Manifold

Abstract

The invention relates to a manifold. The manifold is provided with a flow path housing having a first flow path through which a first cooling fluid flows and a second flow path through which a second cooling fluid flows, and in the flow path housing, heat exchange is performed between the first cooling fluid flowing in the first flow path and the second cooling fluid flowing in the second flow path.

Description

Technical Field

[0001] The present invention relates to manifolds. Background Art

[0002] In recent years, automobiles equipped with motors (hybrid electric vehicles (HEV: Hybrid Electric Vehicle), plug-in hybrid electric vehicles (PHEV: Plug-in Hybrid Electric Vehicle), battery vehicles (BEV: Battery Electric Vehicle), fuel cell vehicles (FCEV: Fuel Cell Electric Vehicle), etc.) have become popular as driving sources. The above-mentioned automobiles (hereinafter collectively referred to as "electric vehicles") are equipped with batteries for driving motors. In electric vehicles, there are many devices that need to be cooled, such as motors (including internal combustion engines such as engines), batteries, air conditioners, ECUs, etc., so a cooling circuit that circulates cooling water and refrigerant is constructed to cool them. However, the above-mentioned devices are often suitable for different operating temperatures. In such a case, in order to change the temperature of the circulating cooling water and refrigerant in units of devices with different operating temperatures, heat exchange is performed through heat exchangers such as coolers and water-cooled condensers, and the temperature of the cooling water and refrigerant is controlled.

[0003] The heat exchange system disclosed in Patent Document 1 includes a heat pump cycle, a high-temperature water circuit, and a low-temperature water circuit. In addition, heat exchange is performed between the heat pump cycle and the high-temperature water circuit via a water-cooled condenser, and heat exchange is performed between the heat pump cycle and the low-temperature water circuit via a cooler and an internal heat exchanger.

[0004] In addition, the heat exchange system disclosed in Patent Document 2 is provided with a heat pump cycle. The heat pump cycle is composed of auxiliary equipment such as a compressor (in Patent Document 2, a compressor), an indoor radiator, an electric expansion valve, a first heat exchanger, a solenoid valve, an evaporator (in Patent Document 2, an evaporator), and a pressure accumulator. The heat pump cycle is a heat cycle used for heating or cooling the interior of a vehicle.

[0005] Furthermore, Patent Document 3 describes a vehicle air conditioning device that cools a battery that supplies power to an electric motor for driving a vehicle. The refrigerant circuit in the vehicle air conditioning device includes a heat absorber, a radiator, a compressor, an expansion valve, an outdoor heat exchanger, and an internal heat exchanger, which are connected by piping. In addition, the internal heat exchanger is configured to perform heat exchange between the refrigerant flowing into the heat absorber and the refrigerant flowing out of the heat absorber.

[0006] Patent Document 1: Japanese Patent Application Publication No. 2020-192965

[0007] Patent Document 2: Japanese Patent Application Publication No. 2013-139251

[0008] Patent Document 3: Japanese Patent Application Publication No. 2020-11615

[0009] In the heat exchange system disclosed in Patent Document 1, the locations for heat exchange are limited to the water-cooled condenser, the cooler, and the internal heat exchanger (hereinafter collectively referred to as the "heat exchanger"). Therefore, in order to improve the performance (efficiency) of heat exchange, a large-sized heat exchanger needs to be used. Therefore, the limited space of the engine room of the vehicle is occupied. In addition, there is a concern that the desired cooling performance cannot be obtained if the size of the heat exchanger is reduced.

[0010] In addition, in the heat exchange system disclosed in Patent Document 2, auxiliary devices such as a compressor, an indoor radiator, an electric expansion valve, a first heat exchanger, a solenoid valve, an evaporator, and a pressure accumulator are configured as independent devices. The auxiliary devices are usually fixed to the vehicle body by bolts, etc. Therefore, since the heat exchange system occupies a limited space in the engine room of the vehicle, there is room for improvement.

[0011] Furthermore, when mounted on a vehicle, miniaturization is desired from the perspective of piping wiring and weight reduction. In the vehicle air conditioning device described in Patent Document 3, as described above, each part of the refrigerant circuit is connected by piping, so a portion for connecting the piping is required, and the refrigerant circuit becomes larger. In addition, since an internal heat exchanger is provided, the refrigerant circuit is larger, and there is room for improvement in miniaturization. Summary of the invention

[0012] Therefore, a manifold capable of miniaturizing the heat exchange system is desired.

[0013] The characteristic structure of the manifold of the present invention is the following aspect, that is, it is equipped with a flow path shell, which has: a first flow path for flowing a first cooling fluid, and a second flow path for flowing a second cooling fluid, in which heat exchange is performed between the first cooling fluid flowing in the first flow path and the second cooling fluid flowing in the second flow path.

[0014] According to such a characteristic structure, by performing heat exchange between the first cooling fluid flowing in the first flow path of the flow path shell provided in the manifold and the second cooling fluid flowing in the second flow path, sufficient cooling performance can be obtained even with a small heat exchanger. In addition, heat exchange can be performed in the flow path shell, so the manifold can be miniaturized compared to the case where the heat exchanger is externally placed in the flow path shell. Moreover, the first cooling fluid flowing in the first flow path and the second cooling fluid flowing in the second flow path can be cooled and heated in the flow path shell. By performing heat exchange between fluids in the flow path shell, for example, the coefficient of performance of a compressor or an expansion valve can be improved. Therefore, the internal heat exchanger for cooling and heating the fluid can be miniaturized, or heat exchange can be performed without additional settings, so the manifold can be miniaturized. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a circuit configuration diagram of a cooling system having a manifold according to the first embodiment.

[0016] Figure 2 It is a simplified diagram of the structure of the manifold.

[0017] Figure 3 It is a diagram showing the relationship between the first internal refrigerant path and the eighth internal flow path and other flow paths according to the first embodiment.

[0018] Figure 4 It is a diagram showing a flow path structure of a manifold according to a second embodiment.

[0019] Figure 5 It is a diagram showing a flow path structure of a manifold according to a modified example of the second embodiment.

[0020] Figure 6 It is a diagram showing a flow path structure of a manifold according to another modified example of the second embodiment.

[0021] Figure 7 It is a cross-sectional view showing a method of fixing the cooler to the flow path casing according to the third embodiment.

[0022] Figure 8 It is a schematic diagram showing the structure of a manifold according to a fourth embodiment.

[0023] Fig. 9 It is a cross-sectional view showing the structure of a cooler in a flow channel casing according to a fourth embodiment.

[0024] Fig.10 It is a circuit configuration diagram of a cooling system having a manifold according to a fifth embodiment.

[0025] Fig.11 It is a schematic diagram showing the structure of a manifold according to a fifth embodiment.

[0026] Fig.12 It is a diagram showing the relationship between the second refrigerant flow path and the fourth refrigerant flow path and other flow paths according to the fifth embodiment.

[0027] Fig.13 It is a Mollier diagram that represents the thermal cycle.

[0028] Fig.14 It is a diagram showing a high-temperature flow path and a low-temperature flow path according to another embodiment.

[0029] Fig.15 It is a diagram showing a high-temperature flow path and a low-temperature flow path according to another embodiment.

[0030] Fig.16 It is a diagram showing a high-temperature flow path and a low-temperature flow path according to another embodiment. DETAILED DESCRIPTION

[0031] Hereinafter, the embodiment of the manifold of the present invention will be described in detail using the accompanying drawings. In addition, the embodiment described below is an example for explaining the present invention, and does not limit the present invention to the above-mentioned embodiment. Therefore, the present invention can be implemented in various forms as long as it does not deviate from the purpose.

[0032] [First embodiment]

[0033] 〔Cooling system structure〕

[0034] like Figure 1 As shown, the cooling system A including the manifold 100 of the present embodiment is roughly composed of a cooling water circuit B and a refrigerant circuit C. Cooling water (an example of a second cooling fluid, a cooling fluid) such as an antifreeze solution or a long-life coolant containing ethylene glycol as a main component flows in the cooling water circuit B, and a refrigerant (an example of a first cooling fluid) such as a hydrofluorocarbon (HFC) flows in the refrigerant circuit C. Figure 1 In the figure, the portion surrounded by the dotted line is the manifold 100 of the present embodiment. The manifold 100 has a flow path housing 105, and auxiliary equipment, which includes a cooler 110 (an example of an evaporator), a water-cooled condenser 120 (an example of a condenser), a first electric pump 4, a rotary valve 5 composed of a four-way valve, a second electric pump 7, a switching valve 10 composed of a three-way valve, a third electric pump 11, a first expansion valve 23, and a second expansion valve 26. Figure 1 In the figure, although the auxiliary equipment is depicted as being located inside the flow path housing 105, Figure 2 As shown, it is actually installed on the outer surface of the flow path housing 105. Figure 2 A simplified diagram of the structure of the manifold 100 is shown in FIG. Figure 2In the description of auxiliary equipment (such as pumps and valves) other than the cooler 110 and the water-cooled condenser 120, the description is omitted. In the present embodiment, the flow path housing 105 is formed of a metal material with high thermal conductivity including aluminum, and the flow paths constituting the cooling water circuit B and the refrigerant circuit C are formed by directly opening holes in the flow path housing 105. In addition, in the present embodiment, as an example of a coolant, although cooling water such as antifreeze liquid and long-acting coolant with ethylene glycol as the main component is used, it may also be a coolant composed of insulating oil such as paraffin-based. In addition, the refrigerant may also be a refrigerant such as hydrofluoroolefin (HFO). These are the same in all the embodiments described below.

[0035] First, the cooling water circuit B is described. Figure 1 The flow path on the right side of the cooler 110 and the water-cooled condenser 120 in the cooling water circuit B. The cooling water circuit B has a first external flow path 31 outside the flow path housing 105. The first external flow path 31 is connected to a first internal flow path 41 (an example of a second flow path, a cooling flow path) and a second internal flow path 42 (an example of a second flow path, a cooling flow path) formed inside the flow path housing 105. A radiator 1 is arranged in the middle of the first external flow path 31. The cooling water flows in the order of the second internal flow path 42, the first external flow path 31, the radiator 1, the first external flow path 31, and the first internal flow path 41. Hereinafter, the upstream side and the downstream side relative to the flow direction of the cooling water in the cooling water circuit B are also referred to as the upstream side and the downstream side.

[0036] The second external flow path 32 and the third external flow path 33 are branched from the first external flow path 31 on the downstream side of the radiator 1 and the upstream side of the first internal flow path 41. The second external flow path 32 is connected to the third internal flow path 43 formed inside the flow path housing 105 on the downstream side. The third internal flow path 43 is connected to the second internal flow path 42 on the downstream side. The cooling water branched from the first external flow path 31 to the second external flow path 32 flows in the second external flow path 32, cools the charger 2 and the DC-DC converter 3, and flows into the third internal flow path 43. The cooling water is pressurized by the first electric pump 4 in the third internal flow path 43 and then flows into the second internal flow path 42.

[0037] The fourth internal flow path 44 branches off from the third internal flow path 43 on the upstream side of the first electric pump 4 in the third internal flow path 43. Figure 1 In the state of the fourth internal flow path 44, the fifth internal flow path 45 is connected via the rotary valve 5. The downstream side of the fifth internal flow path 45 is connected to the second internal flow path 42.

[0038] The third external flow path 33 is connected to the sixth internal flow path 46 formed inside the flow path housing 105 on the downstream side. The sixth internal flow path 46 is connected to the seventh internal flow path 47 via the rotary valve 5. The second electric pump 7 is arranged in the middle of the seventh internal flow path 47. The cooling water branched from the first external flow path 31 to the third external flow path 33 flows in the third external flow path 33, cools the electric shaft inverter 6, and flows into the sixth internal flow path 46. Figure 1 In the state, the cooling water is pressurized by the second electric pump 7 in the seventh internal flow path 47 through the rotary valve 5, and then flows out to the outside of the flow path housing 105. The electric shaft inverter 6 is a unit that accommodates the rotary motor, the speed reducer, and the differential gear mechanism in the housing, and the inverter is provided integrally with the unit. In addition, by rotating the rotary valve 5, the fourth internal flow path 44 and the sixth internal flow path 46 can be connected, and the fifth internal flow path 45 and the seventh internal flow path 47 can be connected.

[0039] The seventh internal flow path 47 is connected to the fourth external flow path 34 outside the flow path housing 105. The fourth external flow path 34 is connected to the eighth internal flow path 48 (an example of a second flow path, a cooling flow path) formed inside the flow path housing 105 on the downstream side. The cooling water flowing out of the seventh internal flow path 47 flows in the fourth external flow path 34, is cooled by the first heater core 8, and then is heated by cooling the battery 9, and flows into the eighth internal flow path 48. The eighth internal flow path 48 is connected to the cooler 110 on the downstream side. The downstream side of the cooler 110 is connected to the second internal flow path 42. The cooling water flowing in the eighth internal flow path 48 flows into the cooler 110, and after the heat is taken away by the mist-like refrigerant flowing from the third internal refrigerant path 73 (an example of a first flow path, a refrigerant flow path) described later in the cooler 110 and is cooled, it flows in the second internal flow path 42. The cooling water flowing through the second internal flow path 42 flows into the first external flow path 31 connected to the outside of the flow path case 105 .

[0040] The first internal flow path 41 connected to the first external flow path 31 is connected to the water-cooled condenser 120 on the downstream side. In addition, the switching valve 10 and the third electric pump 11 are sequentially arranged in the middle of the first internal flow path 41. The downstream side of the water-cooled condenser 120 is connected to the ninth internal flow path 49 (an example of a second flow path, a cooling flow path). The cooling water flowing into the first internal flow path 41 is pressurized by the third electric pump 11 and flows into the water-cooled condenser 120. After the refrigerant in the state of high-temperature compressed gas flowing from the second internal refrigerant path 72 (an example of a first flow path, a refrigerant flow path) described later in the water-cooled condenser 120 takes away heat and is heated, it flows in the ninth internal flow path 49 and flows out to the outside of the flow path shell 105.

[0041] The ninth internal flow path 49 is connected to the fifth external flow path 35 outside the flow path housing 105. The fifth external flow path 35 is connected to the tenth internal flow path 50 formed inside the flow path housing 105 on the downstream side. The tenth internal flow path 50 is connected to the sixth internal flow path 46 on the downstream side. The cooling water flowing out of the ninth internal flow path 49 flows in the fifth external flow path 35, is cooled by the second heater core 12, and flows into the tenth internal flow path 50. The cooling water flowing in the tenth internal flow path 50 flows into the sixth internal flow path 46.

[0042] The switching valve 10 disposed in the first internal flow path 41 switches the flow direction of the cooling water between the first internal flow path 41 and the eleventh internal flow path 51 formed inside the flow path housing 105. The eleventh internal flow path 51 is connected to the tenth internal flow path 50 on the downstream side. When the switching valve 10 is switched so that the cooling water flows in the eleventh internal flow path 51, the cooling water flows from the first internal flow path 41 to the eleventh internal flow path 51 and flows into the tenth internal flow path 50, and then flows into the sixth internal flow path 46.

[0043] Next, the refrigerant circuit C will be described. The refrigerant circuit C is Figure 1 The refrigerant circuit C is formed inside the flow path shell 105, through which the refrigerant flows. With respect to the cooler 110, there is a first internal refrigerant path 71 (an example of a first flow path, a refrigerant flow path) on the downstream side of the flow direction of the refrigerant (hereinafter, the upstream side and the downstream side of the refrigerant circuit C relative to the flow direction of the refrigerant are referred to as the upstream side and the downstream side). The first internal refrigerant path 71 is connected to the first external refrigerant path 61 formed outside the flow path shell 105. The accumulator 21 and the compressor 22 are sequentially arranged in the middle of the first external refrigerant path 61. The first external refrigerant path 61 is connected to the second internal refrigerant path 72 formed inside the flow path shell 105 on the downstream side. The second internal refrigerant path 72 is connected to the water-cooled condenser 120 on the downstream side. The downstream side of the water-cooled condenser 120 is connected to the third internal refrigerant path 73 formed inside the flow path shell 105. The third internal refrigerant path 73 is connected to the cooler 110 via the first expansion valve 23 disposed midway. That is, in the flow path housing 105, the water-cooled condenser 120 is installed at a position on the upstream side relative to the flow direction of the refrigerant in the third internal refrigerant path 73, and the cooler 110 is installed at a position on the downstream side relative to the flow direction of the refrigerant.

[0044] The fourth internal refrigerant path 74 branches from the third internal refrigerant path 73 on the upstream side of the first expansion valve 23 in the third internal refrigerant path 73. The second expansion valve 26 is arranged in the middle of the fourth internal refrigerant path 74. The fourth internal refrigerant path 74 is connected to the second external refrigerant path 62 formed outside the flow path housing 105. The evaporator 24 and the check valve 25 are arranged in sequence in the middle of the second external refrigerant path 62. The second external refrigerant path 62 is connected to the fifth internal refrigerant path 75 formed inside the flow path housing 105. The fifth internal refrigerant path 75 is connected to the first internal refrigerant path 71 on the downstream side.

[0045] Next, the flow of the refrigerant in the refrigerant circuit C is described. The refrigerant that flows in the first external refrigerant path 61 and becomes a high-temperature compressed gas by the compressor 22 flows in the first external refrigerant path 61 and flows into the water-cooled condenser 120 from the second internal refrigerant path 72. In the water-cooled condenser 120, the refrigerant is deprived of heat by the cooling water flowing in from the first internal flow path 41, thereby being condensed and liquefied. Among the liquefied refrigerants, the refrigerant used for cooling the interior of the vehicle flows out of the water-cooled condenser 120 and flows through the third internal refrigerant path 73 through the fourth internal refrigerant path 74. After being expanded in the second expansion valve 26 and becoming a mist of low temperature and low pressure, it flows out of the flow path housing 105, flows in the second external refrigerant path 62, and is transported to the evaporator 24. The mist refrigerant is deprived of heat by the air introduced from the outside in the evaporator 24 and evaporates. On the contrary, the air is cooled by the heat being deprived by the refrigerant, and becomes cold air and is transported into the vehicle. The evaporated and gasified refrigerant passes through the check valve 25 disposed in the second external refrigerant path 62 and flows into the fifth internal refrigerant path 75, and flows out from the first internal refrigerant path 71 to the outside of the flow path housing 105. In addition, the gasified refrigerant flows in the first external refrigerant path 61 and is transported to the accumulator 21. In the accumulator 21, when the gasified refrigerant contains liquid, the liquid is separated from the gasified refrigerant. Then, the gasified refrigerant flows in the first external refrigerant path 61 and flows back to the compressor 22, and is compressed again to become a high-temperature compressed gas.

[0046] The refrigerant that is not used for cooling the vehicle interior among the refrigerant liquefied by the water-cooled condenser 120 flows out of the water-cooled condenser 120 and flows in the third internal refrigerant path 73. After being expanded in the first expansion valve 23 and becoming a mist of low temperature and low pressure, it is transported to the cooler 110. In the cooler 110, the mist refrigerant is deprived of heat by the cooling water flowing in from the eighth internal flow path 48 and evaporates. The evaporated and gasified refrigerant flows out of the flow path housing 105 from the first internal refrigerant path 71. In addition, the gasified refrigerant flows in the first external refrigerant path 61 and is transported to the accumulator 21. Since the second external refrigerant path 62 has a check valve 25, the refrigerant does not flow into the evaporator 24. In the accumulator 21, when the gasified refrigerant contains liquid, the liquid refrigerant is separated. Then, the gasified refrigerant flows in the first external refrigerant path 61 and flows back to the compressor 22, and is compressed again to become a high-temperature compressed gas.

[0047] Normally, heat exchange between cooling water and refrigerant is performed only in the cooler 110 and the water-cooled condenser 120 which serve as heat exchangers. However, in the present embodiment, by bringing the flow path of the cooling water circuit B and the flow path of the refrigerant circuit C close to each other, heat exchange is performed not only in the cooler 110 and the water-cooled condenser 120 but also between the flow paths.

[0048] Specifically, if Figure 2As shown, the flow path connected to the cooler 110 is arranged in the flow path housing 105 so that the eighth internal flow path 48 of the cooling water circuit B flowing into the cooler 110 and the first internal refrigerant path 71 of the refrigerant circuit C flowing out of the cooler 110 are arranged in parallel and close to each other, and the second internal flow path 42 of the cooling water circuit B flowing out of the cooler 110 and the third internal refrigerant path 73 of the refrigerant circuit C flowing into the cooler 110 are arranged in parallel and close to each other. At this time, the flow direction of the cooling water flowing in the eighth internal flow path 48 is opposite to the flow direction of the refrigerant flowing in the first internal refrigerant path 71, and the flow direction of the cooling water flowing in the second internal flow path 42 is opposite to the flow direction of the refrigerant flowing in the third internal refrigerant path 73. In addition, in the flow path housing 105, the eighth internal flow path 48 and the first internal refrigerant path 71 perform heat exchange at a position formed in an L shape, and the second internal flow path 42 and the third internal refrigerant path 73 perform heat exchange at a position formed in a straight line. With such a configuration, heat exchange is performed not only in the cooler 110 but also between the cooling water flowing in the eighth internal flow path 48 and the refrigerant flowing in the first internal refrigerant path 71, and heat exchange is performed between the cooling water flowing in the second internal flow path 42 and the refrigerant flowing in the third internal refrigerant path 73. In this way, since heat exchange is also performed between the internal flow path and the internal refrigerant path outside the cooler 110, even if a small cooler is used as the cooler 110, a required sufficient cooling performance can be obtained.

[0049] In addition, specifically, Figure 2As shown, the flow path connected to the water-cooled condenser 120 is arranged in the flow path housing 105 so that the first internal flow path 41 of the cooling water circuit B flowing into the water-cooled condenser 120 and the third internal refrigerant path 73 of the refrigerant circuit C flowing out of the water-cooled condenser 120 are arranged in parallel and close to each other, and the ninth internal flow path 49 of the cooling water circuit B flowing out of the water-cooled condenser 120 and the second internal refrigerant path 72 of the refrigerant circuit C flowing into the water-cooled condenser 120 are arranged in parallel and close to each other. At this time, the flow direction of the cooling water flowing in the first internal flow path 41 is opposite to the flow direction of the refrigerant flowing in the third internal refrigerant path 73, and the flow direction of the cooling water flowing in the ninth internal flow path 49 is opposite to the flow direction of the refrigerant flowing in the second internal refrigerant path 72. In addition, in the flow path housing 105, the first internal flow path 41 and the third internal refrigerant path 73 perform heat exchange at a position formed in a straight line, and the ninth internal flow path 49 and the second internal refrigerant path 72 perform heat exchange at a position formed in an L shape. With such a configuration, heat exchange is performed not only between the cooling water flowing in the first internal flow path 41 and the refrigerant flowing in the third internal refrigerant path 73 in the water-cooled condenser 120, but also between the cooling water flowing in the ninth internal flow path 49 and the refrigerant flowing in the second internal refrigerant path 72. In this way, since heat exchange is performed between the internal flow path outside the water-cooled condenser 120 and the internal refrigerant path, even if a small condenser is used as the water-cooled condenser 120, sufficient cooling performance can be obtained.

[0050] Figure 3 4 is a diagram showing the relationship between the first internal refrigerant path 71 and the eighth internal flow path 48 of the present embodiment and other flow paths. Figure 3As shown, the first internal refrigerant path 71 through which the refrigerant flows out of the cooler 110 and the eighth internal flow path 48 through which the cooling water flows into the cooler 110 are arranged at a shorter interval than the intervals between other flow paths arranged in the flow path housing 105. The first internal refrigerant path 71 is a refrigerant flow path through which the refrigerant flows from the cooler 110 to the accumulator 21. The eighth internal flow path 48 is a cooling flow path through which the cooling water flows from the battery 9 to the cooler 110. Other flow paths arranged in the flow path housing 105 are the first internal flow path 41 through which the cooling water flows into the water-cooled condenser 120, the ninth internal flow path 49 through which the cooling water flows out of the water-cooled condenser 120, the third internal refrigerant path 73 through which the refrigerant flows out of the water-cooled condenser 120, and the second internal refrigerant path 72 through which the refrigerant flows into the water-cooled condenser 120. Therefore, the first internal refrigerant path 71 and the eighth internal flow path 48 are provided at a distance shorter than the distance between the first internal flow path 41 and the third internal refrigerant path 73 and the distance between the ninth internal flow path 49 and the second internal refrigerant path 72. That is, the eighth internal flow path 48 is formed closer to the first internal refrigerant path 71 than the first internal flow path 41, the second internal flow path 42 and the ninth internal flow path 49.

[0051] In addition, it is preferred that the ninth internal flow path 49 is formed near the water-cooled condenser 120 so as to be closer to the second internal refrigerant path 72 than the first internal flow path 41, the second internal flow path 42, and the eighth internal flow path 48, and the first internal flow path 41 is formed near the third internal refrigerant path 73 than the second internal flow path 42, the eighth internal flow path 48, and the ninth internal flow path 49. Furthermore, it is preferred that the second internal flow path 42 is formed near the cooler 110 so as to be closer to the third internal refrigerant path 73 than the first internal flow path 41, the eighth internal flow path 48, and the ninth internal flow path 49.

[0052] [Second embodiment]

[0053] Next, the manifold 100 of the second embodiment is described. In this embodiment, the shapes of the eighth internal flow path 48 and the first internal refrigerant path 71, the second internal flow path 42 and the third internal refrigerant path 73, the first internal flow path 41 and the third internal refrigerant path 73, and the ninth internal flow path 49 and the second internal refrigerant path 72 arranged in parallel and close to each other in the flow path housing 105 are different from those of the first embodiment. The other structures are the same as those of the first embodiment, so detailed descriptions of the same structures are omitted. Hereinafter, the eighth internal flow path 48, the portion of the second internal flow path 42 arranged in parallel and close to the third internal refrigerant path 73, the portion of the first internal flow path 41 arranged in parallel and close to the third internal refrigerant path 73, and the ninth internal flow path 49 are collectively referred to as parallel internal flow paths 81. In addition, the first internal refrigerant path 71, the portion of the third internal refrigerant path 73 arranged in parallel and close to the second internal flow path 42 and the first internal flow path 41, and the second internal refrigerant path 72 are collectively referred to as parallel internal refrigerant paths 82.

[0054] like Figure 4 As shown, in the present embodiment, a plurality of closed internal flow paths 83 (an example of a second flow path) are branched from the parallel internal flow path 81 in a direction perpendicular to the direction in which the flow path extends and protrudes. In addition, a plurality of closed internal refrigerant paths 84 (an example of a first flow path) are branched from the parallel internal refrigerant path 82 in a direction perpendicular to the direction in which the flow path extends and protrudes. The front end of the closed internal flow path 83 is closed, and extends and protrudes in a direction close to the parallel internal refrigerant path 82. In addition, the front end of the closed internal refrigerant path 84 is closed, and extends and protrudes in a direction close to the parallel internal flow path 81. The closed internal flow path 83 and the closed internal refrigerant path 84 are arranged in parallel and close to each other. In addition, the closed internal flow path 83 and the closed internal refrigerant path 84 both have the same cross-sectional shape as the parallel internal flow path 81 and the parallel internal refrigerant path 82, and the flow path cross-sectional area is also equal. The flow direction of the cooling water flowing in the parallel internal flow path 81 is opposite to the flow direction of the refrigerant flowing in the parallel internal refrigerant path 82.

[0055] Since the manifold 100 has such a structure, the heat exchange between the cooling water and the refrigerant can be performed not only between the parallel internal flow path 81 and the parallel internal refrigerant path 82, but also between the closed internal flow path 83 and the closed internal refrigerant path 84. As a result, even if the interval between the parallel internal flow path 81 and the parallel internal refrigerant path 82 is the same as that of the manifold 100 of the first embodiment, a condenser smaller than that of the first embodiment can be used as the water-cooled condenser 120 to obtain the required sufficient cooling performance. In addition, the closed internal flow path 83 and the closed internal refrigerant path 84 may not be multiple but one (the same applies to the following modified examples).

[0056] In the case where it is difficult to directly open a hole in the flow path housing 105 to form the closed internal flow path 83 and the closed internal refrigerant path 84, it is also possible to set a structure in which two shells (not shown) are joined to form the flow path housing 105. In this case, grooves constituting the parallel internal flow paths 81, the parallel internal refrigerant paths 82, the closed internal flow paths 83, and the closed internal refrigerant paths 84 are formed on each of the joint surfaces of the two shells, and then the two shells are joined, thereby forming the parallel internal flow paths 81, the parallel internal refrigerant paths 82, the closed internal flow paths 83, and the closed internal refrigerant paths 84 in the flow path housing 105.

[0057] [Modification of the Second Embodiment]

[0058] Next, a manifold 100 of a modification of the second embodiment is described. In this modification, the closed internal flow path 83 and the closed internal refrigerant path 84 are different from the second embodiment. The other structures are the same as the second embodiment, so detailed description of the same structures is omitted.

[0059] In this variation, if Figure 5 As shown, the closed internal flow path 83 is not perpendicular to the extending direction of the parallel internal flow path 81, but extends in the direction of a branch angle θ (an example of an acute angle) that is acute to the flow direction of the cooling water. In addition, the closed internal refrigerant path 84 is not perpendicular to the extending direction of the parallel internal refrigerant path 82, but extends in the direction of a branch angle θ that is acute to the flow direction of the refrigerant.

[0060] The closed internal flow path 83 branches at a branch angle θ in an acute angle direction relative to the flow direction of the cooling water of the parallel internal flow path 81, and the closed internal refrigerant path 84 branches at a branch angle θ in an acute angle direction relative to the flow direction of the refrigerant of the parallel internal refrigerant path 82, so the closed internal flow path 83 and the closed internal refrigerant path 84 are arranged in parallel and close to each other. By configuring in this way, even if the interval between the parallel internal flow path 81 and the parallel internal refrigerant path 82 is the same as that in the second embodiment, the length of the closed internal flow path 83 and the closed internal refrigerant path 84 can be made longer than that in the second embodiment. As a result, the heat exchange between the closed internal flow path 83 and the closed internal refrigerant path 84 can be performed more efficiently than in the second embodiment, so even if a smaller condenser is used as the water-cooled condenser 120, the required sufficient cooling performance can be obtained. In addition, since the closed internal flow path 83 and the closed internal refrigerant path 84 branch at an acute angle relative to the flow direction of the cooling water and the refrigerant, the pressure loss of the cooling water and the refrigerant when they flow into the closed internal flow path 83 and the closed internal refrigerant path 84 can be limited to a minimum.

[0061] [Other Modifications of the Second Embodiment]

[0062] Next, a manifold 100 of another modified example of the second embodiment is described. In this modified example, the closed internal flow path 83 and the closed internal refrigerant path 84 are different from those of the second embodiment and its modified examples. The other structures are the same as those of the second embodiment, so detailed description of the same structures is omitted.

[0063] like Figure 6 As shown, in this variant, the closed internal flow path 83 and the closed internal refrigerant path 84 both have a right triangle shape in a top view, and are composed of the hypotenuse of the right triangle and its adjacent side. The other adjacent side is a part of the parallel internal flow path 81. The position of the closed internal flow path 83 corresponding to the hypotenuse of the right triangle extends in the direction of the branch angle θ that is acute to the flow direction of the cooling water, and the position corresponding to the adjacent side is perpendicular to the flow direction of the cooling water. In addition, the position of the closed internal refrigerant path 84 corresponding to the hypotenuse of the right triangle extends in the direction of the branch angle θ that is acute to the flow direction of the refrigerant, and the position corresponding to the adjacent side is perpendicular to the flow direction of the refrigerant. That is, in this variant, the positions of the closed internal flow path 83 and the closed internal refrigerant path 84 corresponding to the hypotenuse and the positions corresponding to the adjacent sides are arranged parallel and close to each other.

[0064] The position of the hypotenuse corresponding to the closed internal flow path 83 branches at a branch angle θ in an acute angle direction relative to the flow direction of the cooling water in the parallel internal flow path 81, and the position of the hypotenuse corresponding to the closed internal refrigerant path 84 branches at a branch angle θ in an acute angle direction relative to the flow direction of the refrigerant in the parallel internal refrigerant path 82, so the positions of the hypotenuse corresponding to the closed internal flow path 83 and the closed internal refrigerant path 84 and the positions corresponding to the adjacent sides are arranged parallel and close to each other. By configuring the closed internal flow path 83 and the closed internal refrigerant path 84 in this way, even if the interval between the parallel internal flow path 81 and the parallel internal refrigerant path 82 is the same as that in the second embodiment, the length of the closed internal flow path 83 and the closed internal refrigerant path 84 (the sum of the length of the hypotenuse and the length of the adjacent side in the top view) can be made longer than that in the second embodiment. As a result, the heat exchange between the closed internal flow path 83 and the closed internal refrigerant path 84 can be performed more efficiently than in the second embodiment, so as to obtain the required sufficient cooling performance even if a smaller condenser is used as the water-cooled condenser 120. In addition, the positions of the oblique sides corresponding to the closed internal flow path 83 and the closed internal refrigerant path 84 are branched in an acute angle direction relative to the flow direction of the cooling water and the refrigerant, and the positions of the adjacent sides corresponding to the closed internal flow path 83 and the closed internal refrigerant path 84 are branched in a vertical direction relative to the flow direction of the cooling water and the refrigerant, so that the pressure loss of the cooling water and the refrigerant when the cooling water and the refrigerant flow into and out of the closed internal flow path 83 and the closed internal refrigerant path 84 can be limited to a minimum.

[0065] [Another embodiment of the first embodiment and the second embodiment]

[0066] In the first and second embodiments, the cooling water and the refrigerant for heat exchange flow in opposite directions in the flow channel housing 105, but the flow directions may be the same. In this case, the cooler 110 may be arranged on the upstream side, and the water-cooled condenser 120 may be arranged on the downstream side.

[0067] In the first and second embodiments, the flow path for heat exchange is linear or L-shaped in the flow path housing 105, but it is not limited thereto. By making the flow path for heat exchange as long as possible, the cooler 110 and the water-cooled condenser 120 can be made smaller. In addition, the flow path for heat exchange can also be in a form of heat exchange through a plate member.

[0068] [Third embodiment]

[0069] 〔Cooling system structure〕

[0070] A cooling system A including the manifold 100 of the third embodiment and Figure 1The cooling system A of the first embodiment shown in FIG. 1 is the same. In addition, the schematic structure of the manifold 100 is also the same as that of FIG. Figure 2 same.

[0071] Below, use Figure 2 , Figure 7 The method of fixing the cooler 110 to the flow path housing 105 is described. The cooler 110 is directly connected to the third internal refrigerant path 73, the first internal refrigerant path 71, the eighth internal flow path 48, and the second internal flow path 42, so as to fix the flow path housing 105. The cooler 110 has a refrigerant inlet 111 through which the refrigerant flows in, a refrigerant outlet 112 through which the refrigerant flows out, a cooling water inlet (an example of a "cooling liquid inlet") 113 through which the cooling water flows in, and a cooling water outlet (an example of a "cooling liquid outlet") 114 through which the cooling water flows out. Furthermore, the third internal refrigerant path 73 and the refrigerant inlet 111, the first internal refrigerant path 71 and the refrigerant outlet 112, the eighth internal flow path 48 and the cooling water inlet 113, and the second internal flow path 42 and the cooling water outlet 114 are joined by brazing using a brazing material 116. Brazing has the characteristics of being difficult to produce changes in the shape and material of each shell and having high bonding strength by bonding near the melting temperature of the brazing material 116 which is lower than the melting point of the shell of the flow channel shell 105 and the cooler 110. In addition, bonding is performed by filling the brazing material 116, so the air tightness and liquid tightness of the bonding position are excellent.

[0072] In the past, the cooler was fixed to the flow path housing 105 by bolts, etc., so multiple bolts, pipes connecting the flow path and the heat exchanger, and seals to prevent the leakage of refrigerant and cooling water were required, the number of parts and man-hours for fixing the cooler increased, and the volume of the cooler became larger. However, according to this embodiment, by brazing the flow path and the inlet and outlet of the cooler 110, it is possible to simultaneously achieve the fixation of the cooler 110 to the flow path housing 105 without bolts, etc. (high bonding strength and miniaturization), the connection between the flow path and the cooler 110 (no piping required), and the airtightness and watertightness of the bonding position (no sealing material required). Therefore, by reducing the number of parts and man-hours, a small and low-cost manifold 100 can be achieved.

[0073] The flow path housing 105 of this embodiment is formed by joining an upper housing 105a and a lower housing 105b. Figure 2As shown, the third internal refrigerant path 73, the first internal refrigerant path 71, the eighth internal flow path 48 and the second internal flow path 42 penetrate the upper shell 105a from the boundary surface between the upper shell 105a and the lower shell 105b. After the inlet and outlet of the cooler 110 are positioned at the above-mentioned through flow paths, the brazing material 116 is applied to the respective boundaries of the third internal refrigerant path 73 and the refrigerant inlet 111, the first internal refrigerant path 71 and the refrigerant outlet 112, the eighth internal flow path 48 and the cooling water inlet 113, and the second internal flow path 42 and the cooling water outlet 114. Then, a brazing tool is inserted from the lower surface of the upper shell 105a (the boundary surface with the lower shell 105b) into each of the third internal refrigerant path 73, the first internal refrigerant path 71, the eighth internal flow path 48 and the second internal flow path 42 to perform brazing. At this time, the thinner the thickness of the upper housing 105a is, the easier it is to insert the brazing tool, so brazing can be easily performed.

[0074] [Fourth embodiment]

[0075] Next, use Figure 8 , Fig. 9 A manifold 100 of a fourth embodiment is described. In this embodiment, a cooler 110 is disposed inside a flow path housing 105. Specifically, a flow path having a heat exchange function of the cooler 110 is formed inside the flow path housing 105. The other structures are the same as those of the third embodiment. Therefore, in the description of this embodiment, the same reference numerals are given to the positions of the same structures as those of the third embodiment, and detailed descriptions of the same structures are omitted.

[0076] The flow path shell 105 is formed by joining an upper shell 105a and a lower shell 105b. Furthermore, a heat exchange flow path 117 (an example of a stacked flow path) is formed inside the flow path shell 105 from the upper shell 105a to the lower shell 105b. The heat exchange flow path 117 is formed by alternately stacking a plurality of heat exchange refrigerant flow paths 117a (an example of a stacked flow path) and a plurality of heat exchange cooling water flow paths 117b (an example of a stacked flow path). The plurality of heat exchange cooling water flow paths 117b are respectively connected to the eighth internal flow path 48 and the second internal flow path 42. Fig. 9 , the plurality of heat exchange refrigerant flow paths 117a are depicted as separate flow paths, but are actually connected to the third internal refrigerant path 73 and the first internal refrigerant path 71. A flow path wall 118 separating the heat exchange refrigerant flow path 117a and the heat exchange cooling water flow path 117b is supported by the flow path casing 105.

[0077] In this way, compared with the case where the cooler 110 is provided outside the flow path housing 105 , by arranging the cooler 110 inside the flow path housing 105 , the manifold 100 can be reduced in size.

[0078] [Other embodiments of the third embodiment and the fourth embodiment]

[0079] (1) In the third and fourth embodiments, the cooler 110 is fixed to the flow path housing 105 by brazing, but the present invention is not limited thereto. As long as the bonding strength, air tightness, liquid tightness, etc. of the cooler 110 to the flow path housing 105 can be ensured, any method such as welding may be used instead of brazing for bonding.

[0080] (2) In the third and fourth embodiments described above, the joining and fixing of the cooler 110 to the flow path housing 105 are described. However, the same can be applied to the water-cooled condenser 120 and other heat exchangers.

[0081] [Fifth embodiment]

[0082] Fig.10 1 is a diagram showing a circuit configuration of a cooling system 300 including a manifold 201 according to the present embodiment. Fig.11 This is a diagram showing a schematic configuration of the manifold 201 of the present embodiment. The manifold 201 includes a refrigerant circuit in which a refrigerant such as hydrofluorocarbon (HFC) or hydrofluoroolefin (HFO) flows.

[0083] The manifold 201 is configured with a flow path housing 210. The flow path housing 210 is formed using a metal material such as aluminum containing a material with high thermal conductivity, and has a first refrigerant flow path (an example of a "first flow path") 211, a second refrigerant flow path (an example of a "first flow path") 212, a third refrigerant flow path (an example of a "second flow path") 213, and a fourth refrigerant flow path (an example of a "second flow path") 214 formed by opening holes in such a metal material. An on-off valve (not shown) is provided on the upstream side of the third refrigerant flow path 213 relative to the first expansion valve 235 described later. For example, when the manifold 201 is provided in a vehicle, the on-off valve is opened when indoor cooling is used in the vehicle, and is closed when indoor cooling is not used.

[0084] Here, if Fig.11As shown, the flow path housing 210 is provided with an accumulator 220, a compressor (an example of a "compressor") 225, a water-cooled condenser (an example of a "condenser") 230, a first expansion valve (an example of an "expansion valve") 235, a second expansion valve 240, an evaporator (an example of an "evaporator") 245, a check valve 250, and a cooler (an example of an "evaporator") 255 on the outside. In this embodiment, the water-cooled condenser 230, the evaporator 245, the check valve 250, and the cooler 255 are integrated with the flow path housing 210. In addition, the auxiliary equipment integrated with the flow path housing 210 is arbitrary and is not particularly limited.

[0085] The first refrigerant flow path 211 is a flow path that allows the refrigerant (an example of the "first cooling fluid") to flow between the compressor 225 and the water-cooled condenser 230. The second refrigerant flow path 212 is a flow path that allows the refrigerant (an example of the "first cooling fluid") to flow between the water-cooled condenser 230 and the first expansion valve 235 and / or the second expansion valve 240. The third refrigerant flow path 213 is a flow path that allows the refrigerant (an example of the "second cooling fluid") to flow between the first expansion valve 235 and the evaporator 245 and the second expansion valve 240 and the cooler 255, respectively. The fourth refrigerant flow path 214 is a flow path that allows the refrigerant (an example of the "second cooling fluid") to flow between the evaporator 245 and / or the cooler 255 and the compressor 225.

[0086] The accumulator 220 is a gas-liquid separator that stores liquid refrigerant and performs gas-liquid separation of the refrigerant. The gaseous refrigerant separated by the accumulator 220 flows through the fourth refrigerant flow path 214 and is sent to the compressor 225 .

[0087] The compressor 225 compresses the gaseous refrigerant from the accumulator 220 . As a result, the pressure of the refrigerant increases, and the temperature (referred to as “ T1 ”) becomes higher. The high-temperature and high-pressure gaseous refrigerant is sent to the water-cooled condenser 230 via the first refrigerant flow path 211 .

[0088] The cooling water flows to the water-cooled condenser 230 through the cooling water flow path 231 which is different from the first refrigerant flow path 211 and the second refrigerant flow path 212. The high-temperature and high-pressure gaseous refrigerant sent to the water-cooled condenser 230 has its heat taken away by the cooling water. As a result, the high-temperature and high-pressure gaseous refrigerant is condensed and becomes a medium-temperature and high-pressure liquid refrigerant. That is, the temperature of the refrigerant drops from T1 to T2. The medium-temperature and high-pressure liquid refrigerant is delivered to the first expansion valve 235 and / or the second expansion valve 240 via the second refrigerant flow path 212.

[0089] The first expansion valve 235 is configured so that the flow area is drastically reduced compared to the second refrigerant flow path 212, and only a small amount of refrigerant flows. As a result, the pressure of the refrigerant decreases, and the temperature of the refrigerant decreases with the decrease in pressure, and the gaseous refrigerant is mixed with the liquid refrigerant. The low-temperature and low-pressure refrigerant is transported to the evaporator 245 via the third refrigerant flow path 213. Here, the temperature of the refrigerant drops to T3.

[0090] In the evaporator 245, by taking in the outside air, heat exchange is performed between the outside air and the low-temperature and low-pressure refrigerant. As a result, the refrigerant temperature rises and changes into a gaseous refrigerant, and the outside air is cooled and used for indoor cooling. The medium-temperature and low-pressure gaseous refrigerant is sent to the accumulator 220 via the check valve 250 and the fourth refrigerant flow path 214. The temperature of the refrigerant sent from the evaporator 245 at this time is set to T4. T4 is a temperature higher than T3 and lower than T2.

[0091] A part or all of the refrigerant condensed by the water-cooled condenser 230 is branched from the second refrigerant flow path 212 and delivered to the second expansion valve 240. In the second expansion valve 240, the medium-temperature and high-pressure liquid refrigerant is changed into a low-temperature and low-pressure refrigerant, similar to the first expansion valve 235. The low-temperature and low-pressure refrigerant is delivered to the cooler 255 via the third refrigerant flow path 213.

[0092] The cooling water flows in the cooler 255 through the cooling water flow path 256 which is different from the third refrigerant flow path 213 and the fourth refrigerant flow path 214. The low-temperature and low-pressure refrigerant sent to the cooler 255 cools the cooling water and imparts heat to the cooling water. As a result, the cooling water is changed into a medium-temperature and low-pressure gaseous refrigerant. The refrigerant changed into a gaseous state is transported to the accumulator 220 via the fourth refrigerant flow path 214. The refrigerant sent from the cooler 255 via the fourth refrigerant flow path 214 does not flow to the evaporator 245 due to the check valve 250.

[0093] As described above, the high-temperature and high-pressure refrigerant (refrigerant at temperature T1) is delivered to the first refrigerant flow path 211 from the compressor 225, and the medium-temperature and high-pressure refrigerant (refrigerant at temperature T2) is delivered to the second refrigerant flow path 212 from the water-cooled condenser 230. In addition, the low-temperature and low-pressure refrigerant (refrigerant at temperature T3) is delivered to the third refrigerant flow path 213 from the first expansion valve 235, and the medium-temperature and low-pressure refrigerant (refrigerant at temperature T4) is delivered to the fourth refrigerant flow path 214 from the evaporator 245 and / or the cooler 255. Here, T1>T2>T4>T3. That is, in the present embodiment, the temperature T2 of the refrigerant delivered to the second refrigerant flow path 212 is higher than the temperature T4 of the refrigerant delivered to the fourth refrigerant flow path 214. Therefore, in the branch pipe 201 , the first refrigerant flow path 211 and the second refrigerant flow path 212 correspond to the high-temperature flow path 201H, and the third refrigerant flow path 213 and the fourth refrigerant flow path 214 correspond to the low-temperature flow path 201L.

[0094] In the flow path housing 210, heat exchange is performed between the high temperature flow path 201H and the low temperature flow path 201L. In the present embodiment, heat exchange is performed between the high temperature flow path 201H, i.e., the second refrigerant flow path 212, and the low temperature flow path 201L, i.e., the fourth refrigerant flow path 214. The second refrigerant flow path 212 and the fourth refrigerant flow path 214 are arranged parallel to and close to each other in the flow path housing 210. In the present embodiment, the second refrigerant flow path 212, in which the refrigerant flows from the water-cooled condenser 230 toward the first expansion valve 235 and / or the second expansion valve 240, and the fourth refrigerant flow path 214, in which the refrigerant flows from the evaporator 245 toward the accumulator 220 via the check valve 250, are arranged between X1 and X2 along the X direction and are arranged parallel to each other. In addition, in order to improve the heat exchange efficiency, the interval Y1 in the Y direction orthogonal to the X direction is shortened. The interval Y1 can be set based on the processing accuracy when forming the second refrigerant flow path 212 and the fourth refrigerant flow path 214 by drilling processing (it can be closer). In addition, the refrigerant flow path for heat exchange can be formed by the divided surface of the flow path casing 210.

[0095] Between X1 and X2, the refrigerant flows from X2 toward X1 in the second refrigerant flow path 212, and the refrigerant flows from X1 toward X2 in the fourth refrigerant flow path 214. Therefore, in the present embodiment, the flow directions of the refrigerants in the high-temperature flow path 201H and the low-temperature flow path 201L are opposite to each other. Thus, the refrigerant flowing in the second refrigerant flow path 212 performs heat exchange with the refrigerant flowing in the fourth refrigerant flow path 214, and the refrigerant flowing in the fourth refrigerant flow path 214 performs heat exchange with the refrigerant flowing in the second refrigerant flow path 212. The temperature of the refrigerant flowing in the high-temperature flow path 201H gradually decreases as it flows in the high-temperature flow path 201H in the first direction (from X2 to X1), and the temperature of the refrigerant flowing in the low-temperature flow path 201L gradually increases as it flows in the low-temperature flow path 201L in the second direction (from X1 to X2) opposite to the first direction. That is, the temperature difference between the high temperature flow path 201H and the low temperature flow path 201L in the heat exchange region becomes balanced, so that the heat exchange efficiency can be improved. Therefore, heat exchange can be performed efficiently.

[0096] In addition, in the present embodiment, the second refrigerant flow path 212 where the refrigerant flows from the water-cooled condenser 230 toward the second expansion valve 240, and the third refrigerant flow path 213 where the refrigerant flows from the second expansion valve 240 toward the cooler 255 are spread between X3 and X4 along the X direction and are arranged parallel to each other. In addition, in order to improve the heat exchange efficiency, it is configured to shorten the interval Y2 in the Y direction orthogonal to the X direction. The interval Y2 can be set based on the processing accuracy when the second refrigerant flow path 212 and the third refrigerant flow path 213 are formed by hole processing (can be closer). In addition, the refrigerant flow path of heat exchange can be formed by the dividing surface of the flow path shell 210.

[0097] Between X3 and X4, the refrigerant flows from X4 to X3 in the second refrigerant flow path 212, and the refrigerant flows from X3 to X4 in the third refrigerant flow path 213. Therefore, here, the flow directions of the refrigerants in the high-temperature flow path 201H and the low-temperature flow path 201L are also opposite to each other. As a result, the refrigerant flowing in the second refrigerant flow path 212 performs heat exchange with the refrigerant flowing in the third refrigerant flow path 213, and the refrigerant flowing in the third refrigerant flow path 213 performs heat exchange with the refrigerant flowing in the second refrigerant flow path 212. The temperature of the refrigerant flowing in the high-temperature flow path 201H gradually decreases as it flows in the high-temperature flow path 201H in the first direction (from X4 to X3), and the temperature of the refrigerant flowing in the low-temperature flow path 201L gradually increases as it flows in the low-temperature flow path 201L in the second direction (from X3 to X4) opposite to the first direction. That is, the temperature difference between the high temperature flow path 201H and the low temperature flow path 201L in the heat exchange region becomes balanced, so that the heat exchange efficiency can be improved. Therefore, heat exchange can be performed efficiently.

[0098] Fig.12 2 is a diagram showing the relationship between the second refrigerant flow path 212 and the fourth refrigerant flow path 214 of this embodiment and other flow paths. Fig.12 As shown, the second refrigerant flow path 212 for allowing the refrigerant to flow between the water-cooled condenser 230 and the first expansion valve 235, and the fourth refrigerant flow path 214 for allowing the refrigerant to flow between the evaporator 255 and the compressor 225 are arranged at a shorter interval than the intervals between other flow paths arranged in the flow path housing 210. The second refrigerant flow path 212 is a refrigerant flow path for the refrigerant to flow from the water-cooled condenser 230 to the first expansion valve 235. The fourth refrigerant flow path 214 is a refrigerant flow path for the refrigerant to flow from the evaporator 245 to the compressor 225 via the accumulator 220. The other flow paths arranged in the flow path housing 210 are equivalent to the first refrigerant flow path 211 for the refrigerant to flow from the compressor 225 to the water-cooled condenser 230, and the third refrigerant flow path 213 for the refrigerant to flow from the first expansion valve 235 to the evaporator 245. Therefore, the second refrigerant flow path 212 and the fourth refrigerant flow path 214 are provided at a shorter interval than the interval between the first refrigerant flow path 211 and the third refrigerant flow path 213 .

[0099] That is, in the vicinity of the evaporator 245 , the fourth refrigerant flow path 214 is formed closer to the second refrigerant flow path 212 than to the first refrigerant flow path 211 and the third refrigerant flow path 213 .

[0100] Fig.13 is a Mollier diagram showing the heat cycle in the cooling system 300. Fig.13In the Mollier diagram, the horizontal axis is the specific enthalpy of the refrigerant, and the vertical axis is the pressure of the refrigerant. In the Mollier diagram, according to the combination of specific enthalpy and pressure, the region R1 where the refrigerant exists in a supercooled state (liquid state), the region R2 where the refrigerant exists as wet steam (gas-liquid mixed state), and the region R3 where the refrigerant exists as superheated steam (gas state) are divided. The boundary between the supercooled state and the wet steam state is the saturated liquid line L1, and the boundary between the wet steam state and the superheated steam state is the saturated steam line L2. The boundary point between the saturated liquid line L1 and the saturated steam line L2 is the critical point CP.

[0101] When the refrigerant is pressurized (compressed) in the compressor 225, the specific enthalpy increases. Fig.13 The medium-temperature, low-pressure gaseous refrigerant shown in (a) becomes Fig.13 The high-temperature and high-pressure gaseous refrigerant shown in (b) is Fig.13 The high-temperature and high-pressure refrigerant shown in (b) is sent to the water-cooled condenser 30 and condensed, and the specific enthalpy becomes smaller under the isobaric state. Fig.13 (c) shows a medium-temperature and high-pressure liquid refrigerant. Fig.13 The medium-temperature and high-pressure refrigerant shown in (c) expands in the first expansion valve 235, and the pressure decreases. Fig.13 (d) is a low-temperature and low-pressure gas-liquid mixed refrigerant. Fig.13 The low-temperature and low-pressure refrigerant shown in (d) evaporates in the evaporator 245, and the specific enthalpy changes greatly under the isobaric state. Fig.13 (a) is a medium-temperature, low-pressure gaseous refrigerant.

[0102] As in the present embodiment, in the flow path housing 210, the refrigerant pressurized by the compressor 225 can be preheated by performing heat exchange between the high-temperature flow path 201H, i.e., the second refrigerant flow path 212, and the low-temperature flow path 201L, i.e., the fourth refrigerant flow path 214. Thus, the specific enthalpy of the refrigerant before pressurization can be increased, and the refrigerant generated by the compressor 225 is compressed along the dotted lines shown by (e) to (f). On the other hand, the refrigerant condensed by the water-cooled condenser 230 can be precooled by heat exchange between the high-temperature flow path 201H, i.e., the second refrigerant flow path 212, and the low-temperature flow path 201L, i.e., the fourth refrigerant flow path 214. Thus, the specific enthalpy of the refrigerant before expansion in the first expansion valve 235 can be reduced, and the refrigerant expands along the dotted lines shown by (g) to (h) in the first expansion valve 235.

[0103] Thus, in the flow path housing 210, heat is exchanged between the high-temperature flow path 201H, i.e., the second refrigerant flow path 212, and the low-temperature flow path 201L, i.e., the fourth refrigerant flow path 214, so that the refrigerant pressurized by the compressor 225 becomes a more superheated vapor state, and the refrigerant delivered to the first expansion valve 235 becomes a more supercooled state. Therefore, the coefficient of performance can be improved with a compact structure.

[0104] [Other embodiments of the fifth embodiment]

[0105] In the above-mentioned embodiment, in the flow path housing 210, a case where heat exchange is performed between the high-temperature flow path 201H, i.e., the second refrigerant flow path 212, and the low-temperature flow path 201L, i.e., the fourth refrigerant flow path 214 is described. For example, in the flow path housing 210, heat exchange can also be performed between the high-temperature flow path 201H, i.e., the first refrigerant flow path 211, and the low-temperature flow path 201L, i.e., the third refrigerant flow path 213. In addition, heat exchange can also be performed between the high-temperature flow path 201H, i.e., the first refrigerant flow path 211, and the low-temperature flow path 201L, i.e., the fourth refrigerant flow path 214, and heat exchange can also be performed between the high-temperature flow path 201H, i.e., the second refrigerant flow path 212, and the low-temperature flow path 201L, i.e., the third refrigerant flow path 213. Furthermore, it is also possible to configure the heat exchange to be performed between the high temperature flow path 201H, i.e., the first refrigerant flow path 211 and the second refrigerant flow path 212, and the low temperature flow path 201L, i.e., the third refrigerant flow path 213, and it is also possible to configure the heat exchange to be performed between the high temperature flow path 201H, i.e., the first refrigerant flow path 211 and the second refrigerant flow path 212, and the low temperature flow path 201L, i.e., the fourth refrigerant flow path 214. Of course, it is also possible to configure the heat exchange to be performed between the high temperature flow path 201H, i.e., the first refrigerant flow path 211, and the low temperature flow path 201L, i.e., the third refrigerant flow path 213 and the fourth refrigerant flow path 214, and it is also possible to configure the heat exchange to be performed between the high temperature flow path 201H, i.e., the second refrigerant flow path 212, and the low temperature flow path 201L, i.e., the third refrigerant flow path 213 and the fourth refrigerant flow path 214.

[0106] In the fifth embodiment, the high temperature flow path 201H and the low temperature flow path 201L are arranged parallel to each other and close to each other, but the high temperature flow path 201H and the low temperature flow path 201L may be arranged close to each other in a non-parallel state, or the high temperature flow path 201H and the low temperature flow path 201L may be arranged to cross each other. In addition, the shape of the high temperature flow path 201H and the low temperature flow path 201L being arranged parallel to each other and close to each other may be, for example, a meandering flow path, and is not particularly limited.

[0107] In the fifth embodiment, the refrigerant flows in opposite directions in the high temperature flow path 201H and the low temperature flow path 201L. However, the refrigerant flows in the high temperature flow path 201H and the low temperature flow path 201L may be the same.

[0108] In the fifth embodiment described above Fig.11 In FIG. 1 , the high temperature flow path 201H and the low temperature flow path 201L are shown to extend in a predetermined direction (X direction). A comb-shaped portion 260 that protrudes from one of the high temperature flow path 201H and the low temperature flow path 201L toward the other side may be formed in each of the high temperature flow path 201H and the low temperature flow path 201L. Fig.14 FIG. 2 shows a high temperature flow path 201H and a low temperature flow path 201L formed with such a comb-shaped portion 260. Fig.14 As shown, a comb-tooth-shaped portion 260 (specifically, a comb-tooth-shaped portion 260H) is provided in the high-temperature flow path 201H to protrude from the high-temperature flow path 201H toward the low-temperature flow path 201L, and a comb-tooth-shaped portion 260 (specifically, a comb-tooth-shaped portion 260L) is provided in the low-temperature flow path 201L to protrude from the low-temperature flow path 201L toward the high-temperature flow path 201H. Fig.14 As shown, the comb-tooth-shaped portion 260H and the comb-tooth-shaped portion 260L are configured such that the comb-tooth-shaped portion 260H enters between two comb-tooth-shaped portions 260L, and the comb-tooth-shaped portion 260L enters between two comb-tooth-shaped portions 260H. Thus, the area close to the high-temperature flow path 201H and the low-temperature flow path 201L (the area that contributes to heat exchange) is increased, and the heat exchange efficiency can be improved.

[0109] In addition, Fig.14 In the example of FIG. 1 , the comb-shaped portion 260 is formed to protrude from each of the high-temperature flow path 201H and the low-temperature flow path 201L in a direction orthogonal to the high-temperature flow path 201H and the low-temperature flow path 201L, but it may also be formed as follows. Fig.15 As shown in FIG. 1 , the comb-tooth-shaped portion 260 may be formed at an obtuse angle to the above-mentioned orthogonal direction, and the comb-tooth-shaped portion 260 may also protrude in an arc shape. Fig.16As shown, the top view of the comb-tooth-shaped portion 260 is configured as a triangle. In this case, for example, it can also be configured as a triangle having an edge at an obtuse angle to the flow direction of the refrigerant flowing in the high-temperature flow path 201H and the low-temperature flow path 201L on the upstream side, and having an edge orthogonal to the flow direction of the refrigerant flowing in the high-temperature flow path 201H and the low-temperature flow path 201L on the downstream side. Of course, the edge on the downstream side can also be configured with an edge at an acute angle to the flow direction of the refrigerant flowing in the high-temperature flow path 201H and the low-temperature flow path 201L on the downstream side. By setting it as such a structure, it is possible to easily allow the refrigerant to enter the comb-tooth-shaped portion 260. Therefore, the high-temperature flow path 201H and the low-temperature flow path 201L can be made close to each other without hindering the flow of the refrigerant in the high-temperature flow path 201H and the low-temperature flow path 201L.

[0110] In the fifth embodiment described above, the case where the flow path in the flow path housing 210 is formed by drilling is described, but it may also be formed by casting, forging, or the like, for example.

[0111] [Overview of the above-mentioned embodiment]

[0112] Hereinafter, the outline of the manifolds 100 and 201 described above will be described.

[0113] (1) The manifold 100, 201 includes a flow path housing 105, 210, which has a first flow path 71, 72, 73 through which a first cooling fluid flows, and a second flow path 41, 42, 48, 49 through which a second cooling fluid flows. In the flow path housing 105, 210, heat exchange is performed between the first cooling fluid flowing in the first flow paths 71, 72, 73 and the second cooling fluid flowing in the second flow paths 41, 42, 48, 49.

[0114] According to this structure, by performing heat exchange between the first cooling fluid flowing in the first flow path 71, 72, 73 and the second cooling fluid flowing in the second flow path 41, 42, 48, 49 of the flow path housing 105, 210 provided in the manifold 100, 201, sufficient cooling performance can be obtained even with a small heat exchanger. In addition, since heat exchange can be performed in the flow path housing 105, 210, the manifold 100, 201 can be miniaturized compared to the case where the heat exchanger is externally provided in the flow path housing 105, 210. Furthermore, the first cooling fluid flowing in the first flow path 71, 72, 73 can be cooled and the second cooling fluid flowing in the second flow path 41, 42, 48, 49 can be heated in the flow path housing 105, 210. By performing heat exchange between fluids in the flow path housing 105, 210, for example, the coefficient of performance of the compressor 22, 225 and the expansion valve 26, 235, 240 can be improved. Therefore, the internal heat exchanger that performs cooling and heating of the fluid can be miniaturized or heat exchange can be performed without additional provision, so the manifolds 100 and 201 can be miniaturized.

[0115] (2) According to the manifold 100 described in (1), the first flow paths 71, 72, 73 are preferably refrigerant flow paths between the evaporator 110 and the condenser 120, through which the refrigerant serving as the first cooling fluid flows, and the second flow paths 41, 42, 48, 49 are cooling flow paths through which the coolant serving as the second cooling fluid flows at least toward the battery 9.

[0116] According to this structure, heat exchange is performed not only in the heat exchangers, that is, the evaporator 110 and the condenser 120, but also between the refrigerant flowing in the refrigerant flow path provided in the flow path housing 105 of the manifold 100 and the coolant flowing in the cooling flow path, thereby achieving the required cooling performance even when using small evaporators 110 and condensers 120. Therefore, it is possible to provide a manifold 100 that can achieve sufficient cooling performance even when using a small heat exchanger.

[0117] (3) According to the manifold 100 described in (2), preferably, the flow path shell 105 is provided with a water-cooled condenser 120 as a condenser 120 for the refrigerant at a position on the upstream side relative to the flow direction of the refrigerant, and a cooler 110 as an evaporator 110 for the refrigerant is installed at a position on the downstream side relative to the flow direction of the refrigerant.

[0118] According to this structure, by arranging the water-cooled condenser 120 as the condenser 120 at a position that is on the upstream side with respect to the flow direction of the refrigerant, the refrigerant condensed by the water-cooled condenser 120 can flow and apply heat to the low-temperature coolant, so that the refrigerant that is not completely condensed by the water-cooled condenser 120 can also be condensed. In addition, by arranging the cooler 110 as the evaporator 110 at a position that is on the downstream side with respect to the flow direction of the refrigerant, the refrigerant before flowing into the cooler 110 can flow and take away heat from the high-temperature coolant, so that a part of the refrigerant can be evaporated before flowing into the cooler 110.

[0119] (4) According to the manifold 201 described in (1), preferably, the first flow path is the first refrigerant flow path 211 that allows the refrigerant as the first cooling fluid to flow between the compressor 225 and the condenser 230, or the second refrigerant flow path 212 that allows the refrigerant to flow between the condenser 230 and the expansion valve 235, and the second flow path is the third refrigerant flow path 213 that allows the refrigerant as the second cooling fluid with a temperature lower than the first cooling fluid to flow between the expansion valves 235, 240 and the evaporators 245, 255, or the fourth refrigerant flow path 214 that allows the refrigerant to flow between the evaporators 245, 255 and the compressor 225.

[0120] According to this structure, the refrigerant flowing in at least one of the first refrigerant flow path 211 and the second refrigerant flow path 212 can be cooled, and the refrigerant flowing in at least one of the third refrigerant flow path 213 and the fourth refrigerant flow path 214 can be heated in the flow path housing 210. By performing heat exchange between refrigerants in the flow path housing 210, the coefficient of performance of the compressor 225 and the expansion valves 235 and 240 can be improved. Therefore, the internal heat exchanger that cools and heats the refrigerant can be miniaturized, or heat exchange can be performed without additional installation, so the heat exchange system can be miniaturized.

[0121] (5) According to the manifold 100 described in (1), preferably, the first flow paths 71, 72, 73 are refrigerant flow paths for allowing the refrigerant as the first cooling fluid to flow toward the heat exchanger, and the second flow paths 41, 42, 48, 49 are cooling flow paths for allowing the coolant as the second cooling fluid to flow toward the heat exchanger, and the heat exchanger has a refrigerant inlet 111 for the refrigerant to flow in, a refrigerant outlet 112 for the refrigerant to flow out, a coolant inlet 113 for the coolant to flow in, and a coolant outlet 114 for the coolant to flow out, and the heat exchanger is fixed to the flow path housing 105 by respectively connecting the refrigerant flow path and the refrigerant inlet 111, the refrigerant flow path and the refrigerant outlet 112, the cooling flow path and the coolant inlet 113, and the cooling flow path and the coolant outlet 114.

[0122] According to this structure, the heat exchanger can be fixed to the flow channel housing 105 without using bolts, etc., so there is no need to provide a flange for fixing the bolts, etc. to the heat exchanger, and the heat exchanger can be miniaturized. Thus, a small and low-cost manifold 100 can be realized.

[0123] (6) According to the manifold 100 described in (5), preferably, the heat exchanger has a laminated flow path 117 .

[0124] According to this configuration, the manifold 100 can be equipped with functions required as a heat exchanger.

[0125] (7) In the manifold 100 or 201 described in any one of (1) to (6), preferably, the first flow paths 71 , 72 , 73 and the second flow paths 41 , 42 , 48 , 49 are provided in close proximity.

[0126] According to this structure, heat exchange can be easily performed between the first flow paths 71, 72, 73 and the second flow paths 41, 42, 48, 49, so the heat exchange efficiency can be improved. In addition, the configuration of the first flow paths 71, 72, 73 and the second flow paths 41, 42, 48, 49 can be simplified, and the manifolds 100, 201 can be miniaturized.

[0127] (8) In the manifold 201 described in any one of (1) to (7), preferably, each of the first flow path and the second flow path is formed with a comb-tooth-like portion 260 protruding from one side of the first flow path and the second flow path toward the other side.

[0128] According to this structure, the heat exchange between the first cooling fluid and the second cooling fluid is performed not only between the first flow path and the second flow path, but also in the comb-tooth-shaped portion 260. In addition, by such a comb-tooth-shaped portion 260, the area (area) where the first flow path and the second flow path are close can be increased. Therefore, the heat exchange efficiency can be further improved. As a result, even if a smaller condenser is used as a heat exchanger, the required sufficient cooling performance can be obtained.

[0129] (9) According to the manifold 201 described in (7), the flow path for allowing the refrigerant to flow between the condenser 230 and the expansion valves 235, 240, and the flow path for allowing the refrigerant to flow between the evaporators 245, 255 and the compressor 225 are preferably arranged at a shorter interval than the interval between other flow paths arranged in the flow path casing 210.

[0130] According to this structure, heat exchange can be performed between the flow path where the refrigerant flows between the condenser 230 and the expansion valves 235 and 240, and the flow path where the refrigerant flows between the evaporators 245 and 255 and the compressor 225. For example, by making the flow direction of the refrigerant flowing in the flow path between the condenser 230 and the expansion valves 235 and 240 and the flow direction of the refrigerant flowing in the flow path between the evaporators 245 and 255 and the compressor 225 opposite to each other (reverse), the temperature difference between the flow path between the condenser 230 and the expansion valves 235 and 240 and the flow path between the evaporators 245 and 255 and the compressor 225 becomes balanced, so that the heat exchange efficiency can be improved. Therefore, heat exchange can be performed efficiently.

[0131] (10) According to the manifold 100 described in (7), the refrigerant flow path in which the refrigerant flowing out of the evaporator 110 as the first cooling fluid flows, and the cooling flow path in which the coolant flowing into the evaporator 110 as the second cooling fluid flows are preferably arranged at a shorter interval than the interval between other flow paths arranged in the flow path housing 105.

[0132] According to this configuration, heat exchange can be performed between the refrigerant flowing in the refrigerant flow path from the evaporator 110 and the coolant flowing in the cooling flow path to the evaporator 110. Thus, even if a small condenser is used as the evaporator 110, a required sufficient cooling performance can be obtained.

[0133] Possibility of industrial application

[0134] The technique of the present invention can be used in manifolds.

[0135] Description of Reference Numerals

[0136] [First embodiment]

[0137] 9: battery, 41: first internal flow path (second flow path, cooling flow path, cooling pipe), 42: second internal flow path (second flow path, cooling flow path, cooling pipe), 48: eighth internal flow path (second flow path, cooling flow path, cooling pipe), 49: ninth internal flow path (second flow path, cooling flow path, cooling pipe), 71: first internal refrigerant path (first flow path, refrigerant flow path, refrigerant pipe), 72: second internal refrigerant path (first flow path, refrigerant flow path, refrigerant pipe), 73: third internal refrigerant path (first flow path, refrigerant pipe) Refrigerant flow path, refrigerant tube), 81: parallel internal flow path (second flow path, cooling flow path, cooling tube), 82: parallel internal refrigerant path (first flow path, refrigerant flow path, refrigerant tube), 83: closed internal flow path (second flow path, closed cooling flow path, cooling flow path, cooling tube), 84: closed internal refrigerant path (first flow path, closed refrigerant flow path, refrigerant flow path, refrigerant tube), 100: manifold, 105: flow path shell, 110: cooler (evaporator), 120: water-cooled condenser (condenser, heat exchanger).

[0138] [Second embodiment]

[0139] 111: refrigerant inlet, 112: refrigerant outlet, 113: cooling water inlet, 114: cooling water outlet, 117: heat exchange flow path (laminated flow path), 117a: heat exchange refrigerant flow path (laminated flow path), 117b: heat exchange cooling water flow path (laminated flow path).

[0140] [Third embodiment]

[0141] 201: manifold, 201H: high-temperature flow path, 201L: low-temperature flow path, 210: flow path housing, 211: first refrigerant flow path, 212: second refrigerant flow path, 213: third refrigerant flow path, 214: fourth refrigerant flow path, 225: compressor (compressor), 230: water-cooled condenser (condenser), 235: first expansion valve (expansion valve), 240: second expansion valve (expansion valve), 245: evaporator (evaporator), 255: cooler (evaporator), 260: comb-tooth portion, 260H: comb-tooth portion, 260L: comb-tooth portion.

Claims

1. A manifold comprising: a flow path housing having a first flow path through which a first cooling fluid flows and a second flow path through which a second cooling fluid flows, In the flow path housing, heat exchange is performed between the first cooling fluid flowing in the first flow path and the second cooling fluid flowing in the second flow path.

2. The manifold according to claim 1, wherein: The first flow path is a refrigerant flow path between the evaporator and the condenser, through which the refrigerant serving as the first cooling fluid flows. The second flow path is a cooling flow path that allows a coolant serving as the second cooling fluid to flow at least toward the battery.

3. The manifold of claim 2, wherein: The flow path shell is provided with a water-cooled condenser as the condenser for the refrigerant at an upstream position relative to the flow direction of the refrigerant, and a cooler as the evaporator for the refrigerant at a downstream position relative to the flow direction of the refrigerant.

4. The manifold of claim 1, wherein: The first flow path is a first refrigerant flow path that allows the refrigerant, which is the first cooling fluid, to flow between the compressor and the condenser, or a second refrigerant flow path that allows the refrigerant to flow between the condenser and the expansion valve. The second flow path is a third refrigerant flow path that allows the refrigerant, which is the second cooling fluid having a lower temperature than the first cooling fluid, to flow between the expansion valve and the evaporator, or a fourth refrigerant flow path that allows the refrigerant to flow between the evaporator and the compressor.

5. The manifold of claim 1, wherein: The first flow path is a refrigerant flow path for allowing the refrigerant serving as the first cooling fluid to flow toward the heat exchanger. The second flow path is a cooling flow path for allowing the coolant as the second cooling fluid to flow toward the heat exchanger. The heat exchanger has a refrigerant inlet through which the refrigerant flows in, a refrigerant outlet through which the refrigerant flows out, a coolant inlet through which the coolant flows in, and a coolant outlet through which the coolant flows out. The heat exchanger is fixed to the flow path housing by respectively joining the refrigerant flow path and the refrigerant inlet, the refrigerant flow path and the refrigerant outlet, the cooling flow path and the coolant inlet, and the cooling flow path and the coolant outlet.

6. The manifold of claim 5, wherein: The heat exchanger has a laminated flow path.

7. The manifold according to any one of claims 1 to 6, wherein: The first flow path and the second flow path are provided in close proximity.

8. The manifold according to any one of claims 1 to 7, wherein: A comb-teeth-like portion that protrudes from one of the first flow path and the second flow path toward the other is formed in each of the first flow path and the second flow path.

9. The manifold of claim 7, wherein: The flow path for allowing the refrigerant to flow between the condenser and the expansion valve and the flow path for allowing the refrigerant to flow between the evaporator and the compressor are provided at a shorter interval than intervals between other flow paths provided in the flow path housing.

10. The manifold of claim 7, wherein: The refrigerant flow path in which the refrigerant as the first cooling fluid flows out of the evaporator and the cooling flow path in which the coolant as the second cooling fluid flows into the evaporator are provided at a shorter interval than the interval between other flow paths provided in the flow path housing.

Images