Temperature control system

Abstract

Provided is a temperature control system for a vehicle comprising: a heat medium cycle which has a first refrigeration cycle, a second refrigeration cycle, a pump that forcibly circulates a heat medium, and a heat medium heat exchanger that heats or cools a temperature control target by means of the heat medium, and which circulates the heat medium through a heat medium circuit; and an integrated heat exchanger (100) which has a first refrigerant flow path (101) through which a first refrigerant compressed by a first compressor flows, a second refrigerant flow path (102) through which a second refrigerant expanded by a second expansion valve flows, and a heat medium flow path (103) through which the heat medium that has passed through the heat medium heat exchanger flows, and which performs heat exchange between the first refrigerant and the second refrigerant, heat exchange between the first refrigerant and the heat medium, and heat exchange between the second refrigerant and the heat medium.

Description

Temperature Control System

[0001] The present disclosure relates to a temperature adjustment system.

[0002] Conventionally, a refrigeration cycle device that combines multiple refrigeration cycles to improve the efficiency of refrigeration cycles used for air conditioning in a vehicle cabin and temperature control of on-board devices such as a battery (see, for example, Patent Document 1). The refrigeration cycle device disclosed in Patent Document 1 transfers heat from a first refrigerant in a first refrigeration cycle to a heat medium circulating through a first circulation path in an operation mode that warms up a battery while heating a vehicle cabin space. Heat is transferred from the heat medium to a second refrigerant in a second refrigeration cycle, and heat is transferred from the second refrigerant to a heat medium circulating through a second circulation path. The battery is warmed up by the heat medium circulating through the first circulation path, and blown air is heated by the heat medium circulating through the second circulation path.

[0003] Japanese Patent Application Laid-Open No. 2023-135138

[0004] However, in the refrigeration cycle device disclosed in Patent Document 1, the heat exchanger that performs heat exchange between the first refrigerant in the first refrigeration cycle and the heat medium circulating through the first circulation path and the heat exchanger that performs heat exchange between the heat medium circulating through the first circulation path and the second refrigerant in the second refrigeration cycle are independent heat exchangers. Because heat is transferred indirectly from the first refrigerant in the first refrigeration cycle to the second refrigeration cycle in the second refrigeration cycle via the heat medium circulating through the first circulation path, the coefficient of performance (COP) of the refrigeration cycle device is lower than when heat is transferred directly from the first refrigerant to the second refrigerant.

[0005] The present disclosure has been made in consideration of the above circumstances, and aims to improve the COP in a temperature control system equipped with multiple refrigeration cycles.

[0006] In order to solve the above problems, a temperature adjustment system according to the present disclosure employs the following means. A temperature adjustment system according to one aspect of the present disclosure includes a first refrigeration cycle having a first compressor, a first expansion valve that expands a first refrigerant compressed by the first compressor, and a first low-pressure side heat exchanger that is supplied with the first refrigerant expanded by the first expansion valve and guides the first refrigerant to the first compressor, and circulates the first refrigerant in a first refrigerant circuit, a second compressor, a second high-pressure side heat exchanger that is supplied with a second refrigerant compressed by the second compressor, and a second expansion valve that expands the second refrigerant supplied from the second high-pressure side heat exchanger and guides the second refrigerant to the second compressor, and the integrated heat exchanger includes a second refrigeration cycle that circulates a heat medium, a pump that pressurizes the heat medium, and a heat medium heat exchanger that heats or cools a temperature-controlled object with the heat medium, the integrated heat exchanger having a first refrigerant flow path through which the first refrigerant compressed by the first compressor flows, a second refrigerant flow path through which the second refrigerant expanded by the second expansion valve flows, and a heat medium flow path through which the heat medium that has passed through the heat medium heat exchanger flows, and performing heat exchange between the first refrigerant and the second refrigerant, heat exchange between the first refrigerant and the heat medium, and heat exchange between the second refrigerant and the heat medium.

[0007] According to the present disclosure, it is possible to improve the COP in a temperature adjustment system equipped with multiple refrigeration cycles.

[0008] 1 is a schematic configuration diagram showing a vehicle temperature control system according to a first embodiment of the present disclosure, showing a state in which the vehicle temperature control system is operating in cooling mode. It is a perspective view showing the appearance of a plate heat exchanger, which is an example of the integrated heat exchanger shown in FIG. 1 . It is a schematic diagram showing the flows of a first refrigerant, a second refrigerant, and a heat medium in the integrated heat exchanger shown in FIG. 2 . It is a schematic diagram showing the flows of a first refrigerant, a second refrigerant, and a heat medium in a first modified example of the integrated heat exchanger shown in FIG. 2 . It is a schematic diagram showing the flows of a first refrigerant, a second refrigerant, and a heat medium in a second ... configuration diagram showing a vehicle temperature control system according to a second embodiment of the present disclosure, showing a state in which the vehicle temperature control system is operating in heating mode. It is a schematic diagram showing the flows of a first refrigerant, a second refrigerant, and a heat medium in the integrated heat exchanger shown in FIG. 6 . It is a schematic diagram showing the flows of a first refrigerant, a second refrigerant, and a heat medium in the modified example of the integrated heat exchanger shown in FIG. 6 . It is a schematic diagram showing the flows of a first refrigerant, a second refrigerant, and a heat medium in an integrated heat exchanger according to a third embodiment of the present disclosure. FIG. 10 is a schematic diagram showing the flows of a first refrigerant, a second refrigerant, and a heat medium in a modified example of the integrated heat exchanger shown in FIG. 9 .

[0009] First Embodiment A vehicle temperature control system 1 according to a first embodiment of the present disclosure will be described with reference to the drawings. The vehicle temperature control system 1 of this embodiment is installed in a vehicle (not shown), such as an electric vehicle that does not have an engine and obtains driving force for running the vehicle from an electric motor, or a so-called hybrid vehicle that obtains driving force for running the vehicle from an engine and an electric motor.

[0010] The vehicle temperature control system 1 is responsible for air conditioning such as heating and cooling, dehumidification, and ventilation of the passenger compartment, as well as thermal management and exhaust heat recovery of on-board devices such as the vehicle's battery 4, traction motor 5, and heat-generating electronic devices. Conditioning the air to an appropriate temperature and humidity and maintaining the on-board devices at an appropriate temperature are collectively referred to as "thermal management." Power stored in the on-board battery 4 is supplied to the vehicle temperature control system 1 and the electrically powered devices and electronic devices installed in the on-board devices.

[0011] 1 is a schematic diagram showing a vehicle temperature control system 1 according to a first embodiment of the present disclosure, illustrating a state in which the vehicle temperature control system 1 is operating in cooling mode. As shown in FIG. 1, the vehicle temperature control system 1 includes a first refrigeration cycle 10, a second refrigeration cycle 20, an HVAC unit 30, a battery heat exchange cycle (heat medium cycle) 40, a motor heat exchanger 50, an exterior heat exchange unit 60, pumps 71, 73, and 74, switching valves 81, 83, 84, and 85, a control unit 90, and an integrated heat exchanger 100.

[0012] The first refrigeration cycle 10 has a first compressor 11, a first expansion valve 13, a first low-pressure side heat exchanger 14, and a first refrigerant circuit 15. The first refrigeration cycle 10 is connected by the first refrigerant circuit 15, and circulates a first refrigerant R1 between the first compressor 11, the integrated heat exchanger 100, the first expansion valve 13, and the first low-pressure side heat exchanger 14.

[0013] The first compressor 11 compresses the first refrigerant R1 guided from the first low-pressure side heat exchanger 14 and discharges it to the integrated heat exchanger 100. The integrated heat exchanger 100 is supplied with the first refrigerant R1 compressed by the first compressor 11 and exchanges heat between the high-temperature, high-pressure first refrigerant R1 and the heat medium Mb and second refrigerant R2 circulating in the battery heat exchange cycle 40.

[0014] The first expansion valve 13 expands the first refrigerant R1 supplied from the integrated heat exchanger 100 and supplies the expanded refrigerant to the first low-pressure side heat exchanger 14. The first low-pressure side heat exchanger 14 is supplied with the first refrigerant R1 expanded by the first expansion valve 13, and exchanges heat between the decompressed first refrigerant R1 and air blown by the blower 34 to cool the air.

[0015] The second refrigeration cycle 20 has a second compressor 21, a second high-pressure side heat exchanger 22, a second expansion valve 23, and a second refrigerant circuit 25. The second refrigeration cycle 20 is connected by the second refrigerant circuit 25, and circulates a second refrigerant R2 between the second compressor 21, the second high-pressure side heat exchanger 22, the second expansion valve 23, and the integrated heat exchanger 100.

[0016] The second compressor 21 compresses the second refrigerant R2 guided from the integrated heat exchanger 100 and discharges it to the second high-pressure side heat exchanger 22. The second high-pressure side heat exchanger 22 is supplied with the second refrigerant R2 compressed by the second compressor 21 and exchanges heat between the high-temperature, high-pressure second refrigerant R2 and the heat medium Me circulating through the exterior heat exchange unit 60.

[0017] The second expansion valve 23 expands the second refrigerant R2 supplied from the second high-pressure side heat exchanger 22 and supplies the expanded refrigerant to the integrated heat exchanger 100. The integrated heat exchanger 100 is supplied with the second refrigerant R2 expanded by the second expansion valve 23, and performs heat exchange between the decompressed second refrigerant R2 and the heat medium Mb and the first refrigerant R1 circulating in the battery heat exchange cycle 40, and guides the second refrigerant R2 to the second compressor 21.

[0018] The HVAC unit 30 includes a first low-pressure-side heat exchanger 14, an interior heat exchanger 32, an interior heat exchanger 33, a blower 34, and a temperature sensor 35. The interior heat exchanger 32 is disposed upstream of the first low-pressure-side heat exchanger 14 in the flow direction AD of air guided by the blower 34. The interior heat exchanger 33 is disposed downstream of the first low-pressure-side heat exchanger 14 in the flow direction AD of air guided by the blower 34.

[0019] When the vehicle temperature control system 1 is in cooling operation, the heat medium Mb that has exchanged heat with the second refrigerant R2 in the integrated heat exchanger 100 is supplied to the interior heat exchanger 32. The interior heat exchanger 32 exchanges heat between the air blown by the blower 34 and the heat medium Mb to cool the air.

[0020] When the vehicle temperature control system 1 is in heating operation, the heat medium Me that has exchanged heat with the second refrigerant R2 in the second high-pressure side heat exchanger 22 is supplied to the interior heat exchanger 33. The interior heat exchanger 33 exchanges heat between the air blown by the blower 34 and the heat medium Me, thereby heating the air.

[0021] The blower 34 is a device that blows air along the flow direction AD and guides it into the vehicle interior. The blower 34 blows air through the first low-pressure side heat exchanger 14 and the interior heat exchangers 32, 33, and guides the air that has passed through the first low-pressure side heat exchanger 14 and the interior heat exchangers 32, 33 into the vehicle interior.

[0022] The temperature sensor 35 is a device that detects the temperature of the air that is guided from the blower 34 to the first low-pressure side heat exchanger 14 and the interior heat exchangers 32 and 33 .

[0023] The battery heat exchange cycle 40 has a pump 73 and a heat medium heat exchanger 41, and heats or cools the battery (temperature control target) 4, which stores electric power used in the vehicle, with a heat medium Mb supplied to the heat medium heat exchanger 41. By operating the pump 73, the battery heat exchange cycle 40 circulates the heat medium Mb through a heat medium circuit 42 that connects the integrated heat exchanger 100, the interior heat exchanger 32, and the heat medium heat exchanger 41. When cooling of the battery 4 is required during air-conditioning operation of the vehicle temperature control system 1, the heat medium Mb is supplied to the heat medium heat exchanger 41, and heat exchange with the battery 4, which stores electric power used in the vehicle, is performed. When the vehicle temperature control system 1 operates in air-conditioning mode, the battery 4 is cooled by heat exchange with the heat medium Mb.

[0024] When the vehicle temperature control system 1 is in cooling operation or heating operation and cooling of the traction motor 5 or waste heat recovery is required, the motor heat exchanger 50 is supplied with the heat medium Me and exchanges heat with the traction motor 5. When the vehicle temperature control system 1 is in cooling operation or heating operation, the traction motor 5 is cooled by heat exchange with the heat medium Me.

[0025] The exterior heat exchange unit 60 is a unit that exchanges heat between air (outside air) and the heat medium Me outside the vehicle, and includes an exterior heat exchanger 61 and a fan 62. The fan 62 blows air toward the exterior heat exchanger 61. The exterior heat exchanger 61 exchanges heat between the heat medium Me and the air (outside air).

[0026] The control unit 90 is a device that controls the vehicle temperature control system 1. The control unit 90 controls each part of the vehicle temperature control system 1, including the first refrigeration cycle 10, the second refrigeration cycle 20, the battery heat exchange cycle 40, the pumps 71, 73, and 74, and the switching valves 81, 83, 84, and 85.

[0027] (Configuration of the integrated heat exchanger 100) The integrated heat exchanger 100 is a device that performs heat exchange between the first refrigerant R1 of the first refrigeration cycle 10 and the second refrigerant R2 of the second refrigeration cycle 20, between the first refrigerant R1 and the heat medium Mb of the battery heat exchange cycle 40, and between the second refrigerant R2 and the heat medium Mb. The integrated heat exchanger 100 performs heat exchange among the first refrigerant R1, the second refrigerant R2, and the heat medium Mb.

[0028] The integrated heat exchanger 100 functions as a condenser that condenses the first refrigerant R1 compressed by the first compressor 11 through heat exchange with the second refrigerant R2 and the heat medium Mb in the first refrigeration cycle 10. The integrated heat exchanger 100 also functions as an evaporator that evaporates the second refrigerant R2 expanded by the second expansion valve 23 through heat exchange with the first refrigerant R1 and the heat medium Mb in the second refrigeration cycle 20.

[0029] Fig. 2 is a perspective view showing the appearance of a plate heat exchanger, which is an example of the integrated heat exchanger 100 shown in Fig. 1. Fig. 3 is a schematic diagram showing the flows of the first refrigerant R1, the second refrigerant R2, and the heat medium Mb in the integrated heat exchanger 100 shown in Fig. 2. As shown in Figs. 2 and 3, the integrated heat exchanger 100 includes a plurality of rectangular plates 100A stacked in a stacking direction S and a stack 100S of the plates 100A.

[0030] A first refrigerant flow path 101, a second refrigerant flow path 102, and a heat medium flow path 103 are formed between plates 100A adjacent to each other in the stacking direction S. The plates 100A are not shown in Fig. 3 and in Figs. 4, 5, and 7 to 10 described below. In Fig. 3 and Figs. 4, 5, and 7 to 10 described below, the flow of the first refrigerant R1 is indicated by solid arrows, the flow of the second refrigerant R2 is indicated by dashed arrows, and the flow of the heat medium Mb is indicated by dotted arrows.

[0031] One side S1 of the stack 100S in the stacking direction S is a region that functions as a condenser in the first refrigeration cycle 10. The other side S2 of the stack 100S in the stacking direction S is a region that functions as an evaporator in the second refrigeration cycle 20. The region that functions as a condenser in the first refrigeration cycle 10 and the region that functions as an evaporator in the second refrigeration cycle 20 are adjacent to each other in the stacking direction S.

[0032] The first refrigerant flow path 101 is a flow path through which the first refrigerant R1 compressed by the first compressor 11 flows, and extends between the plates 100A on one side S1 in the stacking direction S in the longitudinal direction L of the plates 100A. A first refrigerant inlet R1in, which allows the first refrigerant R1 to flow into the first refrigerant flow path 101, is provided at one end in the longitudinal direction L of the side surface 100C on one side S1 in the stacking direction S of the stack 100S. A first refrigerant outlet R1out, which allows the first refrigerant R1 to flow out of the first refrigerant flow path 101, is provided at the other end in the longitudinal direction L of the side surface 100C.

[0033] The second refrigerant flow path 102 is a flow path through which the second refrigerant R2 expanded by the second expansion valve 23 flows, and extends between the plates 100A in the longitudinal direction L of the plates 100A from one side S1 to the other side S2 in the stacking direction S. A second refrigerant inlet R2in, which allows the second refrigerant R2 to flow into the second refrigerant flow path 102, is provided at one end in the longitudinal direction L of the side surface 100D on the other side S2 in the stacking direction S of the stack 100S. A second refrigerant outlet R2out, which allows the second refrigerant R2 to flow out from the second refrigerant flow path 102, is provided at the other end in the longitudinal direction L of the side surface 100D. The second refrigerant inlet R2in and the second refrigerant outlet R2out may be provided on the one side S1 in the stacking direction S.

[0034] The heat medium flow path 103 is a flow path through which the heat medium Mb that has passed through the heat medium heat exchanger 41 flows, and extends between the plates 100A in the longitudinal direction L on the other side S2 in the stacking direction S. A heat medium inlet Min that allows the heat medium Mb to flow into the heat medium flow path 103 and a heat medium outlet Mout that allows the heat medium Mb to flow out from the heat medium flow path 103 are provided on the other side S2 in the stacking direction S.

[0035] The heat medium Mb introduced from the heat medium circuit 42 into the heat medium inlet Min flows into the heat medium flow paths 103 through flow paths 104 extending in the stacking direction S, and while flowing through the heat medium flow paths 103 in the longitudinal direction L, exchanges heat with the first refrigerant R1 flowing through the first refrigerant flow path 101 and the second refrigerant R2 flowing through the second refrigerant flow path 102. The heat medium Mb then flows through flow paths 105 extending in the stacking direction S and flows out of the heat medium circuit 42 from the heat medium outlet Mout.

[0036] The first refrigerant R1 introduced from the first refrigerant circuit 15 to the first refrigerant inlet R1in flows into the plurality of first refrigerant flow paths 101 through flow paths 106 extending in the stacking direction S, and flows out from each first refrigerant flow path 101 through a flow path 107 extending in the stacking direction S. The same is true for the second refrigerant flow path 102, which is formed with flow paths 108 and 109 extending in the stacking direction S.

[0037] To increase the amount of heat exchanged between the heat medium Mb and the second refrigerant R2 throughout the heat exchange process, the heat medium Mb and the second refrigerant R2 preferably flow in opposite directions, that is, counterflow, as shown in Fig. 3. In the example shown in Fig. 3, the heat medium Mb flows from the other side L2 to the one side L1 in the longitudinal direction L, and the second refrigerant R2 flows from the one side L1 to the other side L2 in the longitudinal direction L.

[0038] The heat medium inlet Min, the heat medium outlet Mout, the first refrigerant inlet R1in, the first refrigerant outlet R1out, the second refrigerant inlet R2in, and the second refrigerant outlet R2out are all connected to flow paths within the laminate 100S through openings (not shown) that penetrate the side walls of the laminate 100S, and are connected to pipes (not shown) for the first refrigerant R1, the second refrigerant R2, and the heat medium Mb outside the laminate 100S.

[0039] The heat medium inlet Min, heat medium outlet Mout, first refrigerant inlet R1in, first refrigerant outlet R1out, second refrigerant inlet R2in, and second refrigerant outlet R2out do not necessarily have to be located on the same surface as the corresponding openings, and do not necessarily have to be provided at the end of the side surface of stack 100S in the longitudinal direction L. For example, by using components connected to first refrigerant inlet R1in and first refrigerant outlet R1out, respectively, and routed to the side surface where second refrigerant inlet R2in and second refrigerant outlet R2out are located, it is possible to provide heat medium inlet Min, heat medium outlet Mout, first refrigerant inlet R1in, first refrigerant outlet R1out, second refrigerant inlet R2in, and second refrigerant outlet R2out on the same side surface of stack 100S.

[0040] In the integrated heat exchanger 100, the first refrigerant flow path 101, the second refrigerant flow path 102, and the heat medium flow path 103 are configured so that a second heat exchange rate between the second refrigerant R2 and the heat medium Mb is greater than a first heat exchange rate between the first refrigerant R1 and the heat medium Mb. Specifically, the integrated heat exchanger 100 is configured so that a second area, which is the sum of the areas of the plates 100A separating the second refrigerant flow path 102 and the heat medium flow path 103, is larger than a first area, which is the sum of the areas of the plates 100A separating the first refrigerant flow path 101 and the heat medium flow path 103.

[0041] 3, the first refrigerant flow path 101 and the heat medium flow path 103 are not adjacent to each other, and the second area is larger than the first area. The second heat exchange amount between the second refrigerant R2 and the heat medium Mb is preferably 1.1 times or more, and more preferably 1.5 times or more, the first heat exchange amount between the first refrigerant R1 and the heat medium Mb.

[0042] (First Modification of the Integrated Heat Exchanger 100) As shown in Fig. 4, the integrated heat exchanger 100 of this embodiment may be a first modification in which the region where the first refrigerant flow path 101 is arranged and the region where the heat medium flow path 103 is arranged are adjacent to each other in the longitudinal direction L. Fig. 4 is a schematic diagram showing the flows of the first refrigerant R1, the second refrigerant R2, and the heat medium Mb in the first modification of the integrated heat exchanger 100 shown in Fig. 2.

[0043] 4, the first refrigerant flow paths 101 extend between the plates 100A in the longitudinal direction L of the plates 100A on one side L1 in the longitudinal direction L of the plates 100A. The heat medium flow paths 103 extend between the plates 100A in the longitudinal direction L of the plates 100A on the other side L2 in the longitudinal direction L of the plates 100A. The second refrigerant flow paths 102 extend between the plates 100A in the longitudinal direction L from one side L1 to the other side L2 in the longitudinal direction L.

[0044] According to the first variant of the integrated heat exchanger 100, the first refrigerant flow path 101 and the heat medium flow path 103 are not arranged adjacent to each other in the stacking direction S, so that the second heat exchange amount between the second refrigerant R2 and the heat medium Mb is greater than the first heat exchange amount between the first refrigerant R1 and the heat medium Mb.

[0045] (Second Modification of Integrated Heat Exchanger 100) As shown in Fig. 5 , the integrated heat exchanger 100 of this embodiment may be configured as a second modification in which the distance from the second refrigerant flow path 102 to the heat medium flow path 103 is shorter in the stacking direction S than the distance from the first refrigerant flow path 101 to the heat medium flow path 103. Fig. 5 is a schematic diagram showing the flows of the first refrigerant R1, the second refrigerant R2, and the heat medium Mb in the second modification of the integrated heat exchanger 100 shown in Fig. 2 .

[0046] 5 , the first refrigerant flow paths 101 extend between the plates 100A from one side L2 to one side L1 in the longitudinal direction L of the plates 100A in a region spanning from one side S1 to the other side S2 in the stacking direction S. The second refrigerant flow paths 102 extend between the plates 100A from one side L1 to the other side L2 in the longitudinal direction L of the plates 100A in a region spanning from one side S1 to the other side S2 in the stacking direction S. The heat medium flow paths 103 extend between the plates 100A from one side L1 to the other side L2 in the longitudinal direction L of the plates 100A in a region spanning from one side S1 to the other side S2 in the stacking direction S.

[0047] 5 , in the stacking direction S, the second refrigerant flow path 102 is disposed adjacent to the heat medium flow path 103, and the first refrigerant flow path 101 is disposed away from the heat medium flow path 103 with the second refrigerant flow path 102 sandwiched between them. In the stacking direction S, the distance from the second refrigerant flow path 102 to the heat medium flow path 103 is shorter than the distance from the first refrigerant flow path 101 to the heat medium flow path 103. Therefore, the second heat exchange amount between the second refrigerant R2 and the heat medium Mb is greater than the first heat exchange amount between the first refrigerant R1 and the heat medium Mb.

[0048] The vehicle temperature control system 1 according to the first embodiment of the present disclosure described above provides the following functions and effects. In the vehicle temperature control system 1 according to this embodiment, the integrated heat exchanger 100 exchanges heat between the first refrigerant R1 circulating through the first refrigeration cycle 10 and compressed by the first compressor 11, and the second refrigerant R2 circulating through the second refrigeration cycle 20 and expanded by the second expansion valve 23. Because heat is exchanged directly between the first refrigerant R1 in the first refrigeration cycle 10 and the second refrigerant R2 in the second refrigeration cycle 20, the coefficient of performance (COP) of the vehicle temperature control system 1 can be improved compared to when heat is exchanged indirectly from the first refrigerant R1 to the second refrigerant R2 via another heat medium.

[0049] Furthermore, according to the vehicle temperature control system 1 of this embodiment, the heat medium Mb that has passed through the heat medium heat exchanger 41 exchanges heat with the first refrigerant R1 and the second refrigerant R2 in the integrated heat exchanger 100. The heat medium Mb that has exchanged heat with the first refrigerant R1 and the second refrigerant R2 circulates through the heat medium circuit 42 and is guided to the heat medium heat exchanger 41, where it heats or cools the battery 4. In the integrated heat exchanger 100, the temperature of the battery 4 can be controlled to an appropriate temperature by appropriately adjusting the first heat exchange amount between the first refrigerant R1 and the heat medium Mb and the second heat exchange amount between the second refrigerant R2 and the heat medium Mb.

[0050] In the vehicle temperature control system 1 of this embodiment, because the second heat exchange rate is greater than the first heat exchange rate, the cooling capacity of the second refrigerant R2 for cooling the heat medium Mb is greater than the heating capacity of the first refrigerant R1 for heating the heat medium Mb. Since the battery 4 is cooled by the heat medium Mb cooled by the integrated heat exchanger 100, the COP when cooling the battery 4 with the heat medium Mb can be improved.

[0051] According to the vehicle temperature control system 1 of this embodiment, by making the second heat exchange amount 1.1 times or more the first heat exchange amount, the cooling capacity of the second refrigerant R2 to cool the heat medium is appropriately made higher than the heating capacity of the first refrigerant R1 to heat the heat medium Mb, thereby improving the COP when cooling the battery 4 with the heat medium Mb.

[0052] According to the vehicle temperature control system 1 of this embodiment, the integrated heat exchanger 100 is a plate-type heat exchanger, and the second area of ​​the plate 100A separating the second refrigerant flow path 102 and the heat medium flow path 103 is larger than the first area of ​​the plate 100A separating the first refrigerant flow path 101 and the heat medium flow path 103. This makes it possible to appropriately increase the cooling capacity of the second refrigerant R2 to cool the heat medium Mb compared to the heating capacity of the first refrigerant R1 to heat the heat medium Mb, thereby improving the COP when cooling the battery 4 with the heat medium Mb.

[0053] According to the vehicle temperature control system 1 of this embodiment, the first refrigerant flow path 101 is arranged only on one side S1 in the stacking direction S, the heat medium flow path 103 is arranged only on the other side S2 in the stacking direction S, and the second refrigerant flow path 102 is arranged across one side S1 and the other side S2 in the stacking direction S. This makes it possible to appropriately increase the cooling capacity of the second refrigerant R2 to cool the heat medium Mb compared to the heating capacity of the first refrigerant R1 to heat the heat medium Mb, thereby improving the COP when cooling the battery 4 with the heat medium Mb.

[0054] According to the vehicle temperature control system 1 of this embodiment, the first refrigerant flow path 101 is arranged only on one side L1 in the longitudinal direction L of the plate 100A, the heat medium flow path 103 is arranged only on the other side L2 in the longitudinal direction L of the plate 100A, and the second refrigerant flow path 102 is arranged across one side L1 and the other side L2 in the longitudinal direction L of the plate 100A. This makes it possible to appropriately increase the cooling capacity of the second refrigerant R2 to cool the heat medium Mb compared to the heating capacity of the first refrigerant R1 to heat the heat medium Mb, thereby improving the COP when cooling the battery 4 with the heat medium Mb.

[0055] Second Embodiment A vehicle temperature control system 1A according to a second embodiment of the present disclosure will be described with reference to the drawings. This embodiment is a modification of the first embodiment, and is similar to the first embodiment except where specifically described below, and therefore will not be described below.

[0056] In the vehicle temperature control system 1 according to the first embodiment of the present disclosure, the integrated heat exchanger 100 is configured to have the first refrigerant flow path 101, the second refrigerant flow path 102, and the heat medium flow path 103 so that the second heat exchange rate between the second refrigerant R2 and the heat medium Mb is greater than the first heat exchange rate between the first refrigerant R1 and the heat medium Mb. In contrast, in the vehicle temperature control system 1A according to the present embodiment, the integrated heat exchanger 100 is configured to have the first refrigerant flow path 101, the second refrigerant flow path 102, and the heat medium flow path 103 so that the first heat exchange rate between the first refrigerant R1 and the heat medium Mb is greater than the second heat exchange rate between the second refrigerant R2 and the heat medium Mb.

[0057] 6 is a schematic diagram showing a vehicle temperature control system 1A according to a second embodiment of the present disclosure, illustrating the vehicle temperature control system 1A in heating operation. The vehicle temperature control system 1A of this embodiment differs from the vehicle temperature control system 1 of the first embodiment in that the HVAC unit 30 includes an interior heat exchanger 31, a pump 72, and a switching valve 82.

[0058] The first low-pressure side heat exchanger 14 is supplied with the first refrigerant R1 expanded by the first expansion valve 13, and performs heat exchange between the decompressed first refrigerant R1 and the heat medium Me circulating through the exterior heat exchange unit 60, and then leads it to the first compressor 11.

[0059] The second high-pressure side heat exchanger 22 exchanges heat between the second refrigerant R2 compressed by the second compressor 21 and the heat medium Mi, and supplies the heat medium Mi to the interior heat exchanger 33 by the pump 71. When the vehicle temperature control system 1A is in heating operation, the interior heat exchanger 33 exchanges heat between the air blown by the blower 34 and the heat medium Mi to heat the air.

[0060] (Configuration of the integrated heat exchanger 100) The integrated heat exchanger 100 is a device that performs heat exchange between the first refrigerant R1 of the first refrigeration cycle 10 and the second refrigerant R2 of the second refrigeration cycle 20, between the first refrigerant R1 and the heat medium Mb of the battery heat exchange cycle 40, and between the second refrigerant R2 and the heat medium Mb. The integrated heat exchanger 100 performs heat exchange among the first refrigerant R1, the second refrigerant R2, and the heat medium Mb.

[0061] The integrated heat exchanger 100 functions as a condenser that condenses the first refrigerant R1 compressed by the first compressor 11 through heat exchange with the second refrigerant R2 and the heat medium Mb in the first refrigeration cycle 10. The integrated heat exchanger 100 also functions as an evaporator that evaporates the second refrigerant R2 expanded by the second expansion valve 23 through heat exchange with the first refrigerant R1 and the heat medium Mb in the second refrigeration cycle 20.

[0062] FIG. 7 is a schematic diagram showing the flows of the first refrigerant R1, the second refrigerant R2, and the heat medium Mb in the integrated heat exchanger 100 shown in FIG.

[0063] The first refrigerant flow path 101 is a flow path through which the first refrigerant R1 compressed by the first compressor 11 flows, and extends between the plates 100A in the longitudinal direction L of the plates 100A in a region from one side S1 to the other side S2 in the stacking direction S. A first refrigerant inlet R1in, which allows the first refrigerant R1 to flow into the first refrigerant flow path 101, is provided at one end in the longitudinal direction L of the side surface 100D on the other side S2 in the stacking direction S of the stack 100S. A first refrigerant outlet R1out, which allows the first refrigerant R1 to flow out from the first refrigerant flow path 101, is provided at the other end in the longitudinal direction L of the side surface 100D. Note that the first refrigerant inlet R1in and the first refrigerant outlet R1out may be provided on the one side S1 in the stacking direction S.

[0064] The second refrigerant flow path 102 is a flow path through which the second refrigerant R2 expanded by the second expansion valve 23 flows, and extends between the plates 100A on one side S1 in the stacking direction S in the longitudinal direction L of the plates 100A. A second refrigerant inlet R2in, which allows the second refrigerant R2 to flow into the second refrigerant flow path 102, is provided at one end in the longitudinal direction L of the side surface 100C on one side S1 in the stacking direction S of the stack 100S. A second refrigerant outlet R2out, which allows the second refrigerant R2 to flow out from the second refrigerant flow path 102, is provided at the other end in the longitudinal direction L of the side surface 100C.

[0065] The heat medium flow path 103 is a flow path through which the heat medium Mb that has passed through the heat medium heat exchanger 41 flows, and extends between the plates 100A in the longitudinal direction L on the other side S2 in the stacking direction S. A heat medium inlet Min that allows the heat medium Mb to flow into the heat medium flow path 103 and a heat medium outlet Mout that allows the heat medium Mb to flow out from the heat medium flow path 103 are provided on the other side S2 in the stacking direction S.

[0066] In the integrated heat exchanger 100, the first refrigerant flow path 101, the second refrigerant flow path 102, and the heat medium flow path 103 are configured so that a first heat exchange rate between the first refrigerant R1 and the heat medium Mb is greater than a second heat exchange rate between the second refrigerant R2 and the heat medium Mb. Specifically, the first area, which is the total area of ​​the plates 100A separating the first refrigerant flow path 101 and the heat medium flow path 103, is larger than a second area, which is the total area of ​​the plates 100A separating the second refrigerant flow path 102 and the heat medium flow path 103.

[0067] 7, the second refrigerant flow path 102 and the heat medium flow path 103 are not adjacent to each other, and the first area is larger than the second area. The first heat exchange amount between the first refrigerant R1 and the heat medium Mb is preferably 1.1 times or more, and more preferably 1.5 times or more, the second heat exchange amount between the second refrigerant R2 and the heat medium Mb.

[0068] (Modification of the integrated heat exchanger 100) As shown in Fig. 8 , the integrated heat exchanger 100 of this embodiment may be modified such that the region where the second refrigerant flow path 102 is arranged and the region where the heat medium flow path 103 is arranged are adjacent to each other in the longitudinal direction L. Fig. 8 is a schematic diagram showing the flows of the first refrigerant R1, the second refrigerant R2, and the heat medium Mb in the modification of the integrated heat exchanger 100 shown in Fig. 7 .

[0069] 8 , the second refrigerant flow paths 102 extend between the plates 100A in the longitudinal direction L of the plates 100A on one side L1 in the longitudinal direction L of the plates 100A. The heat medium flow paths 103 extend between the plates 100A in the longitudinal direction L of the plates 100A on the other side L2 in the longitudinal direction L of the plates 100A. The first refrigerant flow paths 101 extend between the plates 100A in the longitudinal direction L from one side L1 to the other side L2 in the longitudinal direction L.

[0070] According to a modified example of the integrated heat exchanger 100, the second refrigerant flow path 102 and the heat medium flow path 103 are not arranged adjacent to each other in the stacking direction S, so that the first heat exchange amount between the first refrigerant R1 and the heat medium Mb is greater than the second heat exchange amount between the second refrigerant R2 and the heat medium Mb.

[0071] The following describes the functions and effects of the vehicle temperature control system 1A of the present embodiment described above. According to the vehicle temperature control system 1A of the present embodiment, the first heat exchange rate between the first refrigerant R1 and the heat medium Mb is greater than the second heat exchange rate between the second refrigerant R2 and the heat medium Mb. Therefore, the heating capacity of the first refrigerant R1 to heat the heat medium Mb is greater than the cooling capacity of the second refrigerant R2 to cool the heat medium Mb. Because the battery 4 is heated by the heat medium Mb heated by the integrated heat exchanger 100, the COP (Coefficient of Performance) when the battery 4 is heated by the heat medium Mb can be improved.

[0072] According to the vehicle temperature control system 1A of this embodiment, by making the first heat exchange amount 1.1 times or more the second heat exchange amount, the heating capacity of the first refrigerant R1 to heat the heat medium Mb is appropriately made higher than the cooling capacity of the second refrigerant R2 to cool the heat medium, thereby improving the COP when heating the battery 4 with the heat medium Mb.

[0073] According to the vehicle temperature control system 1A of this embodiment, the integrated heat exchanger 100 is a plate-type heat exchanger, and the first area of ​​the plate 100A separating the first refrigerant flow path 101 and the heat medium flow path 103 is made larger than the second area of ​​the plate 100A separating the second refrigerant flow path 102 and the heat medium flow path 103. This makes it possible to appropriately increase the heating capacity of the first refrigerant R1 to heat the heat medium Mb compared to the cooling capacity of the second refrigerant R2 to cool the heat medium Mb, thereby improving the COP when the battery 4 is heated by the heat medium Mb.

[0074] According to the vehicle temperature control system 1A of this embodiment, the second refrigerant flow path 102 is arranged only on one side S1 in the stacking direction S, the heat medium flow path 103 is arranged only on the other side S2 in the stacking direction S, and the first refrigerant flow path 101 is arranged across one side S1 and the other side S2 in the stacking direction S, so that the heating capacity of the first refrigerant R1 to heat the heat medium Mb is appropriately made higher than the cooling capacity of the second refrigerant R2 to cool the heat medium Mb, and the COP when the battery 4 is heated by the heat medium Mb can be improved.

[0075] According to the vehicle temperature control system 1A of this embodiment, the second refrigerant flow path 102 is arranged only on one side L1 in the longitudinal direction L of the plate 100A, the heat medium flow path 103 is arranged only on the other side L2 in the longitudinal direction L of the plate 100A, and the first refrigerant flow path 101 is arranged across the one side L1 and the other side L2 in the longitudinal direction L of the plate 100A. This makes it possible to appropriately increase the heating capacity of the first refrigerant R1 to heat the heat medium Mb compared to the cooling capacity of the second refrigerant R2 to cool the heat medium Mb, thereby improving the COP when the battery 4 is heated by the heat medium Mb.

[0076] Third Embodiment A vehicle temperature control system according to a third embodiment of the present disclosure will be described with reference to the drawings. This embodiment is a modification of the first embodiment, and is similar to the first embodiment except where specifically described below, and therefore will not be described below.

[0077] In the vehicle temperature control system 1 according to the first embodiment of the present disclosure, the integrated heat exchanger 100 is configured to have the first refrigerant flow path 101, the second refrigerant flow path 102, and the heat medium flow path 103 so that the second heat exchange rate between the second refrigerant R2 and the heat medium Mb is greater than the first heat exchange rate between the first refrigerant R1 and the heat medium Mb. In contrast, in the vehicle temperature control system of the present embodiment, the integrated heat exchanger 100 is configured to have the first refrigerant flow path 101, the second refrigerant flow path 102, and the heat medium flow path 103 so that the first heat exchange rate between the first refrigerant R1 and the heat medium Mb and the second heat exchange rate between the second refrigerant R2 and the heat medium Mb are the same.

[0078] (Configuration of Integrated Heat Exchanger 100) FIG. 9 is a schematic diagram showing the flows of the first refrigerant R1, the second refrigerant R2, and the heat medium Mb in the integrated heat exchanger 100. As shown in FIG.

[0079] The first refrigerant flow path 101 is a flow path through which the first refrigerant R1 compressed by the first compressor 11 flows, and extends between the plates 100A on one side S1 in the stacking direction S in the longitudinal direction L of the plates 100A. A first refrigerant inlet R1in, which allows the first refrigerant R1 to flow into the first refrigerant flow path 101, is provided at one end in the longitudinal direction L of the side surface 100C on one side S1 in the stacking direction S of the stack 100S. A first refrigerant outlet R1out, which allows the first refrigerant R1 to flow out of the first refrigerant flow path 101, is provided at the other end in the longitudinal direction L of the side surface 100C.

[0080] The second refrigerant flow path 102 is a flow path through which the second refrigerant R2 expanded by the second expansion valve 23 flows, and extends between the plates 100A in the longitudinal direction L of the plates 100A on the other side S2 in the stacking direction S. A second refrigerant inlet R2in, which allows the second refrigerant R2 to flow into the second refrigerant flow path 102, is provided at one end in the longitudinal direction L of the side surface 100D on the other side S2 in the stacking direction S of the stack 100S. A second refrigerant outlet R2out, which allows the second refrigerant R2 to flow out from the second refrigerant flow path 102, is provided at the other end in the longitudinal direction L of the side surface 100D. The second refrigerant inlet R2in and the second refrigerant outlet R2out may be provided on the one side S1 in the stacking direction S.

[0081] The heat medium flow path 103 is a flow path through which the heat medium Mb that has passed through the heat medium heat exchanger 41 flows, and extends between the plates 100A in the longitudinal direction L in a region from one side S1 to the other side S2 in the stacking direction S. A heat medium inlet Min through which the heat medium Mb flows into the heat medium flow path 103 and a heat medium outlet Mout through which the heat medium Mb flows out from the heat medium flow path 103 are provided on the other side S2 in the stacking direction S.

[0082] In the integrated heat exchanger 100, the first refrigerant flow path 101, the second refrigerant flow path 102, and the heat medium flow path 103 are configured so that a first heat exchange amount between the first refrigerant R1 and the heat medium Mb is equal to a second heat exchange amount between the second refrigerant R2 and the heat medium Mb. Specifically, the first area, which is the total area of ​​the plates 100A separating the first refrigerant flow path 101 and the heat medium flow path 103, is equal to a second area, which is the total area of ​​the plates 100A separating the second refrigerant flow path 102 and the heat medium flow path 103.

[0083] (Modification of the integrated heat exchanger 100) As shown in Fig. 10 , the integrated heat exchanger 100 of this embodiment may be modified such that the region where the first refrigerant flow path 101 is disposed and the region where the second refrigerant flow path 102 is disposed are adjacent to each other in the longitudinal direction L. Fig. 10 is a schematic diagram showing the flows of the first refrigerant R1, the second refrigerant R2, and the heat medium Mb in the modification of the integrated heat exchanger 100 shown in Fig. 9 .

[0084] 10 , the second refrigerant flow paths 102 extend between the plates 100A in the longitudinal direction L of the plates 100A on one side L1 in the longitudinal direction L of the plates 100A. The first refrigerant flow paths 101 extend between the plates 100A in the longitudinal direction L of the plates 100A on the other side L2 in the longitudinal direction L of the plates 100A. The heat medium flow paths 103 extend between the plates 100A in the longitudinal direction L from one side L1 to the other side L2 in the longitudinal direction L.

[0085] According to a modified example of the integrated heat exchanger 100, the first refrigerant flow path 101 and the heat medium flow path 103 are adjacent to each other in the stacking direction S, and the second refrigerant flow path 102 and the heat medium flow path 103 are adjacent to each other in the stacking direction S, and the lengths of these in the longitudinal direction L are the same, so that the first heat exchange amount between the first refrigerant R1 and the heat medium Mb is the same as the second heat exchange amount between the second refrigerant R2 and the heat medium Mb.

[0086] The temperature control system according to each of the above-described embodiments can be understood, for example, as follows: A temperature control system according to a first aspect of the present disclosure includes a first compressor (11), a first expansion valve (13) that expands a first refrigerant (R1) compressed by the first compressor, a first low-pressure side heat exchanger (14) that receives the first refrigerant expanded by the first expansion valve and directs the first refrigerant to the first compressor, a first refrigeration cycle (10) that circulates the first refrigerant in a first refrigerant circuit (15), a second compressor (21), a second high-pressure side heat exchanger (22) that receives the second refrigerant compressed by the second compressor, and a second expansion valve (23) that expands the second refrigerant supplied from the second high-pressure side heat exchanger and directs the second refrigerant to the second compressor, and a second refrigeration cycle (10) that circulates the second refrigerant in a second refrigerant circuit (25). a heat medium cycle (40) having a second refrigeration cycle (20) for circulating the heat medium in a heat medium circuit (42), a pump (73) for pumping a heat medium (Mb), and a heat medium heat exchanger (41) for heating or cooling a temperature control target (4) with the heat medium, and having a first refrigerant flow path (101) through which the first refrigerant compressed by the first compressor flows, a second refrigerant flow path (102) through which the second refrigerant expanded by the second expansion valve flows, and a heat medium flow path (103) through which the heat medium that has passed through the heat medium heat exchanger flows, and an integrated heat exchanger (100) for performing heat exchange between the first refrigerant and the second refrigerant, heat exchange between the first refrigerant and the heat medium, and heat exchange between the second refrigerant and the heat medium.

[0087] In the temperature control system according to the first aspect of the present disclosure, the integrated heat exchanger performs heat exchange between a first refrigerant circulating through a first refrigeration cycle and compressed by a first compressor, and a second refrigerant circulating through a second refrigeration cycle and expanded by a second expansion valve. Because heat exchange is performed directly between the first refrigerant in the first refrigeration cycle and the second refrigerant in the second refrigeration cycle, the coefficient of performance (COP) of the temperature control system can be improved compared to when heat is exchanged indirectly from the first refrigerant to the second refrigerant via another heat medium.

[0088] According to a temperature control system according to a first aspect of the present disclosure, the heat medium passing through the heat medium heat exchanger exchanges heat with a first refrigerant and a second refrigerant in the integrated heat exchanger. The heat medium that has exchanged heat with the first refrigerant and the second refrigerant circulates through a heat medium circuit and is guided to the heat medium heat exchanger, where it heats or cools a temperature control target. By appropriately adjusting the first heat exchange amount between the first refrigerant and the heat medium and the second heat exchange amount between the second refrigerant and the heat medium in the integrated heat exchanger, the temperature of the temperature control target can be controlled to an appropriate temperature.

[0089] A temperature control system according to a second aspect of the present disclosure is the first aspect, further including the following configuration: In the integrated heat exchanger, a second heat exchange amount between the second refrigerant and the heat medium is greater than a first heat exchange amount between the first refrigerant and the heat medium.

[0090] In the temperature control system according to the second aspect of the present disclosure, since the second heat exchange rate is greater than the first heat exchange rate, the cooling capacity of the second refrigerant for the heat medium is greater than the heating capacity of the first refrigerant for heating the heat medium. Since the temperature control target is cooled by the heat medium cooled by the integrated heat exchanger, the COP when cooling the temperature control target with the heat medium can be improved.

[0091] The temperature adjustment system according to a third aspect of the present disclosure is the second aspect, further including the following configuration: the second heat exchange amount is 1.1 times or more the first heat exchange amount.

[0092] According to the temperature control system of the third aspect of the present disclosure, by making the second heat exchange amount 1.1 times or more the first heat exchange amount, the cooling capacity of the second refrigerant to cool the heat medium can be appropriately made higher than the heating capacity of the first refrigerant to heat the heat medium, thereby improving the COP when cooling the temperature control target with the heat medium.

[0093] A temperature control system according to a fourth aspect of the present disclosure is the second or third aspect, further comprising the following configuration: That is, the integrated heat exchanger is a plate-type heat exchanger having a plurality of plates stacked in a stacking direction, the first refrigerant flow path, the second refrigerant flow path, and the heat medium flow path are formed between the plurality of plates, and a second area of ​​the plate separating the second refrigerant flow path and the heat medium flow path is larger than a first area of ​​the plate separating the first refrigerant flow path and the heat medium flow path.

[0094] According to the temperature control system of the fourth aspect of the present disclosure, the integrated heat exchanger is a plate-type heat exchanger, and the second area of ​​the plate separating the second refrigerant flow path and the heat medium flow path is larger than the first area of ​​the plate separating the first refrigerant flow path and the heat medium flow path. This makes it possible to appropriately increase the cooling capacity of the second refrigerant to cool the heat medium compared to the heating capacity of the first refrigerant to heat the heat medium, thereby improving the COP when the temperature control target is cooled by the heat medium.

[0095] A temperature control system according to a fifth aspect of the present disclosure is the fourth aspect, further including the following configuration: the first refrigerant flow path extends between the plates in a longitudinal direction of the plates on one side in the stacking direction, the heat medium flow path extends between the plates in the longitudinal direction on the other side in the stacking direction, and the second refrigerant flow path extends between the plates in the longitudinal direction across the one side and the other side in the stacking direction.

[0096] According to the temperature control system of the fifth aspect of the present disclosure, by arranging the first refrigerant flow path only on one side in the stacking direction, arranging the heat medium flow path only on the other side in the stacking direction, and arranging the second refrigerant flow path across one side and the other side in the stacking direction, the cooling capacity of the second refrigerant to cool the heat medium can be appropriately made higher than the heating capacity of the first refrigerant to heat the heat medium, and the COP can be improved when the temperature control target is cooled by the heat medium.

[0097] A temperature control system according to a sixth aspect of the present disclosure is the fourth aspect, further including the following configuration: the first refrigerant flow path extends in the longitudinal direction (L) between the plates on one side of the plates in the longitudinal direction of the plates, the heat medium flow path extends in the longitudinal direction between the plates on the other side of the longitudinal direction, and the second refrigerant flow path extends in the longitudinal direction between the plates across the one side and the other side in the longitudinal direction.

[0098] According to the temperature control system of the sixth aspect of the present disclosure, by arranging the first refrigerant flow path only on one side of the plate in the longitudinal direction, arranging the heat medium flow path only on the other side of the plate in the longitudinal direction, and arranging the second refrigerant flow path across both sides of the plate in the longitudinal direction, the cooling capacity of the second refrigerant to cool the heat medium can be appropriately made higher than the heating capacity of the first refrigerant to heat the heat medium, and the COP can be improved when the temperature control target is cooled by the heat medium.

[0099] A temperature control system according to a seventh aspect of the present disclosure is the first aspect, further including the following configuration: In the integrated heat exchanger, a first heat exchange amount between the first refrigerant and the heat medium is greater than a second heat exchange amount between the second refrigerant and the heat medium.

[0100] In the temperature control system according to the seventh aspect of the present disclosure, since the first heat exchange amount is greater than the second heat exchange amount, the heating capacity of the first refrigerant to heat the heat medium is greater than the cooling capacity of the second refrigerant to cool the heat medium. Since the temperature control target is heated by the heat medium heated by the integrated heat exchanger, the COP when the temperature control target is heated by the heat medium can be improved.

[0101] A temperature adjustment system according to an eighth aspect of the present disclosure is the seventh aspect, further including the following configuration: the first heat exchange amount is 1.1 times or more the second heat exchange amount.

[0102] According to the temperature control system of the eighth aspect of the present disclosure, by making the first heat exchange amount 1.1 times or more the second heat exchange amount, the heating capacity of the first refrigerant to heat the heat medium can be made appropriately higher than the cooling capacity of the second refrigerant to cool the heat medium, thereby improving the COP when heating the temperature control target with the heat medium.

[0103] A temperature control system according to a ninth aspect of the present disclosure is the seventh or eighth aspect, further comprising the following configuration: the integrated heat exchanger is a plate-type heat exchanger having a plurality of plates stacked in a stacking direction, the first refrigerant flow path, the second refrigerant flow path, and the heat medium flow path are formed between the plurality of plates, and a first area of ​​the plate separating the first refrigerant flow path and the heat medium flow path is larger than a second area of ​​the plate separating the second refrigerant flow path and the heat medium flow path.

[0104] According to the temperature control system of the ninth aspect of the present disclosure, the integrated heat exchanger is a plate-type heat exchanger, and the first area of ​​the plate separating the first refrigerant flow path and the heat medium flow path is larger than the second area of ​​the plate separating the second refrigerant flow path and the heat medium flow path. This makes it possible to appropriately increase the heating capacity of the first refrigerant to heat the heat medium compared to the cooling capacity of the second refrigerant to cool the heat medium, thereby improving the COP when the temperature control target is heated by the heat medium.

[0105] A temperature control system according to a tenth aspect of the present disclosure is the ninth aspect, further including the following configuration: the second refrigerant flow path extends between the plates in a longitudinal direction of the plates on one side in the stacking direction, the heat medium flow path extends between the plates in the longitudinal direction on the other side in the stacking direction, and the first refrigerant flow path extends between the plates in the longitudinal direction across the one side and the other side in the stacking direction.

[0106] According to the temperature control system of the tenth aspect of the present disclosure, by arranging the second refrigerant flow path only on one side in the stacking direction, arranging the heat medium flow path only on the other side in the stacking direction, and arranging the first refrigerant flow path across one side and the other side in the stacking direction, the heating capacity of the first refrigerant to heat the heat medium can be appropriately made higher than the cooling capacity of the second refrigerant to cool the heat medium, and the COP can be improved when the temperature control target is heated by the heat medium.

[0107] A temperature control system according to an eleventh aspect of the present disclosure is the ninth aspect, further including the following configuration: the second refrigerant flow path extends in the longitudinal direction of the plates between the plates on one side in the longitudinal direction of the plates, the heat medium flow path extends in the longitudinal direction between the plates on the other side in the longitudinal direction, and the first refrigerant flow path extends in the longitudinal direction between the plates across the one side and the other side in the longitudinal direction.

[0108] According to the temperature control system of the eleventh aspect of the present disclosure, by arranging the second refrigerant flow path only on one side of the plate in the longitudinal direction, arranging the heat medium flow path only on the other side of the plate in the longitudinal direction, and arranging the first refrigerant flow path across one side and the other side of the plate in the longitudinal direction, the heating capacity of the first refrigerant to heat the heat medium can be appropriately made higher than the cooling capacity of the second refrigerant to cool the heat medium, and the COP can be improved when the temperature control target is heated by the heat medium.

[0109] DESCRIPTION OF SYMBOLS 1, 1A Vehicle temperature control system 4 Battery (temperature control target) 5 Travel motor 10 First refrigeration cycle 11 First compressor 13 First expansion valve 14 First low-pressure side heat exchanger 15 First refrigerant circuit 20 Second refrigeration cycle 21 Second compressor 22 Second high-pressure side heat exchanger 23 Second expansion valve 25 Second refrigerant circuit 30 HVAC unit 31, 32, 33 In-vehicle heat exchanger 34 Blower 35 Temperature sensor 40 Battery heat exchange cycle 41 Heat medium heat exchanger 42 Heat medium circuit 50 Motor heat exchanger 60 Exterior heat exchange unit 61 Exterior heat exchanger 62 Fan 71, 72, 73, 74 Pump 81, 82, 83, 84, 85 Switching valve 90 Control unit 100 Integrated heat exchanger 100A Plates 100C, 100D Side surface 100S Laminate 101 First refrigerant flow path 102 Second refrigerant flow path 103 Heat medium flow path L Longitudinal direction L1 One side L2 Other side Mb, Me, Mi Heat medium Min Heat medium inlet Mout Heat medium outlet R1 First refrigerant R1in First refrigerant inlet R1out First refrigerant outlet R2 Second refrigerant R2in Second refrigerant inlet R2out Second refrigerant outlet S Lamination direction S1 One side S2 Other side

Claims

1. A first refrigeration cycle having a first compressor, a first expansion valve that expands a first refrigerant compressed by the first compressor, and a first low-pressure side heat exchanger that is supplied with the first refrigerant expanded by the first expansion valve and guides the first refrigerant to the first compressor, and circulates the first refrigerant in a first refrigerant circuit; a second refrigeration cycle having a second compressor, a second high-pressure side heat exchanger that is supplied with a second refrigerant compressed by the second compressor, and a second expansion valve that expands the second refrigerant supplied from the second high-pressure side heat exchanger and guides the second refrigerant to the second compressor, and circulates the second refrigerant in a second refrigerant circuit; and a heat medium cycle having a pump that pressurizes a heat medium and a heat medium heat exchanger that heats or cools a temperature-controlled object with the heat medium, and circulates the heat medium in a heat medium circuit. a first refrigerant flow path through which the first refrigerant compressed by the first compressor flows, a second refrigerant flow path through which the second refrigerant expanded by the second expansion valve flows, and a heat medium flow path through which the heat medium that has passed through the heat medium heat exchanger flows, and an integrated heat exchanger that performs heat exchange between the first refrigerant and the second refrigerant, heat exchange between the first refrigerant and the heat medium, and heat exchange between the second refrigerant and the heat medium.

2. The temperature control system according to claim 1, wherein the integrated heat exchanger has a second heat exchange rate between the second refrigerant and the heat medium that is greater than a first heat exchange rate between the first refrigerant and the heat medium.

3. A temperature control system according to claim 2, wherein the second heat exchange amount is 1.1 times or more the first heat exchange amount.

4. The temperature control system according to claim 2 or 3, wherein the integrated heat exchanger is a plate-type heat exchanger having a plurality of plates stacked in a stacking direction, with the first refrigerant flow path, the second refrigerant flow path, and the heat medium flow path formed between the plurality of plates, and wherein a second area of ​​the plate separating the second refrigerant flow path and the heat medium flow path is larger than a first area of ​​the plate separating the first refrigerant flow path and the heat medium flow path.

5. A temperature control system as described in claim 4, wherein the first refrigerant flow path extends between the plates in the longitudinal direction of the plates on one side in the stacking direction, the heat medium flow path extends between the plates in the longitudinal direction on the other side in the stacking direction, and the second refrigerant flow path extends between the plates in the longitudinal direction across the one side and the other side in the stacking direction.

6. A temperature control system as described in claim 4, wherein the first refrigerant flow path extends in the longitudinal direction of the plates between the plates on one side in the longitudinal direction of the plates, the heat medium flow path extends in the longitudinal direction between the plates on the other side in the longitudinal direction, and the second refrigerant flow path extends in the longitudinal direction between the plates across the one side and the other side in the longitudinal direction.

7. The temperature control system according to claim 1, wherein the integrated heat exchanger has a first heat exchange amount between the first refrigerant and the heat medium that is greater than a second heat exchange amount between the second refrigerant and the heat medium.

8. A temperature control system according to claim 7, wherein the first heat exchange amount is 1.1 times or more the second heat exchange amount.

9. The temperature control system according to claim 7 or 8, wherein the integrated heat exchanger is a plate-type heat exchanger having a plurality of plates stacked in a stacking direction, with the first refrigerant flow path, the second refrigerant flow path, and the heat medium flow path formed between the plurality of plates, and wherein a first area of ​​the plate separating the first refrigerant flow path and the heat medium flow path is larger than a second area of ​​the plate separating the second refrigerant flow path and the heat medium flow path.

10. A temperature control system as described in claim 9, wherein the second refrigerant flow path extends between the plates in the longitudinal direction of the plates on one side in the stacking direction, the heat medium flow path extends between the plates in the longitudinal direction on the other side in the stacking direction, and the first refrigerant flow path extends between the plates in the longitudinal direction across the one side and the other side in the stacking direction.

11. A temperature control system as described in claim 9, wherein the second refrigerant flow path extends in the longitudinal direction of the plates between the plates on one side in the longitudinal direction of the plates, the heat medium flow path extends in the longitudinal direction between the plates on the other side in the longitudinal direction, and the first refrigerant flow path extends in the longitudinal direction between the plates across the one side and the other side in the stacking direction.

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