amount of change in the required refrigerant amount when the refrigerant flow path is switched tends to increase.

  If the amount of change in the required amount of refrigerant when the refrigerant flow path is changed in this way, the internal volume of the accumulator must be increased in order to absorb this amount of change, thus increasing the size of the accumulator. It causes you to let me. As a result, the refrigeration cycle apparatus as a whole is increased in size.

  In view of the above points, an object of the present invention is to suppress an increase in the size of an accumulator that stores refrigerant in a refrigeration cycle apparatus configured to be able to switch refrigerant flow paths.

The present invention has been devised to achieve the above object. In the invention described in claim 1, the compressor (11) that compresses and discharges the refrigerant, and the outdoor that exchanges heat between the refrigerant and the outside air. The heat exchanger (17), the downstream pressure reducing means (19) for reducing the pressure of the refrigerant flowing out of the outdoor heat exchanger (17), the refrigerant decompressed by the downstream pressure reducing means (19), and the first temperature adjustment target A heat exchanger for cooling (20) for exchanging heat with an object, and separating the gas-liquid refrigerant, causing the separated gas-phase refrigerant to flow out to the suction side of the compressor (11), and the separated liquid-phase refrigerant An accumulator (24) that stores the refrigerant, a branch section (13a, 13d) that branches the flow of the high-pressure refrigerant that has been pressurized by the compressor (11), a refrigerant that is branched by the branch section (13a, 13d), and a second Auxiliary heat exchanger (22) for exchanging heat with the temperature adjustment object and branching (13a, 13d) An inflow side pipe (23) for guiding the refrigerant branched to the inlet side of the auxiliary heat exchanger (22), and a refrigerant flow path switching means (14a) for switching the refrigerant flow path of the refrigerant circulating in the cycle 14b, 15a, 15b, 19, 21),
The refrigerant flow switching means (14a... 21) includes an opening / closing means (21) for opening and closing the inflow side pipe, and the opening / closing means (21) closes the inflow side pipe (23) to perform auxiliary heat exchange. The refrigerant flow and open / close means (21) in the single operation mode for adjusting the temperature of the first temperature adjustment object by prohibiting the flow of the refrigerant into the vessel (22) open the inflow side pipe (23), thereby assisting heat. The refrigerant flow into the exchanger (22) is configured to be switchable between the refrigerant flow path in the combined operation mode for adjusting the temperature of both the first and second temperature adjustment objects,
As the single operation mode, a single cooling mode for cooling the first temperature adjustment object in the cooling heat exchanger (20) is provided,
Further, the refrigerant flow path switching means (14a ... 21) is, in the single cooling mode, the compressor (11)-> outdoor heat exchanger (17)-> branching section (13d)-> downstream pressure reducing means (19)-> heat for cooling. It switches to the refrigerant | coolant flow path which circulates a refrigerant | coolant in order of an exchanger (20)-> accumulator (24), and an opening-and-closing means (21) is an auxiliary heat exchanger rather than a branch part (13a, 13d) among inflow side piping (23). (22) It is arrange | positioned at the position close | similar to the inlet side, and a surplus refrigerant | coolant is stored in the range from a branch part (13a, 13d) to the opening-closing means (21) among inflow side piping (23) at the time of single operation mode. Features a refrigeration cycle apparatus.

  Here, in the single operation mode, the opening / closing means (21) closes the inflow side pipe (23) to inhibit the refrigerant from flowing into the auxiliary heat exchanger (22). The required refrigerant amount that needs to be sealed is smaller than the required refrigerant amount in the combined operation mode. In other words, in the single operation mode, surplus refrigerant that is surplus with respect to the required refrigerant amount is generated.

  On the other hand, according to the invention described in this claim, in the single operation mode, the high-pressure liquid-phase refrigerant that has been pressurized by the compressor (11) and cooled by the outdoor heat exchanger (17) is introduced. It can be stored in a range from the branch portions (13a, 13d) to the opening / closing means (21) in the side pipe (23). That is, the surplus refrigerant generated when switching to the single operation mode is stored not only in the accumulator (24) but also in the inflow side pipe (23) from the branch portions (13a, 13d) to the opening / closing means (21). Can do.

  Furthermore, since the opening / closing means (21) is disposed closer to the inlet side of the auxiliary heat exchanger (22) than the branch portions (13a, 13d) in the inflow side pipe (23), the branch portion (13a , 13d) to the opening / closing means (21), the volume in the inflow side pipe (23) can be sufficiently increased to store the high-pressure liquid refrigerant. Thereby, the enlargement of an accumulator (24) can be suppressed. As a result, the enlargement of the entire refrigeration cycle apparatus (10) can be suppressed.

Furthermore, in invention of Claim 2, from the compressor (11) which compresses and discharges a refrigerant | coolant, the outdoor heat exchanger (17) which heat-exchanges a refrigerant | coolant and external air, and an outdoor heat exchanger (17) A downstream side decompression means (19) for decompressing the refrigerant that has flowed out; a cooling heat exchanger (20) for exchanging heat between the refrigerant decompressed by the downstream side decompression means (19) and the first temperature adjustment object; Gas-liquid of the refrigerant is separated, and the separated gas-phase refrigerant is discharged to the suction side of the compressor (11), and the pressure is increased by the accumulator (24) for storing the separated liquid-phase refrigerant and the compressor (11). Branch parts (13a, 13d) for branching the flow of the high-pressure refrigerant, and an auxiliary heat exchanger (22) for exchanging heat between the refrigerant branched at the branch parts (13a, 13d) and the second temperature adjustment object And assisting the refrigerant branched at the branch parts (13a, 13d) An inflow side pipe (23) leading to the inlet side of the exchanger (22), and a refrigerant flow path switching means (14a, 14b, 15a, 15b, 19, 21) for switching the refrigerant flow path of the refrigerant circulating in the cycle are provided. ,
The refrigerant flow switching means (14a... 21) includes an opening / closing means (21) for opening and closing the inflow side pipe, and the opening / closing means (21) closes the inflow side pipe (23) to perform auxiliary heat exchange. The refrigerant flow and open / close means (21) in the single operation mode for adjusting the temperature of the first temperature adjustment object by prohibiting the flow of the refrigerant into the vessel (22) open the inflow side pipe (23), thereby assisting heat. The refrigerant flow into the exchanger (22) is configured to be switchable between the refrigerant flow path in the combined operation mode for adjusting the temperature of both the first and second temperature adjustment objects,
As the single operation mode, a single cooling mode for cooling the first temperature adjustment object in the cooling heat exchanger (20) is provided,
Further, the refrigerant flow path switching means (14a ... 21) is, in the single cooling mode, the compressor (11)-> outdoor heat exchanger (17)-> branching section (13d)-> downstream pressure reducing means (19)-> heat for cooling. It switches to the refrigerant | coolant flow path which circulates a refrigerant | coolant in order of an exchanger (20)-> accumulator (24), and an opening-and-closing means (21) is an auxiliary heat exchanger rather than a branch part (13a, 13d) among inflow side piping (23). (22) is located near the entrance side,
Accumulator (24) when the difference between the required amount of refrigerant that needs to be enclosed in the cycle in the combined operation mode and the required amount of refrigerant that needs to be enclosed in the cycle in the single operation mode is used as the fluctuation amount total volume in the pipe extending from the volume and the branch portion of the inner to the opening and closing means (21), wherein the refrigeration cycle apparatus change amount of the refrigerant is greater than the volume when that is the liquid phase And

  According to this, the total amount of the volume in the accumulator (24) and the volume in the pipe from the branching portions (13a, 13d) to the opening / closing means (21) is in the liquid phase state. Since it is larger than the time volume, surplus refrigerant generated when switching from the combined operation mode to the single operation mode reaches the opening / closing means (21) from the accumulator (24) and the branch portions (13a, 13d). Can be reliably stored in the piping.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a whole block diagram which shows the refrigerant | coolant flow in the air_conditionaing | cooling operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the air_conditioning | cooling + cooling operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the cooling operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the heating operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the heating + heating operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the heating operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the heating + cooling operation mode of the refrigerating-cycle apparatus of 1st Embodiment. It is a graph which shows the required refrigerant | coolant amount in the refrigerant | coolant flow path of each operation mode of 1st Embodiment. It is a graph which shows the refrigerant | coolant amount which can be stored in piping at the time of the air_conditionaing | cooling operation mode and heating operation mode of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the air_conditionaing | cooling operation mode of the refrigerating-cycle apparatus of 2nd Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the air_conditioning | cooling + cooling operation mode of the refrigerating-cycle apparatus of 2nd Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow in the cooling operation mode of the refrigerating-cycle apparatus of 2nd Embodiment. It is a graph which shows the required refrigerant | coolant amount in the refrigerant | coolant flow path of each operation mode of 2nd Embodiment. It is a graph which shows the refrigerant | coolant amount which can be stored in piping at the time of the air_conditionaing | cooling operation mode of 2nd Embodiment. It is a whole block diagram of the refrigerating-cycle apparatus of 3rd Embodiment. It is a whole refrigeration cycle apparatus block diagram of 4th Embodiment.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the refrigeration cycle apparatus 10 is applied to an electric vehicle that obtains driving force for vehicle travel from an electric motor for travel. Furthermore, in the electric vehicle according to the present embodiment, the temperature of the secondary battery 55, which is a power storage means for storing power supplied to the refrigeration cycle apparatus 10 to the air conditioning (cooling and heating) in the vehicle interior and the electric motor for traveling. Used for adjustment (heating and cooling).

  That is, the refrigeration cycle apparatus 10 of the present embodiment functions to adjust the temperature of the indoor blast air blown into the vehicle interior, and adjusts the temperature of the battery blast air blown toward the secondary battery 55. Fulfills the function of In other words, the refrigeration cycle apparatus 10 can adjust the temperature of a plurality of types of temperature adjustment objects such as indoor air (first temperature adjustment object) and battery air (second temperature adjustment object). .

  Further, the refrigeration cycle apparatus 10 is configured to be able to switch the refrigerant flow path, and as shown in FIGS. 1 to 7, the temperature of the indoor blast air and the battery blast air is switched by switching the refrigerant flow path. Make adjustments.

  Among the components of the refrigeration cycle apparatus 10, the compressor 11 is arranged in a hood in front of the vehicle, sucks refrigerant in the refrigeration cycle apparatus 10, compresses and discharges it, and has a fixed capacity with a fixed discharge capacity. It is configured as an electric compressor that rotationally drives a compression mechanism of a mold by an electric motor. The operation (the number of rotations) of the electric motor of the compressor 11 is controlled by a control signal output from a control device described later.

  The refrigeration cycle apparatus 10 employs an HFC refrigerant (specifically, R134a) as the refrigerant, and constitutes a vapor compression subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure. ing. Of course, an HFO refrigerant (specifically, R1234yf) or the like may be adopted as the refrigerant. Further, the refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port side of the compressor 11. The indoor condenser 12 is disposed in a casing 31 that forms an air passage for indoor blast air in the indoor air conditioning unit 30. The indoor condenser 12 is a heat exchanger for heating that heats the indoor blown air by causing heat exchange between the refrigerant discharged from the compressor 11 and the indoor blown air after passing through the indoor evaporator 20 described later. . The details of the indoor air conditioning unit 30 will be described later.

  The refrigerant outlet side of the indoor condenser 12 is connected to the refrigerant inlet of the first branch part 13 a that branches the flow of the refrigerant that has flowed out of the indoor condenser 12. The first branch portion 13a is formed of a three-way joint, and one of the three inflow / outflow ports is a refrigerant inflow port, and the remaining two are the refrigerant outflow ports. Such a three-way joint may be formed by joining pipes having different pipe diameters, or may be formed by providing a plurality of refrigerant passages in a metal block or a resin block.

  One refrigerant outlet of the first junction 13b is connected to one refrigerant outlet of the first branch 13a via the first on-off valve 14a. The first on-off valve 14a opens and closes the refrigerant flow path from the first branch part 13a to the first junction part 13b, and is an electromagnetic valve whose operation is controlled by a control voltage output from the control device. In addition, one refrigerant inlet / outlet of a first three-way valve 15a described later is connected to the other refrigerant outlet of the first branch portion 13a.

  The 1st junction part 13b is comprised by the same three-way joint as the 1st branch part 13a, and uses two out of three inflow / outlet as a refrigerant | coolant inflow port, and makes the remaining one a refrigerant | coolant outflow port. . Specifically, the outlet side of the first on-off valve 14a is connected to one refrigerant inlet of the first junction 13b, and one refrigerant inlet / outlet of a second three-way valve 15b described later is connected to the other refrigerant inlet. The inlet side of the outdoor heat exchanger 17 is connected to the refrigerant outlet through the heating expansion valve 16.

  Therefore, the first on-off valve 14a opens and closes the refrigerant flow path from the first branch part 13a to the first junction part 13b, whereby the refrigerant outlet side of the indoor condenser 12 and the inlet side of the heating expansion valve 16 are connected. The refrigerant flow path, the refrigerant outlet side of the indoor condenser 12 and the refrigerant passage where the inlet side of the heating expansion valve 16 is blocked can be switched. That is, the first on-off valve 14a constitutes a refrigerant flow path switching unit that switches the refrigerant flow path of the refrigerant circulating in the cycle.

  The heating expansion valve 16 is an upstream decompression unit that decompresses the refrigerant that flows out from the first junction 13b and flows into the outdoor heat exchanger 17 when heating the blown air for indoors to heat the passenger compartment. is there. Therefore, the 1st branch part 13a of this embodiment comprises the upstream branch part which branches the flow of the high-pressure refrigerant | coolant which flows from the indoor condenser 12 to the heating expansion valve 16 which is an upstream pressure reduction means.

  The heating expansion valve 16 includes an electric expansion unit configured to include a valve body configured to change the throttle opening degree and an electric actuator including a stepping motor that changes the throttle opening degree of the valve body. It is a valve and its operation is controlled by a control signal output from the control device. Further, the heating expansion valve 16 is constituted by a variable throttle mechanism with a full-open function that functions as a simple refrigerant passage with almost no refrigerant decompression effect by fully opening the throttle opening.

  The outdoor heat exchanger 17 is arranged in the bonnet, and exchanges heat between the refrigerant flowing through the inside and the outside air blown from the blower fan 17a. More specifically, the outdoor heat exchanger 17 functions as an evaporator that evaporates the low-pressure refrigerant and exerts an endothermic effect when heating the air blown in the room to heat the vehicle interior, etc. It functions as a radiator that radiates heat from the high-pressure refrigerant, for example, when cooling indoor air to cool the passenger compartment. The blower fan 17a is an electric blower in which the operation rate, that is, the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.

  The refrigerant outlet side of the outdoor heat exchanger 17 is connected to the refrigerant inlet of the second branch portion 13 c that branches the refrigerant flow that flows out of the outdoor heat exchanger 17. A refrigerant inlet of the third branch part 13d is connected to one refrigerant outlet of the second branch part 13c via a check valve 18. In addition, one refrigerant inlet of the second junction 13e is connected to the other refrigerant outlet of the second branch portion 13c via the second on-off valve 14b.

  The check valve 18 extends from the second branch portion 13c side (the refrigerant outlet side of the outdoor heat exchanger 17) to the third branch portion 13d side (the inlet side of the cooling expansion valve 19 or the inlet side of the battery expansion valve 21 described later). ) Is allowed to flow only. The refrigerant inlet side of the indoor evaporator 20 is connected to one refrigerant outlet of the third branch part 13d via the cooling expansion valve 19, and another refrigerant outlet of the first three-way valve 15a is connected to the other refrigerant outlet. A refrigerant inlet / outlet is connected.

  The cooling expansion valve 19 is an electric expansion valve having a configuration similar to that of the heating expansion valve 16, and flows out of the outdoor heat exchanger 17 when the air blown into the vehicle interior is cooled to cool the vehicle interior. It is a downstream decompression unit that decompresses the refrigerant flowing into the indoor evaporator 20. Accordingly, the third branch portion 13d of the present embodiment constitutes a downstream branch portion that branches the flow of the refrigerant flowing from the outdoor heat exchanger 17 to the cooling expansion valve 19 that is the downstream pressure reducing means.

  Further, the cooling expansion valve 19 is a fully-closed function capable of closing the refrigerant flow path from the third branch portion 13d to the refrigerant inlet side of the indoor evaporator 20 by fully closing the throttle opening of the valve body. It consists of a variable aperture mechanism with a mark.

  Therefore, the cooling expansion valve 19 opens and closes the refrigerant flow path from the third branch portion 13d to the refrigerant inlet side of the indoor evaporator 20, whereby the third branch portion 13d and the refrigerant inlet side of the indoor evaporator 20 are connected. The refrigerant flow path, and the refrigerant flow path where the refrigerant inlet side of the third evaporator 13d and the indoor evaporator 20 are blocked can be switched. In other words, the cooling expansion valve 19 functions as a downstream pressure reducing unit and also functions as a refrigerant flow path switching unit.

  The indoor evaporator 20 is disposed upstream of the indoor condenser 12 in the casing 31 of the indoor air conditioning unit 30. The indoor evaporator 20 is a cooling heat exchanger that cools the indoor blown air by exchanging heat between the refrigerant decompressed by the cooling expansion valve 19 and the indoor blown air. The refrigerant outlet side of the indoor evaporator 20 is connected to the other refrigerant inlet of the second junction 13e via the third junction 13f.

  The first three-way valve 15a connected to the other refrigerant outlet of the third branch portion 13d is an electric three-way valve whose operation is controlled by a control voltage output from the control device. The refrigerant inlet side of the auxiliary heat exchanger 22 is connected to another refrigerant inlet / outlet of the first three-way valve 15a via the battery expansion valve 21.

  More specifically, the first three-way valve 15a includes a refrigerant flow path connecting the other refrigerant outlet side of the first branch part 13a and the inlet side of the battery expansion valve 21, and a third branch part 13d. The other refrigerant outlet side and the refrigerant passage connecting the inlet side of the battery expansion valve 21 are switched. Accordingly, the first three-way valve 15a, together with the first on-off valve 14a and the like, constitutes a refrigerant flow path switching means.

  The battery expansion valve 21 is an electric expansion valve having the same configuration as the cooling expansion valve 19, and flows out of the outdoor heat exchanger 17 when the battery blowing air is cooled to cool the secondary battery 55. The pressure reducing means reduces the pressure of the refrigerant flowing into the auxiliary heat exchanger 22. Furthermore, the battery expansion valve 21 is fully closed, which can close the refrigerant flow path from the third branch portion 13d to the refrigerant inlet side of the auxiliary heat exchanger 22 by fully closing the throttle opening of the valve body. It consists of a variable aperture mechanism with functions.

  Therefore, the battery expansion valve 21 also has a function as an opening / closing means for opening and closing a refrigerant flow path from the third branch portion 13d to the refrigerant inlet side of the auxiliary heat exchanger 22, and the auxiliary heat is supplied from the third branch portion 13d. The refrigerant flow path to which the refrigerant inlet side of the exchanger 22 is connected and the refrigerant flow path from which the refrigerant inlet side of the auxiliary heat exchanger 22 is blocked from the third branch portion 13d can be switched. That is, the battery expansion valve 21 also has a function as a refrigerant flow path switching unit.

  In the present embodiment, when the first three-way valve 15a connects between the other refrigerant outlet side of the first branch part 13a and the inlet side of the battery expansion valve 21, the first branch part 13a The refrigerant flow path that reaches the inlet side of the auxiliary heat exchanger 22 via the first three-way valve 15a and the battery expansion valve 21 passes the refrigerant branched at the first branch portion 13a to the inlet side of the auxiliary heat exchanger 22. A leading inflow side pipe 23 is configured.

  On the other hand, when the first three-way valve 15a connects between the other refrigerant outlet side of the third branch part 13d and the inlet side of the battery expansion valve 21, the first three-way valve 15a extends from the third branch part 13d. The refrigerant flow path leading to the inlet side of the auxiliary heat exchanger 22 via the battery expansion valve 21 and the inflow side pipe 23 for guiding the refrigerant branched at the third branch portion 13d to the inlet side of the auxiliary heat exchanger 22 Configure.

  Further, when the first three-way valve 15a connects between the other refrigerant outlet side of the first branch portion 13a and the inlet side of the battery expansion valve 21, the battery expansion valve 21 has an inflow side pipe 23. Among these, it arrange | positions in the position nearer the inlet side of the auxiliary heat exchanger 22 than the 1st branch part 13a. On the other hand, when the first three-way valve 15a connects between the other refrigerant outlet side of the third branch part 13d and the inlet side of the battery expansion valve 21, the third branch part 13d of the inlet side pipe 23 is connected. It is arranged at a position closer to the inlet side of the auxiliary heat exchanger 22 than.

  The auxiliary heat exchanger 22 is disposed in the battery pack 50 that forms an air passage for the battery blowing air that is blown toward the secondary battery 55. The auxiliary heat exchanger 22 receives the refrigerant flowing through the battery pack 50 and the battery blowing air. Heat exchange is performed to adjust the temperature of the battery air. Details of the battery pack 50 will be described later. Further, another refrigerant inlet of the second three-way valve 15b is connected to the refrigerant outlet side of the auxiliary heat exchanger 22.

  The basic configuration of the second three-way valve 15b is the same as that of the first three-way valve 15a. The other refrigerant inlet of the second junction 13e is connected to another refrigerant inlet / outlet of the second three-way valve 15b via the third junction 13f.

  More specifically, the second three-way valve 15b includes a refrigerant flow path connecting the refrigerant outlet side of the auxiliary heat exchanger 22 and the other refrigerant inlet of the first merging portion 13b, and the auxiliary heat exchanger 22. The refrigerant flow path that connects between the refrigerant outlet side and the one refrigerant inlet of the third merging portion 13f is switched. Accordingly, the second three-way valve 15b constitutes a refrigerant flow path switching means, similarly to the first three-way valve 15a.

  The inlet side of the accumulator 24 is connected to the refrigerant outlet of the second junction 13e. The accumulator 24 separates the gas-liquid refrigerant flowing into the accumulator 24, causes the separated gas-phase refrigerant to flow out to the suction side of the compressor 11, and stores the separated liquid-phase refrigerant therein. That is, the accumulator 24 functions as a gas-liquid separation unit and also functions as a refrigerant storage unit that stores excess refrigerant in the cycle in a liquid phase state.

  Here, in the refrigeration cycle apparatus configured to be able to switch the refrigerant flow path as in the present embodiment, when the refrigerant flow path is switched, the necessary refrigerant amount that needs to be enclosed in the cycle changes. Therefore, the volume for storing the liquid-phase refrigerant in the accumulator 24 needs to be set so as to absorb the fluctuation amount of the necessary refrigerant amount.

  Therefore, in this embodiment, the maximum value of the necessary refrigerant amount that needs to be enclosed in the cycle during the combined operation mode described later and the minimum value of the necessary refrigerant amount that needs to be enclosed in the cycle during the single operation mode. And the volume in the accumulator 24 and the volume in the pipe extending from the branch portion (specifically, the first branch portion 13a or the third branch portion 13d) to the battery expansion valve 21. Is made larger than the volume when the refrigerant for the amount of fluctuation is in the liquid phase.

  Although the detailed configurations of the second and third branch portions 13c and 13d and the second and third junction portions 13e and 13f described above are not described, their basic configurations are the first branch portion 13a and the third branch portions 13a and 13f, respectively. It is the same as that of the 1st junction part 13b. The second on-off valve 14b is an electromagnetic valve that opens and closes the refrigerant flow path from the second branch part 13c to the second junction part 13e, and the basic configuration thereof is the same as that of the first on-off valve 14a. Further, the second on-off valve 14b constitutes a refrigerant flow path switching means together with the first on-off valve 14a and the like.

  Next, the indoor air conditioning unit 30 will be described. The indoor air conditioning unit 30 is for blowing the temperature-adjusted indoor blast air into the vehicle interior, and is disposed inside the instrument panel (instrument panel) at the foremost part of the vehicle interior to form an outer shell thereof. The casing 31 is configured by housing the blower 32, the above-described indoor condenser 12, the indoor evaporator 20, and the like. Therefore, the indoor air conditioning unit 30 is disposed on the front side of the vehicle interior.

  The casing 31 forms an air passage for indoor blown air inside, and is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent in strength. On the most upstream side of the air flow of the indoor blast air in the casing 31, the air volume ratio between the air volume of the internal air (vehicle interior air) introduced into the air passage in the casing 31 and the air volume of the outside air (vehicle interior air) is changed. An inside / outside air switching door is disposed.

  On the downstream side of the air flow of the inside / outside air switching device 33, a blower 32 that blows air sucked through the inside / outside air switching device 33 toward the vehicle interior is arranged. The blower 32 is an electric blower that drives a centrifugal multiblade fan (sirocco fan) with an electric motor, and the number of rotations (air flow rate) is controlled by a control voltage output from the control device.

  On the downstream side of the air flow of the blower 32, the indoor evaporator 20 and the indoor condenser 12 are arranged in this order with respect to the flow of the indoor blown air. In other words, the indoor evaporator 20 is disposed upstream of the indoor condenser 12 in the flow direction of the indoor blast air.

  Further, on the downstream side of the air flow of the indoor evaporator 20 and the upstream side of the air flow of the indoor condenser 12, the ratio of the amount of air passing through the indoor condenser 12 in the blown air after passing through the indoor evaporator 20. An air mix door 34 for adjusting the air pressure is disposed. Further, on the downstream side of the air flow of the indoor condenser 12, the blown air heated by exchanging heat with the refrigerant in the indoor condenser 12 and the blown air that is not heated bypassing the indoor condenser 12 are mixed. A mixing space 35 is provided.

  In the most downstream part of the air flow of the casing 31, an opening hole for blowing the conditioned air mixed in the mixing space 35 into the vehicle interior that is the air-conditioning target space is arranged. Specifically, the opening hole includes a face opening hole that blows air-conditioned air toward the upper body of the passenger in the passenger compartment, a foot opening hole that blows air-conditioned air toward the feet of the passenger, and an inner surface of the front window glass of the vehicle. A defroster opening hole (both not shown) for blowing the conditioned air toward is provided.

  Therefore, the temperature of the conditioned air mixed in the mixing space 35 is adjusted by adjusting the ratio of the air volume that the air mix door 34 passes through the indoor condenser 12, and the temperature of the conditioned air blown out from each opening hole. Is adjusted. That is, the air mix door 34 constitutes a temperature adjusting means for adjusting the temperature of the conditioned air blown into the vehicle interior. The air mix door 34 is driven by a servo motor (not shown) whose operation is controlled by a control signal output from the control device.

  Furthermore, on the upstream side of the air flow of the face opening hole, foot opening hole, and defroster opening hole, a face door that adjusts the opening area of the face opening hole, a foot door that adjusts the opening area of the foot opening hole, and a defroster opening hole, respectively A defroster door (none of which is shown) for adjusting the opening area is arranged.

  These face doors, foot doors, and defroster doors constitute opening hole mode switching means for switching the opening hole mode, and their operations are controlled by a control signal output from the control device via a link mechanism or the like. It is driven by a servo motor (not shown).

  Next, the battery pack 50 will be described. The battery pack 50 is arranged on the vehicle bottom surface side between the trunk room and the rear seat at the rear of the vehicle, and is blown air for batteries in a metal casing 51 that has been subjected to electrical insulation processing (for example, insulation coating). An air passage that circulates air is formed, and the blower 52, the auxiliary heat exchanger 22, the secondary battery 55, and the like are accommodated in the air passage.

  The blower 52 is arranged on the upstream side of the air flow of the auxiliary heat exchanger 22 and blows the battery air toward the auxiliary heat exchanger 22, and the operating rate is determined by the control voltage output from the control device, that is, It is an electric blower in which the number of rotations (amount of blown air) is controlled. Further, the secondary battery 55 is disposed on the downstream side of the auxiliary heat exchanger 22 in the air flow, and the downstream side of the secondary battery 55 communicates with the suction port side of the blower 52.

  Therefore, when the blower 52 is operated, the battery air that has been temperature-adjusted by the auxiliary heat exchanger 22 is blown to the secondary battery 55, and the temperature of the secondary battery 55 is adjusted. Further, the blown air for battery whose temperature has been adjusted for the secondary battery 55 is sucked into the blower 52 and blown again toward the auxiliary heat exchanger 22.

  Next, the electric control unit of this embodiment will be described. The control device is composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, performs various operations and processes based on a control program stored in the ROM, and is connected to the output side. It controls the operation of the control target devices 11, 14a, 14b, 15a, 15b, 16, 17a, 19, 21, 32, 52, and the like.

  Further, on the input side of the control device, an inside air sensor that detects the vehicle interior temperature Tr, an outside air sensor that detects the outside air temperature Tam, a solar radiation sensor that detects the amount of solar radiation Ts in the vehicle interior, Evaporator temperature) An evaporator temperature sensor that detects Tefin, a blown air temperature sensor that detects a blown air temperature TAV blown into the vehicle interior from the mixing space 35, and a temperature that detects a battery temperature Tb that is the temperature of the secondary battery 55. Various control sensor groups such as a battery temperature sensor as a detecting means are connected.

  Note that the evaporator temperature sensor of the present embodiment specifically detects the temperature of the heat exchange fins of the indoor evaporator 20. Of course, as the evaporator temperature sensor, temperature detecting means for detecting the temperature of other parts of the indoor evaporator 20 may be adopted, or temperature detecting means for directly detecting the temperature of the refrigerant itself flowing through the indoor evaporator 20. May be adopted.

  Moreover, the secondary battery 55 has a large heat capacity with respect to each component device of the refrigeration cycle apparatus 10, and a temperature distribution is likely to occur. Therefore, in the present embodiment, a plurality of temperature detection means for detecting temperatures at a plurality of locations inside and on the surface of the secondary battery 55 are used, and the average value of the detection values of the plurality of temperature detection means is determined as the battery temperature Tb. It is said.

  Moreover, in this embodiment, although the ventilation air temperature sensor which detects blowing air temperature TAV is provided, the value calculated based on evaporator temperature Tefin, discharge refrigerant temperature Td, etc. is employ | adopted as this blowing air temperature TAV. May be.

  Further, an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device, and operation signals from various operation switches provided on the operation panel are input. As various operation switches provided on the operation panel, there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, an air conditioning operation mode selection switch, and the like.

  Here, the control device of the present embodiment is configured such that the control means for controlling various control target devices connected to the output side is integrally configured, but the configuration for controlling the operation of each control target device ( Hardware and software) constitute control means for controlling the operation of each control target device.

  For example, in the control device, the configuration (hardware and software) for controlling the operation of the compressor 11 constitutes the refrigerant discharge capacity control means, and various devices 14a, 14b, 15a, 15b, which constitute the refrigerant flow switching means, The configuration for controlling the operations of 16, 19, and 21 constitutes the refrigerant flow path switching control means.

  Next, the operation of the refrigeration cycle apparatus 10 of the present embodiment having the above configuration will be described. As described above, the refrigeration cycle apparatus 10 can perform air conditioning in the passenger compartment and temperature adjustment of the secondary battery 55.

  Further, the air conditioning operation mode in the passenger compartment includes a cooling mode for cooling the passenger compartment and a heating mode for heating the passenger compartment. The secondary battery 55 is heated in the operation mode for adjusting the temperature of the secondary battery 55. There are a heating mode and a cooling mode for cooling the secondary battery 55. These operation modes are switched by executing a control program stored in the storage circuit in advance by the control device.

  In this control program, the operation signal of the operation panel and the detection signal of the control sensor group are read, the control state of various control target devices is determined based on the read detection signal and the value of the operation signal, and the determined control state The control routine of outputting a control signal or a control voltage to various devices to be controlled is repeated.

  And about the operation mode at the time of air-conditioning of a vehicle interior, when the air conditioning operation switch is turned on (ON) and cooling is selected with the selection switch when the operation signal of the operation panel is read Is switched to the cooling mode, and when heating is selected by the selection switch while the air conditioning operation switch is turned on (ON), the mode is switched to the heating mode.

  As for the operation mode when adjusting the temperature of the secondary battery 55, the battery temperature Tb is equal to or lower than the first reference temperature Tk1 (15 ° C. in the present embodiment) when the detection signal of the control sensor group is read. Is switched to a heating mode in which the secondary battery 55 is heated. When the battery temperature Tb is equal to or higher than the second reference temperature Tk2 (30 ° C. in this embodiment), the secondary battery is cooled. Switch to cooling mode.

  Here, the output characteristics of the secondary battery 55 will be described. As this embodiment, a lithium ion battery is employed as the secondary battery 55. In the secondary battery 55, when the temperature is lower than 10 ° C., sufficient input / output characteristics cannot be obtained because the chemical reaction does not proceed. That is, when the secondary battery 55 becomes 10 ° C. or lower, the output of the secondary battery 55 is lowered and the vehicle cannot be driven.

  On the other hand, when the temperature is high, particularly when the temperature is 40 ° C. or higher, the control device cuts off the input / output of power in order to prevent the secondary battery 55 from deteriorating. Therefore, the vehicle cannot be driven even when the secondary battery 55 reaches a high temperature of 40 ° C. or higher. In other words, in order to drive the vehicle by fully utilizing the capacity of the secondary battery 55 of the present embodiment, it is necessary to manage the temperature of the secondary battery 55 in a range of approximately 10 ° C. or more and 40 ° C. or less. .

  Therefore, in the present embodiment, the battery temperature Tb is equal to or lower than the first reference temperature Tk1, with the temperature range (10 ° C. to 40 ° C.) determined so that the capacity of the secondary battery 55 can be fully utilized as the reference temperature range. When the battery temperature Tb is over the second reference temperature Tk2, the battery temperature Tb is within the reference temperature range by switching to the cooling mode. . Subsequently, each operation mode will be described.

(A) Cooling operation mode The cooling operation mode is an operation mode in which the passenger compartment is cooled without adjusting the temperature of the secondary battery 55. In this operation mode, the operation switch of the operation panel is turned on (ON), cooling is selected by the selection switch, the battery temperature Tb is higher than the first reference temperature Tk1, and the second reference temperature Tk2 Run when it is lower.

  In the cooling operation mode, the control device opens the first on-off valve 14a, closes the second on-off valve 14b, and connects the third branch portion 13d and the battery expansion valve 21 to connect the first three-way valve 15a. The operation is controlled, the operation of the second three-way valve 15b is controlled so as to connect the auxiliary heat exchanger 22 and the third merging portion 13f, the heating expansion valve 16 is fully opened, and the cooling expansion valve 19 is a throttled state that exerts a pressure reducing action, and the battery expansion valve 21 is fully closed.

  As a result, in the cooling operation mode, the refrigeration cycle apparatus 10 causes the outdoor heat exchange of the compressor 11 → the indoor condenser 12 → (the first on-off valve 14a → the heating expansion valve 16 →) as shown by the thick arrows in FIG. It is switched to the refrigerant flow path in which the refrigerant circulates in the order of the unit 17 → (the check valve 18 →) the third branch part 13 d → the cooling expansion valve 19 → the indoor evaporator 20 → the accumulator 24 → the compressor 11.

  With this refrigerant flow path configuration, the control device calculates a target blowing temperature TAO, which is a target temperature of air blown into the vehicle interior, based on the read detection signal and operation signal values. Furthermore, a control apparatus determines the operating state of the various control object apparatus connected to the output side of a control apparatus based on the calculated target blowing temperature TAO and the detection signal of a sensor group.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11 is determined as follows. First, the target evaporator outlet temperature TEO of the indoor evaporator 20 is determined based on the target outlet temperature TAO with reference to a control map stored in advance in the control device.

  And based on the deviation of this target evaporator blowing temperature TEO and the blowing air temperature from the indoor evaporator 20 detected by the evaporator temperature sensor, the blowing air temperature from the indoor evaporator 20 is changed using a feedback control method. A control signal output to the electric motor of the compressor 11 is determined so as to approach the target evaporator outlet temperature TEO.

  The control voltage output to the electric motor of the blower 32 of the indoor air conditioning unit 30 is determined based on the target blowing temperature TAO with reference to a control map stored in advance in the storage circuit. Specifically, the control voltage output to the electric motor is maximized in the extremely low temperature range (maximum cooling range) and the extremely high temperature range (maximum heating range) of the target blowing temperature TAO, and the blown air amount is controlled near the maximum amount. As the blowout temperature TAO approaches the intermediate temperature range, the amount of blown air is reduced.

  As for the control signal output to the servo motor of the air mix door 34, the temperature of the air blown into the vehicle interior is set using the target blow temperature TAO, the blown air temperature Tefin of the indoor evaporator 20, etc. Is determined to be a desired temperature of the occupant set by.

  In the operation mode in which the vehicle interior is cooled as in the cooling operation mode, the air mix door 34 may be operated so that the air mix door 34 closes the air passage on the indoor condenser 12 side.

  With respect to the control signal output to the cooling expansion valve 19, the target subcooling in which the degree of supercooling of the refrigerant flowing into the cooling expansion valve 19 is determined so that the coefficient of performance (COP) of the cycle is substantially maximum. Determined to approach the degree. Then, a control signal or a control voltage is output from the control device to the control target device so as to obtain the control state determined as described above.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 and radiates heat by exchanging heat with the indoor blowing air after passing through the indoor evaporator 20. The refrigerant flowing out of the indoor condenser 12 flows into the outdoor heat exchanger 17 through the first on-off valve 14a and the heating expansion valve 16.

  The refrigerant flowing into the outdoor heat exchanger 17 exchanges heat with the outside air blown from the blower fan 17a to further dissipate heat. Since the second on-off valve 14b is closed, the refrigerant that has flowed out of the outdoor heat exchanger 17 flows from the second branch portion 13c into the third branch portion 13d via the check valve 18.

  Since the battery expansion valve 21 is fully closed, the refrigerant flowing into the third branch portion 13d flows out from one refrigerant outlet to the cooling expansion valve 19 side and is depressurized by the cooling expansion valve 19. The The refrigerant decompressed by the cooling expansion valve 19 flows into the indoor evaporator 20, absorbs heat from the indoor air blown by the blower 32, and evaporates. Thereby, the indoor blowing air is cooled.

  The refrigerant that has flowed out of the indoor evaporator 20 flows into the accumulator 24 through the third merging portion 13f and the second merging portion 13e. The refrigerant flowing into the accumulator 24 is separated into gas and liquid, the separated liquid phase refrigerant is stored in the accumulator 24 as surplus refrigerant, and the gas-phase refrigerant flowing out of the accumulator 24 is sucked into the compressor 11 and compressed again. .

  As described above, in the cooling operation mode, the indoor blowing air is cooled by the indoor evaporator 20 so that the vehicle interior can be cooled.

  In the cooling operation mode of the present embodiment, the battery expansion valve 21 having a function as an opening / closing means is closed, and the indoor blown air (first temperature adjustment object) is cooled. Therefore, the cooling operation mode is an operation mode corresponding to the single operation mode described in the claims. Further, in the single operation mode, the indoor evaporator 20 (cooling heat exchanger) is used for indoor use. This corresponds to the single cooling mode for cooling the blown air (first temperature adjustment object).

(B) Cooling + cooling operation mode The cooling + cooling operation mode is an operation mode in which the secondary battery 55 is cooled at the same time as cooling the passenger compartment. This operation mode is executed when the operation switch of the operation panel is turned on (ON), cooling is selected by the selection switch, and the battery temperature Tb becomes equal to or higher than the second reference temperature Tk2.

  In the cooling + cooling operation mode, the control device opens the first on-off valve 14a, closes the second on-off valve 14b, and connects the first branch valve 13b and the battery expansion valve 21 to connect the first three-way valve. 15a, the operation of the second three-way valve 15b is controlled so as to connect between the auxiliary heat exchanger 22 and the third merging portion 13f, and the heating expansion valve 16 is fully opened, for cooling. The expansion valve 19 and the battery expansion valve 21 are set to the throttle state.

  As a result, in the cooling + cooling operation mode, the refrigeration cycle apparatus 10 has the compressor 11 → the indoor condenser 12 → (the first on-off valve 14a → the heating expansion valve 16 →) as shown by the thick arrow in FIG. The refrigerant circulates in the order of heat exchanger 17 → (check valve 18) third branch 13 d → cooling expansion valve 19 → indoor evaporator 20 → third merger 13 f → accumulator 24 → compressor 11. The refrigerant flow path is switched to the three branch portion 13d → battery expansion valve 21 → auxiliary heat exchanger 22 → third merging portion 13f → accumulator 24 in this order. That is, in the cooling + cooling operation mode, a refrigerant flow path in which the indoor evaporator 20 and the auxiliary heat exchanger 22 are connected in parallel is configured.

  Further, the control device determines the operating states of the compressor 11, the cooling expansion valve 19, the blower 32, and the air mix door 34 as in the cooling operation mode. The control signal output to the battery expansion valve 21 is determined so that the throttle opening degree of the battery expansion valve 21 becomes a predetermined throttle opening degree, and is supplied to the electric motor of the blower 52 of the battery pack 50. The output control voltage is determined so that the blowing capacity of the blower 52 becomes a predetermined predetermined blowing capacity.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling + cooling operation mode, the high-pressure refrigerant discharged from the compressor 11 flows in the order of the indoor condenser 12 → the outdoor heat exchanger 17 → the check valve 18 as in the cooling operation mode. , Flows into the third branch 13d.

  The refrigerant flowing out from one refrigerant outlet of the third branch portion 13d is decompressed by the cooling expansion valve 19 and flows into the indoor evaporator 20. The refrigerant flowing into the indoor evaporator 20 absorbs heat from the indoor air blown by the blower 32 and evaporates. Thereby, the indoor blowing air is cooled. The refrigerant flowing out from the indoor evaporator 20 flows into the accumulator 24 as in the cooling operation mode.

  In addition, the refrigerant flowing out from the other refrigerant outlet of the third branch portion 13d is depressurized until it becomes a low-pressure refrigerant at the battery expansion valve 21 arranged in the inflow side pipe 23 and flows into the auxiliary heat exchanger 22. . The refrigerant flowing into the auxiliary heat exchanger 22 absorbs heat from the battery air blown by the blower 52 and evaporates. Thereby, battery air is cooled.

  The refrigerant that has flowed out of the auxiliary heat exchanger 22 flows into the accumulator 24 through the third merge portion 13f and the second merge portion 13e. The gas-phase refrigerant separated by the accumulator 24 is sucked into the compressor 11 and compressed again.

  As described above, in the cooling + cooling operation mode, the indoor blowing air is cooled by the indoor evaporator 20 to cool the vehicle interior, and the battery blowing air is cooled by the auxiliary heat exchanger 22. Thus, the secondary battery 55 can be cooled.

  In the cooling + cooling operation mode of the present embodiment, the battery expansion valve 21 having a function as an opening / closing means is opened, and the indoor blown air (first temperature adjustment object) and the battery blown air (second temperature). Both adjustment objects) are cooled.

  Therefore, the cooling + cooling operation mode is an operation mode corresponding to the combined operation mode described in the claims, and further, in the combined operation mode, the indoor evaporator 20 (cooling heat exchanger) This is compatible with a combined cooling mode in which the blown air for air (first temperature adjustment object) is cooled, and the auxiliary heat exchanger 22 is used for cooling the blown air for battery (second temperature adjustment object).

(C) Cooling operation mode The cooling operation mode is an operation mode in which the secondary battery 55 is cooled without air conditioning of the passenger compartment. This operation mode is executed when the operation switch of the operation panel is not turned on (OFF) and when the battery temperature Tb becomes equal to or higher than the second reference temperature Tk2.

  In the cooling operation mode, the control device opens the first on-off valve 14a, closes the second on-off valve 14b, and connects the third branch portion 13d and the battery expansion valve 21 to connect the first three-way valve 15a. The operation is controlled, the operation of the second three-way valve 15b is controlled so as to connect the auxiliary heat exchanger 22 and the third merging portion 13f, the heating expansion valve 16 is fully opened, and the cooling expansion valve 19 is fully closed, and the battery expansion valve 21 is in the throttled state.

  As a result, in the cooling operation mode, the refrigeration cycle apparatus 10 causes the outdoor heat exchange of the compressor 11 → the indoor condenser 12 → (the first on-off valve 14a → the heating expansion valve 16 →) as shown by the thick arrows in FIG. In the refrigerant flow path in which the refrigerant circulates in the order of the vessel 17 → (check valve 18) third branch part 13 d → battery expansion valve 21 → auxiliary heat exchanger 22 → third junction 13 f → accumulator 24 → compressor 11. Can be switched.

  Further, the control device determines the operating states of the compressor 11, the battery expansion valve 21, and the blower 52 of the battery pack 50, similarly to the cooling + cooling operation mode. Further, the control signal output to the blower 32 of the indoor air conditioning unit 30 is determined to stop the blower 32, and the control signal output to the servo motor of the air mix door 34 is determined by the air mix door 34 being indoors. The air passage on the condenser 12 side is determined to be closed.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. At this time, since the operation of the blower 32 is stopped and the air mix door 34 fully closes the air passage on the indoor condenser 12 side, the refrigerant flowing into the indoor condenser 12 exchanges heat with the indoor blown air. Without flowing out from the indoor condenser 12. Accordingly, the indoor blown air is not heated.

  The refrigerant that has flowed out of the indoor condenser 12 flows in the order of the outdoor heat exchanger 17 → the check valve 18 and flows into the third branch portion 13d, as in the cooling + cooling operation mode. Since the cooling expansion valve 19 is fully closed, the refrigerant flowing into the third branch portion 13d flows out from the other refrigerant outlet to the battery expansion valve 21 and is decompressed by the battery expansion valve 21. The

  The refrigerant decompressed by the battery expansion valve 21 flows into the auxiliary heat exchanger 22, absorbs heat from the battery air blown by the blower 52, and evaporates. Thereby, battery air is cooled.

  The refrigerant that has flowed out of the auxiliary heat exchanger 22 flows into the accumulator 24 through the third merge portion 13f and the second merge portion 13e. Then, the liquid-phase refrigerant separated by the accumulator 24 is stored as an excess refrigerant in the accumulator 24, and the gas-phase refrigerant separated by the accumulator 24 is sucked into the compressor 11 and compressed again.

  As described above, in the cooling operation mode, the battery air is cooled by the auxiliary heat exchanger 22 and the secondary battery 55 can be cooled.

  Note that, in the cooling operation mode of the present embodiment, the battery expansion valve 21 having a function as an opening / closing means is opened, and the battery blowing air (second temperature adjustment object) is cooled, but the indoor blowing air ( The temperature of the first temperature adjustment object) is not adjusted. Therefore, the cooling operation mode can be expressed as a second single operation mode (second single cooling mode) different from the single operation mode described in the claims.

(D) Heating operation mode The heating operation mode is an operation mode in which the passenger compartment is heated without adjusting the temperature of the secondary battery 55. In this operation mode, the operation switch of the operation panel is turned on (ON), heating is selected by the selection switch, the battery temperature Tb is higher than the first reference temperature Tk1, and the second reference temperature Tk2 Run when it is lower.

  In the heating operation mode, the control device opens the first on-off valve 14a, opens the second on-off valve 14b, and connects the first branch portion 13a and the battery expansion valve 21 to the first three-way valve 15a. The operation is controlled, the operation of the second three-way valve 15b is controlled so as to connect between the auxiliary heat exchanger 22 and the first joining portion 13b, and the heating expansion valve 16 is set in the throttle state, and the expansion for cooling is performed. The valve 19 is fully closed and the battery expansion valve 21 is fully closed.

  As a result, in the heating operation mode, the refrigeration cycle apparatus 10, as shown by the thick arrow in FIG. 4, the compressor 11 → the indoor condenser 12 → (the first on-off valve 14 a →) the heating expansion valve 16 → the outdoor heat exchange. It is switched to the refrigerant flow path in which the refrigerant circulates in the order of the vessel 17 → (second on-off valve 14b →) accumulator 24 → compressor 11.

  Further, the control device controls the operation of the blower 32 of the indoor air conditioning unit 30 as in the cooling operation mode. Further, with respect to the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11, the blown air temperature TAV detected by the blown air temperature sensor is determined so as to approach the target blowing temperature TAO. The In addition, the target blowing temperature TAO determined at the time of heating of a vehicle interior is about 40 to 60 degreeC.

  With respect to the control signal output to the heating expansion valve 16, the target subcooling in which the degree of supercooling of the refrigerant flowing into the heating expansion valve 16 is determined so that the coefficient of performance (COP) of the cycle is substantially maximum. Determined to approach the degree. The control signal output to the servo motor of the air mix door 34 is determined so that the air mix door 34 fully opens the air passage on the indoor condenser 12 side.

  Therefore, in the refrigeration cycle apparatus 10 in the heating operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 and radiates heat by exchanging heat with the indoor blown air after passing through the indoor evaporator 20. Thereby, the air for room | chamber interior is heated. The refrigerant flowing out of the indoor condenser 12 is decompressed by the heating expansion valve 16. The refrigerant decompressed by the heating expansion valve 16 flows into the outdoor heat exchanger 17, absorbs heat from the outside air blown from the blower fan 17a, and evaporates.

  The refrigerant that has flowed out of the outdoor heat exchanger 17 flows into the accumulator 24 through the second on-off valve 14b and the second junction 13e because the cooling expansion valve 19 is fully closed. Then, the liquid-phase refrigerant separated by the accumulator 24 is stored as an excess refrigerant in the accumulator 24, and the gas-phase refrigerant separated by the accumulator 24 is sucked into the compressor 11 and compressed again.

  As described above, in the heating operation mode, the indoor air can be heated by the indoor condenser 12 to heat the vehicle interior.

  In the heating operation mode of the present embodiment, the battery expansion valve 21 that also functions as an opening / closing means is closed, and the indoor blown air (first temperature adjustment object) is heated. Accordingly, the heating operation mode is an operation mode corresponding to the single operation mode described in the claims. Furthermore, in the single operation mode, the indoor condenser 12 (heating heat exchanger) is used for indoor use. This corresponds to a single heating mode for cooling the blown air (first temperature adjustment object).

(E) Heating + Heating Operation Mode The heating + heating operation mode is an operation mode in which the secondary battery 55 is heated at the same time as heating the vehicle interior. More specifically, in this operation mode, when the operation switch of the operation panel is turned on (ON), heating is selected by the selection switch, and the battery temperature Tb becomes equal to or lower than the first reference temperature Tk1. Executed.

  In the heating + heating operation mode, the control device closes the first on-off valve 14a, opens the second on-off valve 14b, and connects the first branch portion 13a and the battery expansion valve 21 to connect the first three-way valve. 15a is controlled, the operation of the second three-way valve 15b is controlled so as to connect between the auxiliary heat exchanger 22 and the first junction 13b, and the heating expansion valve 16 is set in the throttle state, The expansion valve 19 is fully closed, and the battery expansion valve 21 is in the throttle state.

  As a result, in the heating + heating operation mode, the refrigeration cycle apparatus 10 has the compressor 11 → the indoor condenser 12 → the first branch portion 13a → (the first three-way valve 15a →) battery as shown by the thick arrows in FIG. Expansion valve 21 → auxiliary heat exchanger 22 → (second three-way valve 15b → first junction 13b) → heating expansion valve 16 → outdoor heat exchanger 17 → (second on-off valve 14b →) accumulator 24 → compressor 11 is switched to a refrigerant flow path through which the refrigerant circulates. That is, in the heating + heating operation mode, a refrigerant flow path in which the indoor condenser 12 and the auxiliary heat exchanger 22 are connected in series is configured.

  Further, the control device determines the operating states of the compressor 11, the heating expansion valve 16, the blower 32, and the air mix door 34 in the same manner as in the heating operation mode. The operating state of the blower 52 is determined. In addition, for the control signal output to the battery expansion valve 21, the refrigerant pressure in the auxiliary heat exchanger 22 can adjust the battery temperature Tb within an appropriate temperature range (in this embodiment, 10 ° C. to 40 ° C.). The intermediate pressure is determined.

  Therefore, in the refrigeration cycle apparatus 10 in the heating + heating operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 and radiates heat by exchanging heat with the indoor blowing air, as in the heating mode. . Thereby, the air for room | chamber interior is heated. Since the first on-off valve 14a is closed, the refrigerant flowing out of the indoor condenser 12 is reduced to an intermediate pressure at the battery expansion valve 21 via the first branch portion 13a and the first three-way valve 15a. .

  The intermediate pressure refrigerant decompressed by the battery expansion valve 21 flows into the auxiliary heat exchanger 22 and radiates heat by exchanging heat with the battery air. Thereby, battery air is heated. And the warming-up of the secondary battery 55 is implement | achieved by the blowing air for batteries heated to the secondary battery 55 by the air blower 52. FIG. At this time, the refrigerant pressure in the auxiliary heat exchanger 22 is adjusted to a pressure at which the battery temperature Tb is about 10 ° C. to 40 ° C.

  The refrigerant that has flowed out of the auxiliary heat exchanger 22 flows into the heating expansion valve 16 through the second three-way valve 15b and the first junction 13b, and is reduced in pressure until the pressure becomes low. The low-pressure refrigerant decompressed by the heating expansion valve 16 flows into the outdoor heat exchanger 17, absorbs heat from the outside air blown from the blower fan 17a, and evaporates.

  The refrigerant that has flowed out of the outdoor heat exchanger 17 flows into the accumulator 24 through the second on-off valve 14b and the second junction 13e because the cooling expansion valve 19 is fully closed. The gas-phase refrigerant separated by the accumulator 24 is sucked into the compressor 11 and compressed again.

  As described above, in the heating + heating operation mode, the indoor blower air is heated by the indoor condenser 12 to heat the vehicle interior, and the battery blown air is heated by the auxiliary heat exchanger 22. Thus, the secondary battery 55 can be heated.

  In the heating + heating operation mode of the present embodiment, the battery expansion valve 21 having a function as an opening / closing means is opened, and the indoor blown air (first temperature adjustment object) and the battery blown air (second temperature). Both of the adjustment objects are heated.

  Accordingly, the heating + heating operation mode is an operation mode corresponding to the combined operation mode described in the claims, and further, in the combined operation mode, the indoor condenser 12 (heating heat exchanger) It corresponds to the combined heating mode in which the blast air (first temperature adjustment object) is heated and the battery blast air (second temperature adjustment object) is heated by the auxiliary heat exchanger 22.

(F) Heating operation mode The heating operation mode is an operation mode in which the secondary battery 55 is heated without air conditioning of the passenger compartment. This operation mode is executed when the operation switch of the operation panel is not turned on (OFF) and when the battery temperature Tb becomes equal to or lower than the first reference temperature Tk1.

  In this heating operation mode, the control device closes the first on-off valve 14a, opens the second on-off valve 14b, and between the first branch portion 13a and the battery expansion valve 21 as in the heating + heating operation mode. The operation of the first three-way valve 15a is controlled so as to be connected, the operation of the second three-way valve 15b is controlled so as to connect between the auxiliary heat exchanger 22 and the first junction 13b, and further, the expansion for heating The valve 16 is in the throttle state, the cooling expansion valve 19 is fully closed, and the battery expansion valve 21 is fully opened.

  As a result, in the heating operation mode, the refrigeration cycle apparatus 10 is switched to the refrigerant flow path through which the refrigerant flows exactly as in the heating + heating operation mode, as indicated by the thick arrows in FIG.

  Further, the control device determines the operating states of the compressor 11, the heating expansion valve 16, the battery expansion valve 21, and the blower 52 of the battery pack 50, as in the heating + heating operation mode. Further, the control signal output to the blower 32 of the indoor air conditioning unit 30 is determined to stop the blower 32, and the control signal output to the servo motor of the air mix door 34 is determined by the air mix door 34 being indoors. The air passage on the condenser 12 side is determined to be fully closed.

  Therefore, in the refrigeration cycle apparatus 10 in the heating operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12. At this time, since the operation of the blower 32 is stopped and the air mix door 34 fully closes the air passage on the indoor condenser 12 side, the refrigerant flowing into the indoor condenser 12 exchanges heat with the indoor blown air. Without flowing out from the indoor condenser 12. Accordingly, the indoor blown air is not heated.

  The refrigerant that has flowed out of the indoor condenser 12 flows into the auxiliary heat exchanger 22 via the first branch portion 13a, the first three-way valve 15a, and the battery expansion valve 21 in the same manner as in the heating + heating operation mode. Heat is dissipated by exchanging heat with the air. Thereby, battery air is heated. The subsequent operations are the same as those in the heating + heating operation mode.

  As described above, in the heating operation mode, the battery air is heated by the auxiliary heat exchanger 22 and the secondary battery 55 can be heated.

  In the heating operation mode of the present embodiment, the battery expansion valve 21 having a function as an opening / closing means is opened, and the battery air (second temperature adjustment object) is heated, but the indoor air ( The temperature of the first temperature adjustment object) is not adjusted. Therefore, the heating operation mode can be expressed as a second single operation mode (second single heating mode) different from the single operation mode described in the claims.

(G) Heating + cooling operation mode Each of the operation modes (a) to (c) described above is executed mainly for cooling the vehicle interior or the secondary battery 55 when the outside air temperature is relatively high, such as in summer. Each of the operation modes described in (d) to (f) is executed mainly for heating the passenger compartment or the secondary battery 55 when the outside air temperature is relatively low such as in winter.

  On the other hand, in the spring or autumn, the battery temperature Tb is reduced by the self-heating of the secondary battery 55 while heating is selected by the selection switch while the operation switch of the operation panel is turned on (ON). The temperature may be higher than the second reference temperature Tk2. In such a case, the operation in the heating + cooling operation mode is executed.

  In the heating + cooling operation mode, the control device opens the first on-off valve 14a, closes the second on-off valve 14b, and connects the first branch valve 13b and the battery expansion valve 21 to connect the first three-way valve. 15a, the operation of the second three-way valve 15b is controlled so as to connect between the auxiliary heat exchanger 22 and the third merging portion 13f, and the heating expansion valve 16 is brought into a throttled state for cooling. The expansion valve 19 is fully closed, and the battery expansion valve 21 is in the throttle state.

  As a result, in the heating + cooling operation mode, the refrigeration cycle apparatus 10 has the compressor 11 → the indoor condenser 12 → (the first on-off valve 14a →) the heating expansion valve 16 → the outdoor, as shown by the thick arrows in FIG. Refrigerant flow in which the refrigerant circulates in the order of heat exchanger 17 → (check valve 18) third branch 13 d → battery expansion valve 21 → auxiliary heat exchanger 22 → third junction 13 f → accumulator 24 → compressor 11. Switch to the road.

  Further, the control device determines the operating states of the compressor 11, the heating expansion valve 16, the blower 32 of the indoor air conditioning unit 30, and the air mix door 34, as in the heating operation mode, and the battery as in the cooling operation mode. The operating states of the expansion valve 21 and the blower 52 of the battery pack 50 are determined.

  Therefore, in the refrigeration cycle apparatus 10 in the heating + cooling operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 and radiates heat by exchanging heat with the indoor blowing air. Thereby, the air for room | chamber interior is heated. The refrigerant flowing out of the indoor condenser 12 is decompressed by the heating expansion valve 16. The refrigerant decompressed by the heating expansion valve 16 flows into the outdoor heat exchanger 17, absorbs heat from the outside air blown from the blower fan 17a, and evaporates.

  The refrigerant that has flowed out of the outdoor heat exchanger 17 flows in the order of the second branch portion 13c → the check valve 18 → the third branch portion 13d, and flows into the battery expansion valve 21 to be decompressed, as in the cooling operation mode. . The refrigerant decompressed by the battery expansion valve 21 flows into the auxiliary heat exchanger 22, absorbs heat from the battery air blown by the blower 52, and evaporates. Thereby, battery air is cooled. The subsequent operation is the same as in the cooling operation mode.

  As described above, in the heating + cooling operation mode, the indoor blast air can be heated by the indoor condenser 12 to heat the vehicle interior, and the battery blast air is cooled by the auxiliary heat exchanger 22. Thus, the secondary battery 55 can be cooled.

  In the heating + cooling operation mode of the present embodiment, the battery expansion valve 21 having a function as an opening / closing means is opened, and the indoor blown air (first temperature adjustment object) and the battery blown air (second temperature). The temperature of both of the objects to be adjusted) is adjusted.

  Therefore, the heating + cooling operation mode is an operation mode corresponding to the combined operation mode described in the claims, and further, in the combined operation mode, the indoor condenser 12 (heating heat exchanger) It corresponds to the combined heating / cooling mode in which the blast air (first temperature adjustment object) is heated and the battery blast air (second temperature adjustment object) is cooled by the auxiliary heat exchanger 22.

  Further, in the heating + cooling operation mode of the present embodiment, the control device causes the heating expansion valve 16 to be in the throttled state and causes the outdoor heat exchanger 17 to function as an evaporator. The refrigerant evaporation temperature in the exchanger 17 and the refrigerant evaporation temperature in the auxiliary heat exchanger 22 may be equalized.

  Further, the control device may fully open the heating expansion valve 16 (or increase the throttle opening of the heating expansion valve 16), and allow the outdoor heat exchanger 17 to function as a radiator. In this case, the battery expansion valve 21 may be in the throttle state, and the refrigerant decompressed by the battery expansion valve 21 may be evaporated by the auxiliary heat exchanger 22.

  Thus, by making the outdoor heat exchanger 17 function as an evaporator or a radiator, the heat absorption amount of the refrigerant can be changed, and the heating capacity of the indoor blast air in the indoor condenser 12 can be changed. Therefore, for example, when the outdoor air temperature Tam is higher than a predetermined temperature, the outdoor heat exchanger 17 is caused to function as a radiator, and when the outdoor air temperature Tam is lower than a predetermined temperature, the outdoor heat exchanger 17 is You may make it function as an evaporator.

  Further, the refrigeration cycle apparatus 10 of the present embodiment has a cooling + heating operation mode in which, in addition to the operation modes (a) to (g) described above, the vehicle interior is cooled and the secondary battery 55 is heated at the same time. realizable. In addition, since the cooling of the passenger compartment is performed at a time when the outside air temperature is relatively high in summer, there is little opportunity for the secondary battery 55 to be equal to or lower than the first reference temperature Tk1. Therefore, there are few opportunities to perform the operation in the cooling + heating operation mode.

  In the cooling + heating operation mode, the control device closes the first on-off valve 14a, closes the second on-off valve 14b, and connects the first branch portion 13a and the battery expansion valve 21 to connect the first three-way valve. 15a is controlled, the operation of the second three-way valve 15b is controlled so as to connect the auxiliary heat exchanger 22 and the first junction 13b, and the heating expansion valve 16 is fully opened, for cooling. The expansion valve 19 is in the throttle state, and the battery expansion valve 21 is fully opened.

  Further, the control device controls the operation of the compressor 11, the blower 32 of the indoor air conditioning unit 30 and the air mix door 34 as in the cooling operation mode, and the blower 52 of the battery pack 50 as in the heating operation mode. Control.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling + heating operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12, and the blown air for the room after passing through the indoor evaporator 20 as in the cooling operation mode. Heat exchange with heat. The refrigerant that has flowed out of the indoor condenser 12 flows into the auxiliary heat exchanger 22 via the battery expansion valve 21 and exchanges heat with the battery air for heat dissipation, as in the heating operation mode.

  Thereby, battery air is heated. The refrigerant that has flowed out of the auxiliary heat exchanger 22 flows into the outdoor heat exchanger 17 through the second three-way valve 15b, the first joining portion 13b, and the heating expansion valve 16. The refrigerant flowing into the outdoor heat exchanger 17 exchanges heat with the outside air blown from the blower fan 17a to further dissipate heat.

  The refrigerant that has flowed out of the outdoor heat exchanger 17 flows into the cooling expansion valve 19 from the second branch portion 13c through the check valve 18 and the third branch portion 13d, and is decompressed, as in the cooling operation mode. The refrigerant decompressed by the cooling expansion valve 19 flows into the indoor evaporator 20, absorbs heat from the indoor air blown by the blower 32, and evaporates. Thereby, the indoor blowing air is cooled. The subsequent operation is the same as in the cooling operation mode.

  As described above, in the cooling and heating operation mode, the indoor blowing air is cooled by the indoor evaporator 20 to cool the vehicle interior, and the battery blowing air is heated by the auxiliary heat exchanger 22. Thus, the secondary battery 55 can be heated.

  Next, the excellent effect of the refrigeration cycle apparatus 10 of the present embodiment will be described. First, in the refrigeration cycle apparatus 10 according to the present embodiment, the refrigerant flow switching means 14a, 14b, 15a, 15b, 19, and 21 switch the refrigerant flow path, so that the indoor blown air (first temperature adjustment object) and Temperature adjustment of a plurality of types of temperature adjustment objects such as battery air (second temperature adjustment object) can be performed.

  Here, in the refrigeration cycle apparatus configured to be able to switch the refrigerant flow path like the refrigeration cycle apparatus 10 of the present embodiment, the internal volume of the cycle changes by switching the refrigerant flow path. Therefore, as shown in the white belt portion in FIG. 8, by switching to the refrigerant flow path of each operation mode, the necessary refrigerant that needs to be sealed in the cycle in order to exhibit the desired refrigeration capacity in the cycle. The amount also changes.

  Furthermore, in the refrigeration cycle apparatus 10 of the present embodiment, as is apparent from FIG. 8, the required refrigerant amount in the single operation mode (specifically, (a) cooling operation mode and (d) heating operation mode). The required amount of refrigerant in the combined operation mode (specifically, (b) cooling + cooling operation mode and (e) heating + heating operation mode), and cooling operation mode and heating operation mode increases.

  The reason for this is that in the refrigeration cycle apparatus 10 of the present embodiment, the cycle constituent devices such as the compressor 11 are arranged in the hood in front of the vehicle, the indoor air conditioning unit 30 is arranged in the vehicle interior front side, and the battery pack 50 is installed in the vehicle This is because it is arranged on the rear side.

  That is, in the refrigeration cycle apparatus 10 of the present embodiment, the amount of change in the internal volume of the cycle when the refrigerant flow path is switched is arranged on the rear side of the vehicle and the components of the refrigeration cycle apparatus 10 arranged in the hood. A large volume fluctuation corresponding to the internal volume of the refrigerant pipe for connecting to the auxiliary heat exchanger 22 in the battery pack 50 may occur.

  For this reason, the amount of change in the required refrigerant amount tends to increase when the refrigerant channel in the combined operation mode and the refrigerant channel in the single operation mode are switched. In particular, as shown in FIG. 8, the required refrigerant amount is maximized in the cooling / cooling operation mode in the combined operation mode, and the required refrigerant amount is minimized in the heating operation mode in the single operation mode. When switching from the flow path to the refrigerant flow path in the single operation mode, the amount of surplus refrigerant surplus with respect to the required amount of refrigerant is the largest.

  In contrast, in the refrigeration cycle apparatus 10 of the present embodiment, in the cooling operation mode of the single operation mode, the high-pressure liquid-phase refrigerant that has been pressurized by the compressor 11 and cooled by the outdoor heat exchanger 17 is supplied to the inflow side. The piping 23 can be stored in a range (a portion indicated by a thick broken line in FIG. 1) from the third branch portion 13d constituting the downstream branch portion to the battery expansion valve 21 constituting the opening / closing means.

  On the other hand, in the heating operation mode of the single operation mode, the high-pressure liquid-phase refrigerant that has been pressurized by the compressor 11 and cooled by the indoor condenser 12 is converted into the first branch that constitutes the upstream branch portion of the inflow side pipe 23. It can be stored in a range (part indicated by a thick broken line in FIG. 4) from the portion 13a to the battery expansion valve 21 constituting the opening / closing means.

  Furthermore, since the battery expansion valve 21 is disposed closer to the inlet side of the auxiliary heat exchanger 22 than the first branch portion 13a and the third branch portion 13d in the inflow side pipe 23, the first branch portion. The volume in the inflow side piping 23 from the 13a and the third branch portion 13d to the battery expansion valve 21 can be sufficiently increased to store the high-pressure liquid refrigerant. Thereby, the enlargement of the accumulator 24 can be suppressed.

  More specifically, as indicated by hatched hatching in FIG. 9, the battery expansion valve 21 from the branch portion (the first branch portion 13 a or the third branch portion 13 d) in the single operation mode (cooling operation mode or heating operation mode). The high-pressure liquid phase refrigerant can be stored in the inflow side piping 23 leading to. Therefore, when the refrigerant flow path is switched, the fluctuation amount of the necessary refrigerant amount that must be absorbed by the accumulator 24 can be reduced, and the increase in the size of the accumulator 24 can be suppressed. As a result, the enlargement of the entire refrigeration cycle apparatus 10 can be suppressed.

  Further, in the refrigeration cycle apparatus 10 of the present embodiment, the maximum value of the necessary refrigerant amount that needs to be enclosed in the cycle during the combined operation mode (that is, the necessary refrigerant amount in the cooling + cooling operation mode) and the single operation mode. The volume in the accumulator 24 and the first branching portion when the difference from the minimum value of the required refrigerant amount that needs to be sealed in the cycle (that is, the required refrigerant amount in the heating operation mode) is the fluctuation amount. The total value of the volume in the pipe extending from 13a or the third branch portion 13d to the battery expansion valve 21 is larger than the volume when the amount of fluctuation of the refrigerant is in the liquid phase.

  Therefore, the surplus refrigerant generated when switching from the combined operation mode to the single operation mode is reliably stored in the accumulator 24 and in the piping from the first branch portion 13a or the third branch portion 13d to the battery expansion valve 21. Can do.

  Further, according to the refrigeration cycle apparatus 10 of the present embodiment, a refrigerant flow path is configured in which the indoor evaporator 20 and the auxiliary heat exchanger 22 are connected in parallel during the cooling + cooling operation mode. Therefore, for example, even when the operation mode is switched from the cooling + cooling operation mode to the cooling operation mode, it is possible to suppress a sudden change in the degree of dryness of the refrigerant on the inlet side of the indoor evaporator 20, so that the air conditioning feeling is deteriorated. Can be suppressed.

  Further, according to the refrigeration cycle apparatus 10 of the present embodiment, the indoor condenser 12 and the auxiliary heat exchanger 22 are connected in series in the heating + heating operation mode, and the refrigerant flows from the indoor condenser 12 to the auxiliary heat exchanger 22. A refrigerant flow path that flows in this order is configured.

  Therefore, the indoor blowing air can be heated by using the high-temperature refrigerant immediately after being discharged from the compressor 11 as a heat source, and the indoor blowing air by the high-pressure refrigerant having a temperature lower than that of the high-temperature refrigerant immediately after being discharged from the compressor 11. Can be heated. As a result, it is possible to suppress the temperature of the secondary battery 55 from excessively rising. This is effective when the secondary battery 55 that is easily damaged when the temperature exceeds a predetermined temperature is employed.

  Moreover, according to the refrigeration cycle apparatus 10 of the present embodiment, when any temperature adjustment target is heated, it is heated by a heat pump cycle (vapor compression refrigeration cycle), so that the temperature adjustment target is an electric heater or the like. Thus, energy efficiency can be improved as compared with the case of heating.

  Further, according to the refrigeration cycle apparatus 10 of the present embodiment, the battery blowing air can be cooled or heated by the single auxiliary heat exchanger 22 in common, so the battery blowing using a plurality of heat exchangers. The mounting space of the auxiliary heat exchanger 22 can be reduced with respect to the configuration in which the air is cooled or heated. As a result, the refrigeration cycle apparatus 10 as a whole can be reduced in size and cost.

(Second Embodiment)
In the first embodiment, the refrigeration cycle apparatus 10 configured to be able to realize cooling and heating of a plurality of temperature adjustment objects has been described. However, in the present embodiment, as illustrated in FIGS. The refrigeration cycle apparatus 10 that cools the object to be adjusted will be described. 10 to 12, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  Specifically, in the refrigeration cycle apparatus 10 of the present embodiment, the indoor condenser 12, the first and second branch parts 13a and 13c, the first and second open / close operations are compared with the refrigeration cycle apparatus 10 of the first embodiment. The valves 14a, 14b, the first and second junctions 13b, 13e, the heating expansion valve 16, and the check valve 18 are eliminated.

  Therefore, the refrigerant inlet side of the outdoor heat exchanger 17 is connected to the discharge port side of the compressor 11 of the present embodiment. Furthermore, the refrigerant | coolant inflow port of the 3rd branch part 13d which comprises a downstream branch part is connected to the refrigerant | coolant exit side of the outdoor heat exchanger 17. FIG.

  The refrigerant inlet of the indoor evaporator 20 constituting the cooling heat exchanger is connected to one refrigerant outlet of the third branch part 13d via the cooling expansion valve 19 with a fully-closed function constituting the downstream decompression means. The side is connected. The refrigerant outlet side of the indoor evaporator 20 is connected to the suction side of the compressor 11 via the third junction 13f and the accumulator 24.

  The refrigerant inlet side of the auxiliary heat exchanger 22 is connected to the other refrigerant outlet of the third branch portion 13d via an inflow side pipe 23. A battery expansion valve 21 having a function as an opening / closing means is disposed in the inflow side pipe 23, and the battery expansion valve 21 is more auxiliary than the third branch portion 13 d of the inflow side pipe 23. It is arranged at a position close to the entrance side.

  The refrigerant outlet side of the auxiliary heat exchanger 22 is connected to the third junction 13f. Therefore, in the present embodiment, the refrigerant flow switching means is constituted by the cooling expansion valve 19 and the battery expansion valve 21.

  Moreover, in this embodiment, since the indoor condenser 12 is abolished, the heater core 121 is disposed in the indoor air conditioning unit 30. The heater core 121 heats the indoor blown air using the cooling water of an in-vehicle device (for example, an electric motor for traveling) that generates heat during operation as a heat source. Other configurations are the same as those of the first embodiment.

  Next, the operation of the refrigeration cycle apparatus 10 of the present embodiment having the above configuration will be described. In the refrigeration cycle apparatus 10 according to the present embodiment, the refrigerant channel switching means can switch the refrigerant channel, whereby the indoor cooling and the secondary battery 55 can be cooled.

(A) Cooling operation mode The cooling operation mode is a single operation mode in which the vehicle interior is cooled without cooling the secondary battery 55, and the indoor evaporator 20 (cooling heat exchanger) This is a single cooling mode for cooling the blast air (first temperature adjustment object). In this cooling operation mode, the control device places the cooling expansion valve 19 in the throttle state and fully closes the battery expansion valve 21.

  As a result, in the cooling operation mode, the refrigeration cycle apparatus 10 has the compressor 11 → the outdoor heat exchanger 17 → the third branch portion 13d → the cooling expansion valve 19 → the indoor evaporator 20 as shown by the thick arrows in FIG. It is switched to the refrigerant flow path in which the refrigerant circulates in the order of the accumulator 24 → the compressor 11. The operation of other various devices to be controlled is the same as in the cooling operation mode of the first embodiment.

  Accordingly, in the refrigeration cycle apparatus 10 in the cooling operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 17 and radiates heat by exchanging heat with the outside air blown from the blower fan 17a. The refrigerant that has flowed out of the outdoor heat exchanger 17 flows into the third branch portion 13d. Since the battery expansion valve 21 is fully closed, the refrigerant flowing into the third branch portion 13d flows out from one refrigerant outlet to the cooling expansion valve 19 side and is depressurized by the cooling expansion valve 19. The

  The refrigerant decompressed by the cooling expansion valve 19 flows into the indoor evaporator 20, absorbs heat from the indoor air blown by the blower 32, and evaporates. Thereby, the indoor blowing air is cooled. The refrigerant that has flowed out of the indoor evaporator 20 flows into the accumulator 24 through the third junction 13f.

  The refrigerant flowing into the accumulator 24 is separated into gas and liquid, the separated liquid phase refrigerant is stored in the accumulator 24 as surplus refrigerant, and the gas-phase refrigerant flowing out of the accumulator 24 is sucked into the compressor 11 and compressed again. .

  As described above, in the cooling operation mode, the indoor blowing air is cooled by the indoor evaporator 20 so that the vehicle interior can be cooled.

(B) Cooling + cooling operation mode The cooling + cooling operation mode is a combined operation mode in which the vehicle interior is cooled and the secondary battery 55 is cooled at the same time, and the indoor evaporator 20 (cooling heat exchanger) is used. This is a combined cooling mode in which the indoor air (first temperature adjustment object) is cooled and the battery air (second temperature adjustment object) is cooled by the auxiliary heat exchanger 22. In this cooling operation mode, the control device places the cooling expansion valve 19 and the battery expansion valve 21 in the throttle state.

  As a result, in the cooling + cooling operation mode, the refrigeration cycle apparatus 10, as shown by the thick arrow in FIG. 11, the compressor 11 → the outdoor heat exchanger 17 → the third branch portion 13 d → the cooling expansion valve 19 → the indoor evaporation. The refrigerant circulates in the order of the vessel 20 → the third junction 13f → the accumulator 24 → the compressor 11, and the third branch portion 13d → the battery expansion valve 21 → the auxiliary heat exchanger 22 → the third junction 13f → the accumulator 24. The refrigerant flow path is switched to the order.

  That is, in the cooling + cooling operation mode, a refrigerant flow path in which the indoor evaporator 20 and the auxiliary heat exchanger 22 are connected in parallel is configured. The operation of other various devices to be controlled is the same as in the cooling + cooling operation mode of the first embodiment.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling + cooling operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the third branch portion 13d through the outdoor heat exchanger 17 as in the cooling operation mode.

  The refrigerant flowing out from one refrigerant outlet of the third branch portion 13d is decompressed by the cooling expansion valve 19 and flows into the indoor evaporator 20. The refrigerant flowing into the indoor evaporator 20 absorbs heat from the indoor air blown by the blower 32 and evaporates. Thereby, the indoor blowing air is cooled. The refrigerant flowing out from the indoor evaporator 20 flows into the accumulator 24 as in the cooling operation mode.

  In addition, the refrigerant flowing out from the other refrigerant outlet of the third branch portion 13d is depressurized until it becomes a low-pressure refrigerant at the battery expansion valve 21 arranged in the inflow side pipe 23 and flows into the auxiliary heat exchanger 22. . The refrigerant flowing into the auxiliary heat exchanger 22 absorbs heat from the battery air blown by the blower 52 and evaporates. Thereby, battery air is cooled.

  The refrigerant that has flowed out of the auxiliary heat exchanger 22 flows into the accumulator 24 through the third merge portion 13f and the second merge portion 13e. The gas-phase refrigerant separated by the accumulator 24 is sucked into the compressor 11 and compressed again.

  As described above, in the cooling + cooling operation mode, the indoor blowing air is cooled by the indoor evaporator 20 to cool the vehicle interior, and the battery blowing air is cooled by the auxiliary heat exchanger 22. Thus, the secondary battery 55 can be cooled.

(C) Cooling operation mode The cooling operation mode is an operation mode in which the secondary battery 55 is cooled without air conditioning of the passenger compartment. In this operation mode, the control device fully closes the cooling expansion valve 19 and places the battery expansion valve 21 in the throttle state.

  As a result, in the cooling operation mode, the refrigeration cycle apparatus 10 has the compressor 11 → the outdoor heat exchanger 17 → the third branch portion 13d → the battery expansion valve 21 → the auxiliary heat exchanger, as shown by the thick arrows in FIG. The refrigerant flow path is changed to 22 → accumulator 24 in this order. The operation of other various devices to be controlled is the same as in the cooling operation mode of the first embodiment.

  Therefore, in the refrigeration cycle apparatus 10 in the cooling operation mode, the high-pressure refrigerant discharged from the compressor 11 flows into the third branch portion 13d through the outdoor heat exchanger 17 as in the cooling operation mode. Since the cooling expansion valve 19 is fully closed, the refrigerant flowing into the third branch portion 13d flows out from the other refrigerant outlet to the battery expansion valve 21 and is decompressed by the battery expansion valve 21. The

  The refrigerant decompressed by the battery expansion valve 21 flows into the auxiliary heat exchanger 22, absorbs heat from the battery air blown by the blower 52, and evaporates. Thereby, battery air is cooled. The refrigerant that has flowed out of the auxiliary heat exchanger 22 flows into the accumulator 24 through the third junction 13f.

  The refrigerant flowing into the accumulator 24 is separated into gas and liquid, the separated liquid phase refrigerant is stored in the accumulator 24 as surplus refrigerant, and the gas-phase refrigerant flowing out of the accumulator 24 is sucked into the compressor 11 and compressed again. .

  As described above, in the cooling operation mode, the battery air is cooled by the auxiliary heat exchanger 22 and the secondary battery 55 can be cooled.

  As described above, in the refrigeration cycle apparatus 10 according to the present embodiment, the cooling air flow is switched by the cooling expansion valve 19 and the battery expansion valve 21 serving as the refrigerant flow switching means, whereby the indoor blown air (first temperature) is switched. Temperature adjustment of a plurality of types of temperature adjustment objects such as an adjustment object) and battery air (second temperature adjustment object) can be performed.

  Furthermore, also in the refrigeration cycle apparatus 10 of the present embodiment, for the same reason as in the first embodiment, as shown in FIG. 13, when the refrigerant flow path in the combined operation mode is switched to the refrigerant flow path in the single operation mode. The amount of surplus refrigerant increases.

  On the other hand, in the refrigeration cycle apparatus 10 of the present embodiment, in the single operation mode, as shown by hatched hatching in FIG. 14, the surplus refrigerant reaches the battery expansion valve 21 from the third branch portion 13 d (FIG. 10). (Parts indicated by thick broken lines) in FIG. Therefore, the same effect as the first embodiment can be obtained. 13 and 14 are drawings corresponding to FIGS. 8 and 9 of the first embodiment, respectively.

(Third embodiment)
Although 1st Embodiment demonstrated the example which heats or cools the battery blowing air (gas) which flows through the inside of the air path of the battery pack 50 as a 2nd temperature adjustment target object, in this embodiment, the whole of FIG. As shown in the configuration diagram, an example in which a heat medium (liquid) flowing through the heat medium circuit 50a is heated or cooled as the second temperature adjustment object will be described.

  The heat medium circuit 50 a is a circuit that circulates a heat medium (specifically, an ethylene glycol aqueous solution) that adjusts the temperature of the secondary battery 55. More specifically, the heat medium circuit 50a includes a water pump 52a for heat medium pumping, a water-refrigerant heat exchanger 22a for heat exchange between the heat medium and the refrigerant, and heat formed inside or outside the secondary battery 55. It is configured by sequentially connecting the medium passages in a ring shape by piping.

  The water pump 52a is an electric water pump whose operation (heat medium pumping ability) is controlled by a control signal output from the control device. More specifically, the operation of the water pump 52a is controlled in the same manner as the blower 52 in each operation mode described in the first embodiment.

  The water-refrigerant heat exchanger 22a is an auxiliary heat exchanger that exchanges heat between the refrigerant flowing through the refrigerant passage 22b and the heat medium flowing through the water passage 22c. As a specific configuration of such a water-refrigerant heat exchanger 22a, a configuration in which a pipe that forms a water passage 22c is wound around an outer periphery of a refrigerant pipe that forms the refrigerant passage 22b to exchange heat between the heat medium and the refrigerant. May be.

  Further, a meandering tube or a plurality of tubes for circulating the refrigerant is adopted as the refrigerant passage 22b, the water passage 22c is formed between the adjacent tubes, and further heat exchange between the refrigerant and the cooling water is promoted. You may employ | adopt the heat exchanger structure etc. which provide a corrugated fin and a plate fin.

  Furthermore, on the input side of the control device of the present embodiment, a heat medium inlet side temperature sensor for detecting the inlet temperature Tin of the heat medium flowing into the heat medium passage of the secondary battery 55, and the heat medium passage of the secondary battery 55 A heat medium outlet side temperature sensor for detecting a heat medium outlet side temperature Tout of the heat medium flowing out of the heat medium is connected.

  The water pumping capacity of the water pump 52a when cooling or heating the secondary battery is such that the temperature difference between the inlet side temperature Tin and the outlet side temperature Tout is about a predetermined temperature difference (for example, 5 ° C.). It is controlled to become. Other configurations and operations are the same as those in the first embodiment.

  Therefore, when the refrigeration cycle apparatus 10 of the present embodiment is operated, the refrigerant discharged from the compressor 11 is caused to flow into the refrigerant passage 22b of the water-refrigerant heat exchanger 22a in the heating + heating operation mode and the heating operation mode. The heat medium flowing through the water passage 22c can be heated. Thereby, the secondary battery 55 can be heated.

  In the cooling + cooling operation mode, the cooling operation mode, and the heating + cooling operation mode, the refrigerant depressurized by the battery expansion valve 21 is caused to flow into the refrigerant passage 22b of the water-refrigerant heat exchanger 22a, and the water passage 22c. The heat medium that circulates can be cooled. Thereby, the secondary battery 55 can be cooled.

  Furthermore, even in the configuration employing the heat medium circuit 50a as in the present embodiment, the same effects as in the first embodiment can be obtained. In the present embodiment, the example in which the heat medium circuit 50a is employed in the refrigeration cycle apparatus 10 of the first embodiment has been described. Of course, in the refrigeration cycle apparatus 10 of the second embodiment, heat is applied similarly to the present embodiment. The media circuit 50a may be employed.

(Fourth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 16, the secondary battery 55 is directly cooled or heated by the refrigerant flowing out from the first three-way valve 15a as compared to the first embodiment. More specifically, the refrigerant that has flowed out of the first three-way valve 15a passes through the refrigerant passage formed in the outer periphery of the secondary battery 55 and flows out to the second three-way valve 15b side. Therefore, the second temperature adjustment object of this embodiment is the secondary battery 55.

  Other configurations and operations are the same as those in the first embodiment. Therefore, when the refrigeration cycle apparatus 10 of this embodiment is operated, the secondary battery 55 can be directly heated by the refrigerant discharged from the compressor 11 in the heating + heating operation mode and the heating operation mode. In the cooling + cooling operation mode, the cooling operation mode, and the heating + cooling operation mode, the secondary battery 55 can be directly cooled with the refrigerant decompressed by the battery expansion valve 21. As a result, even with the configuration of the present embodiment, the same effects as those of the first embodiment can be obtained.

  In the present embodiment, the example in which the secondary battery 55 is directly cooled or heated by the refrigerant flowing out of the first three-way valve 15a in the refrigeration cycle apparatus 10 of the first embodiment has been described, but of course the second embodiment. In the refrigeration cycle apparatus 10, the secondary battery 55 may be directly cooled or heated by the refrigerant flowing out from the third branch portion 13 d as in the present embodiment.

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

  (1) In the above-described embodiment, an example in which the refrigeration cycle apparatus 10 is applied to an electric vehicle has been described. Of course, a normal vehicle that obtains driving force for vehicle travel from an internal combustion engine, or an internal combustion engine and a travel electric motor You may apply to the hybrid vehicle which obtains the driving force for vehicle travel from both sides. When applied to a vehicle having an internal combustion engine, the heater core 121 described in the second embodiment may be one that heats indoor air using the cooling water of the internal combustion engine as a heat source.

  Furthermore, you may apply the refrigerating-cycle apparatus 10 other than a vehicle. For example, the first temperature adjustment object may be blown air that blows air into the room, and the second temperature adjustment object may be a heat medium for adjusting the temperature of the power generation device.

  (2) In the above-described embodiment, the indoor blowing air is heated or cooled as the first temperature adjustment object, and the battery blowing air (gas), the heat medium (liquid), or the battery 55 itself is used as the second temperature adjustment object. Although the example which heated or cooled (solid) was demonstrated, a 1st, 2nd temperature target object is not limited to these. Of course, the first temperature adjustment object may be liquid or solid.

  For example, the temperature adjustment of an in-vehicle device different from the battery 55 may be performed as the first and second temperature adjustment objects. For example, the internal combustion engine (engine cooling water, engine intake), electric motor, inverter, transmission, engine catalyst, or the like may be cooled or heated.

  Furthermore, you may employ | adopt indoor blowing air ventilated to the same or different air-conditioning object space as a 1st, 2nd temperature adjustment object.

  For example, in a one-box car or the like, a front-seat indoor air-conditioning unit that adjusts the temperature of indoor blown air that is arranged on the front side of the vehicle interior and blows to the front seat side, and the rear side or upper side of the vehicle interior ( Some have a so-called dual air conditioner system that includes a rear seat indoor air conditioning unit that is arranged at a position other than the front side (such as the ceiling side) and adjusts the temperature of the indoor blown air that is blown to the rear seat side. .

  In such a dual air conditioning system, a cooling heat exchanger (and a heating heat exchanger) is arranged in the front seat air conditioning unit, and an auxiliary heat exchanger is arranged in the rear seat air conditioning unit. Similarly to the above-described embodiment, the effect of suppressing the increase in the size of the accumulator 24 can be obtained.

  (3) In the above-described embodiment, the example in which the battery expansion valve 21 with a fully-closed function is employed as the opening / closing means for opening / closing the inflow side pipe 23 has been described, but the opening / closing means is not limited thereto. For example, a battery on / off valve having the same configuration as that of the first and second on / off valves 14a and 14b may be employed as the on / off means. In this case, a battery throttle mechanism (including a fixed throttle) connected in series with the battery open / close valve may be arranged in the inflow side pipe 23.

  Furthermore, in the above-described embodiment, the opening / closing means for opening and closing the inflow side pipe 23 is located closer to the inlet side of the auxiliary heat exchanger 22 than the first branch part 13a and the third branch part 13d in the inflow side pipe 23. Although described above, the opening / closing means may be integrated with the refrigerant inlet of the auxiliary heat exchanger 22.

  In the above-described embodiment, the example in which the cooling expansion valve 19 with a fully-closed function is used as the downstream pressure reducing unit has been described. However, the cooling throttle mechanism (not having the fully-closed function as the downstream pressure reducing unit) ( (Including a fixed aperture). In this case, a cooling on / off valve having the same configuration as the first and second on / off valves 14a and 14b may be arranged in series with respect to the cooling throttling mechanism so as to function as the refrigerant flow switching means. .

  In the above-described embodiment, the heating expansion valve 16 with the fully open function is used as the upstream pressure reducing means. However, the heating throttle mechanism (fixed throttle) that does not have the fully open function as the upstream pressure reducing means has been described. May be adopted. In this case, a bypass passage that bypasses the heating throttle mechanism is provided, and a heating on / off valve having the same configuration as the first and second on / off valves 14a and 14b is arranged in the bypass passage, so that the refrigerant flow path switching means is provided. Just make it work.

  In the above-described embodiment, the first and second on-off valves 14a and 14b, the first and second three-way valves 15a and 15b, the cooling expansion valve 19 and the battery expansion valve 21 constitute the refrigerant circuit switching means. Although an example has been described, the refrigerant circuit switching means is not limited to this. You may comprise by combining an electric three-way valve and a some on-off valve.

  (4) In the above-described first embodiment, the example in which the indoor evaporator 20 and the auxiliary heat exchanger 22 are switched to the refrigerant flow path connected in parallel in the cooling + cooling operation mode has been described. The configuration of the refrigerant flow path in the mode is not limited to this.

  For example, the refrigerant flow path in which the refrigerant circulates in the order of the compressor 11 → the outdoor heat exchanger 17 → the cooling expansion valve 19 → the indoor evaporator 20 → the battery expansion valve 21 → the auxiliary heat exchanger 22 → the accumulator 24 → the compressor 11. You may make it switch to. Further, the refrigerant flow path in which the refrigerant circulates in the order of the compressor 11 → the outdoor heat exchanger 17 → the battery expansion valve 21 → the auxiliary heat exchanger 22 → the cooling expansion valve 19 → the indoor evaporator 20 → the accumulator 24 → the compressor 11. You may make it switch to. That is, a refrigerant flow path in which the indoor evaporator 20 and the auxiliary heat exchanger 22 are connected in series may be configured in the cooling + cooling operation mode.

  Moreover, although the example which switched to the refrigerant | coolant flow path in which the indoor condenser 12 and the auxiliary heat exchanger 22 are connected in series at the time of heating + heating operation mode was demonstrated, the structure of the refrigerant | coolant flow path in heating + heating operation mode is this. It is not limited to.

  For example, the refrigerant circulates in the order of the compressor 11 → the first branch part 13a → the indoor condenser 12 → the first junction part 13b → the heating expansion valve 16 → the outdoor heat exchanger 17 → the accumulator 24 → the compressor 11 and You may make it switch to the refrigerant | coolant flow path through which a refrigerant | coolant flows in order of 1 branch part 13a-> auxiliary heat exchanger 22-> 1st junction part 13b. That is, you may comprise the refrigerant | coolant flow path in which the indoor condenser 12 and the auxiliary heat exchanger 22 are connected in parallel at the time of heating + heating operation mode.

  In the heating + heating operation mode, the indoor condenser 12 and the auxiliary heat exchanger 22 are connected in series so that the refrigerant discharged from the compressor 11 flows in the order of the auxiliary heat exchanger 22 → the indoor condenser 12. May be.

  Moreover, although the example which switched to the refrigerant flow path in which the outdoor heat exchanger 17 and the auxiliary heat exchanger 22 were connected in series at the time of heating + cooling operation mode was demonstrated, the structure of the refrigerant flow path in heating + cooling operation mode is shown. It is not limited to this.

  For example, the refrigerant in the order of the compressor 11 → the indoor condenser 12 → the first branch part 13 a → the heating expansion valve 16 → the outdoor heat exchanger 17 → the second branch part 13 c → the second junction part 13 e → the accumulator 24 → the compressor 11. May be switched to the refrigerant flow path through which the refrigerant flows in the order of the first branch portion 13a → the battery expansion valve 21 → the auxiliary heat exchanger 22 → the third merge portion 13f → the second merge portion 13e. That is, in the heating + cooling operation mode, a refrigerant flow path in which the outdoor heat exchanger 17 and the auxiliary heat exchanger 22 are connected in parallel may be configured.

  (5) As described in the above embodiment, since the secondary battery 55 is likely to have a temperature distribution, the secondary battery 55 is not cooled or heated even in the single operation mode (cooling operation mode and heating operation mode). The blower 52 of the battery pack 50 may be operated. Thereby, the battery air in the battery pack 50 is circulated, and the temperature distribution of the secondary battery 55 can be suppressed.

  (6) In the above-described embodiment, the temperature sensor that detects the temperature of the main body of the secondary battery 55 has been described as the temperature detector that detects the battery temperature Tb. However, the temperature detector is not limited to this. For example, in the first embodiment, a temperature detection unit that detects the temperature of the blown air for the battery immediately after passing through the secondary battery 55 may be employed, and in the second embodiment, the temperature passes through the secondary battery 55. You may employ | adopt the temperature detection means to detect the temperature of the heat medium immediately after.

  (7) In the refrigeration cycle apparatus 10 of the first embodiment described above, the example in which the blown air is heated by exchanging heat between the high-pressure refrigerant and the blown air in the indoor condenser 12 has been described, but the blown air is heated. The configuration is not limited to this.

  For example, a heat medium circuit having the same configuration as that of the heat medium circuit 50a described in the third embodiment is provided, and the heat medium circulating circuit heat-exchanges the high-pressure refrigerant discharged from the compressor 11 and the heat medium. The heat exchanger which heat-exchanges a refrigerant | coolant heat exchanger and the heat medium heated with the water-refrigerant heat exchanger, and blowing air is arrange | positioned, and this heat exchanger is set to the indoor condenser 12. Instead, it may be used to heat indoor air.

  In other words, the indoor blown air may be indirectly heated through the heat medium using the high-pressure refrigerant discharged from the compressor 11 as a heat source. Furthermore, when applied to a vehicle having an internal combustion engine, the heat medium circulation circuit may be circulated using cooling water of the internal combustion engine as a heat medium. Moreover, in an electric vehicle, you may make it distribute | circulate a heat-medium circulation circuit by using the cooling water which cools a battery and an electric equipment as a heat medium.

DESCRIPTION OF SYMBOLS 10 Refrigeration cycle apparatus 11 Compressor 13a, 13d Upstream branch part, downstream branch part 14a, 14b 1st, 2nd on-off valve 15a, 15b 1st, 2nd three-way valve 17 Outdoor heat exchanger 19 Expansion valve for cooling ( Downstream pressure reducing means)
20 Cooling heat exchanger 21 Battery expansion valve (opening / closing means)
22 Auxiliary heat exchanger 23 Inflow side piping

Claims (10)

A compressor (11) for compressing and discharging the refrigerant;
An outdoor heat exchanger (17) for exchanging heat between the refrigerant and the outside air;
Downstream pressure reducing means (19) for reducing the pressure of the refrigerant flowing out of the outdoor heat exchanger (17);
A cooling heat exchanger (20) for exchanging heat between the refrigerant depressurized by the downstream pressure reducing means (19) and the first temperature adjustment object;
An accumulator (24) for separating the gas-liquid refrigerant, causing the separated gas-phase refrigerant to flow out to the suction side of the compressor (11), and storing the separated liquid-phase refrigerant;
Branch portions (13a, 13d) for branching the flow of the high-pressure refrigerant pressurized by the compressor (11);
An auxiliary heat exchanger (22) for exchanging heat between the refrigerant branched at the branch portions (13a, 13d) and the second temperature adjustment object;
An inflow side pipe (23) for guiding the refrigerant branched at the branch parts (13a, 13d) to the inlet side of the auxiliary heat exchanger (22);
Refrigerant channel switching means (14a, 14b, 15a, 15b, 19, 21) for switching the refrigerant channel of the refrigerant circulating in the cycle,
The refrigerant flow switching means (14a ... 21) includes an opening / closing means (21) for opening and closing the inflow side pipe, and the opening / closing means (21) closes the inflow side pipe (23). The refrigerant flow path in the single operation mode for adjusting the temperature of the first temperature adjustment object by prohibiting the inflow of the refrigerant to the auxiliary heat exchanger (22) and the opening / closing means (21) are connected to the inflow side pipe ( 23) is configured to allow switching of the refrigerant flow path in the combined operation mode in which the refrigerant flows into the auxiliary heat exchanger (22) to adjust the temperature of both the first and second temperature adjustment objects. And
As the single operation mode, a single cooling mode for cooling the first temperature adjustment object in the cooling heat exchanger (20) is provided,
Further, the refrigerant flow switching means (14a... 21) is, in the single cooling mode, the compressor (11) → the outdoor heat exchanger (17) → the branch portion (13d) → the downstream pressure reducing means ( 19) → switching to the refrigerant flow path for circulating the refrigerant in the order of the cooling heat exchanger (20) → the accumulator (24),
The opening / closing means (21) is disposed closer to the inlet side of the auxiliary heat exchanger (22) than the branching portions (13a, 13d) of the inflow side pipe (23) ,
In the single operation mode, a surplus refrigerant is stored in a range from the branch portion (13a, 13d) to the opening / closing means (21) in the inflow side pipe (23) . A compressor (11) for compressing and discharging the refrigerant;
An outdoor heat exchanger (17) for exchanging heat between the refrigerant and the outside air;
Downstream pressure reducing means (19) for reducing the pressure of the refrigerant flowing out of the outdoor heat exchanger (17);
A cooling heat exchanger (20) for exchanging heat between the refrigerant depressurized by the downstream pressure reducing means (19) and the first temperature adjustment object;
An accumulator (24) for separating the gas-liquid refrigerant, causing the separated gas-phase refrigerant to flow out to the suction side of the compressor (11), and storing the separated liquid-phase refrigerant;
Branch portions (13a, 13d) for branching the flow of the high-pressure refrigerant pressurized by the compressor (11);
An auxiliary heat exchanger (22) for exchanging heat between the refrigerant branched at the branch portions (13a, 13d) and the second temperature adjustment object;
An inflow side pipe (23) for guiding the refrigerant branched at the branch parts (13a, 13d) to the inlet side of the auxiliary heat exchanger (22);
Refrigerant channel switching means (14a, 14b, 15a, 15b, 19, 21) for switching the refrigerant channel of the refrigerant circulating in the cycle,
The refrigerant flow switching means (14a ... 21) includes an opening / closing means (21) for opening and closing the inflow side pipe, and the opening / closing means (21) closes the inflow side pipe (23). The refrigerant flow path in the single operation mode for adjusting the temperature of the first temperature adjustment object by prohibiting the inflow of the refrigerant to the auxiliary heat exchanger (22) and the opening / closing means (21) are connected to the inflow side pipe ( 23) is configured to allow switching of the refrigerant flow path in the combined operation mode in which the refrigerant flows into the auxiliary heat exchanger (22) to adjust the temperature of both the first and second temperature adjustment objects. And
As the single operation mode, a single cooling mode for cooling the first temperature adjustment object in the cooling heat exchanger (20) is provided,
Further, the refrigerant flow switching means (14a... 21) is, in the single cooling mode, the compressor (11) → the outdoor heat exchanger (17) → the branch portion (13d) → the downstream pressure reducing means ( 19) → switching to the refrigerant flow path for circulating the refrigerant in the order of the cooling heat exchanger (20) → the accumulator (24),
The opening / closing means (21) is disposed closer to the inlet side of the auxiliary heat exchanger (22) than the branching portions (13a, 13d) of the inflow side pipe (23) ,
When the difference between the required refrigerant amount that needs to be enclosed in the cycle during the combined operation mode and the required refrigerant amount that needs to be enclosed in the cycle during the single operation mode is defined as a fluctuation amount,
The total value of the volume in the accumulator (24) and the volume in the pipe extending from the branch portion to the opening / closing means (21) is larger than the volume when the refrigerant corresponding to the fluctuation amount is in a liquid phase state. is it possible that the refrigeration cycle apparatus according to claim. As the branch portion, a downstream branch portion (13d) for branching the flow of the refrigerant flowing from the outdoor heat exchanger (17) to the downstream pressure reducing means (19) is provided,
As the combined operation mode, the first temperature adjustment object is cooled by the cooling heat exchanger (20), and the second temperature adjustment object is cooled by the auxiliary heat exchanger (22). Cooling mode is provided,
The refrigerant flow switching means (14a... 21) is, in the combined cooling mode, the compressor (11) → the outdoor heat exchanger (17) → the downstream branch portion (13d) → the downstream pressure reducing means ( 19) → the cooling heat exchanger (20) → the accumulator (24), and the refrigerant is circulated in the order, and the downstream branch (13d) → the auxiliary heat exchanger (22) → the accumulator (24). The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is switched to a refrigerant flow path for circulating the refrigerant in order. Furthermore, a heat exchanger for heating (12) for exchanging heat between the refrigerant discharged from the compressor (11) and the first temperature adjustment object,
An upstream pressure reducing means (16) for reducing the pressure of the refrigerant flowing out of the heating heat exchanger (12) and flowing it out to the inlet side of the outdoor heat exchanger (17);
As the single operation mode, a single heating mode for heating the first temperature adjustment object in the heat exchanger for heating (12) is provided,
In the single heating mode, the refrigerant flow switching means (14a... 21) is the compressor (11) → the heating heat exchanger (12) → the upstream pressure reducing means (16) → the outdoor heat exchanger. The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein the refrigerant cycle is switched to a refrigerant flow path for circulating the refrigerant in the order of (17) to the accumulator (24). As the branching portion, an upstream branching portion (13a) for branching the flow of the refrigerant flowing from the heating heat exchanger (12) to the upstream decompression means (16) is provided,
As the combined operation mode, the first temperature adjustment object is heated by the heating heat exchanger (12), and the second temperature adjustment object is heated by the auxiliary heat exchanger (22). A heating mode is provided,
The refrigerant flow switching means (14a... 21) is, in the combined heating mode, the compressor (11) → the heating heat exchanger (12) → the upstream branch (13a) → the auxiliary heat exchanger. 5. The refrigeration according to claim 4, wherein the refrigerant is switched to a refrigerant flow path for circulating the refrigerant in the order of (22) → the upstream pressure reducing means (16) → the outdoor heat exchanger (17) → the accumulator (24). Cycle equipment. As the combined operation mode, the first temperature adjustment object is heated by the heating heat exchanger (12) and the second temperature adjustment object is cooled by the auxiliary heat exchanger (22). Heating / cooling mode is provided,
The refrigerant flow switching means (14a... 21) is, in the combined heating / cooling mode, the compressor (11) → the heating heat exchanger (12) → the upstream pressure reducing means (16) → the outdoor heat exchange. The refrigerant flow path for circulating the refrigerant is switched in the order of the vessel (17) → the downstream branching portion (13d) → the auxiliary heat exchanger (22) → the accumulator (24). The refrigeration cycle apparatus described.   The refrigeration cycle apparatus according to any one of claims 1 to 6, wherein the opening / closing means includes a variable throttle mechanism (21) configured to be capable of changing a refrigerant passage area. A refrigeration cycle apparatus applied to a vehicle,
The first temperature adjustment object is blown air blown into the vehicle interior,
The refrigeration cycle according to any one of claims 1 to 7, wherein the auxiliary heat exchanger (22) is used to adjust a temperature of an in-vehicle device (55) mounted on the vehicle. apparatus.   The refrigeration cycle apparatus according to claim 8, wherein the in-vehicle device is a secondary battery (55) for storing electric power. A refrigeration cycle apparatus applied to a vehicle,
The refrigeration cycle apparatus according to any one of claims 1 to 7, wherein each of the first temperature adjustment object and the second temperature adjustment object is blown air blown into a vehicle interior. .

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