Manifold

Abstract

The present invention provides a manifold comprising a channel housing including a first channel for circulating a first cooling fluid and a second channel for circulating a second cooling fluid, wherein in the channel housing, heat is exchanged between the first cooling fluid circulating in the first channel and the second cooling fluid circulating in the second channel.

Description

manifold

[0001] The present invention relates to a manifold.

[0002] In recent years, automobiles equipped with motors as a driving source (such as hybrid electric vehicles (HEVs), plug-in hybrid electric vehicles (PHEVs), battery electric vehicles (BEVs), and fuel cell electric vehicles (FCEVs)) have become widespread. These automobiles (hereinafter collectively referred to as "electric vehicles") are equipped with batteries to drive the motors. Electric vehicles have many devices that require cooling, such as motors (including internal combustion engines such as engines), batteries, air conditioners, and ECUs. To cool these devices, cooling circuits are configured to circulate coolant or refrigerant. However, these devices may have different optimum operating temperatures. In such cases, the temperatures of the circulating coolant or refrigerant are controlled by exchanging heat through heat exchangers such as chillers or water-cooled condensers to change the temperature of the circulating coolant or refrigerant for each device with a different operating temperature.

[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. Heat is exchanged between the heat pump cycle and the high-temperature water circuit by a water-cooled condenser, and heat is exchanged between the heat pump cycle and the low-temperature water circuit by a chiller and an internal heat exchanger.

[0004] The heat exchange system disclosed in Patent Document 2 includes a heat pump cycle. The heat pump cycle includes auxiliary devices such as a compressor (called a compressor in Patent Document 2), an indoor radiator, an electric expansion valve, a first heat exchanger, a solenoid valve, an evaporator (called an evaporator in Patent Document 2), and an accumulator. The heat pump cycle is a thermal cycle for heating or cooling the vehicle interior.

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

[0006] JP 2020-192965 A JP 2013-139251 A JP 2020-11615 A

[0007] In the heat exchange system disclosed in Patent Document 1, the heat exchange locations are limited to a water-cooled condenser, a chiller, and an internal heat exchanger (hereinafter collectively referred to as "heat exchangers"), so in order to improve the heat exchange performance (efficiency), a large-sized heat exchanger must be used. This occupies the limited space in the engine compartment of the vehicle. Furthermore, if the size of the heat exchanger is reduced, there is a risk that the desired cooling performance cannot be obtained.

[0008] In the heat exchange system disclosed in Patent Document 2, the compressor, the interior radiator, the electric expansion valve, the first heat exchanger, the solenoid valve, the evaporator, and the accumulator are arranged as independent components. These components are usually fixed to the vehicle body with bolts or the like. Therefore, the heat exchange system occupies a limited space in the engine compartment of the vehicle, leaving room for improvement.

[0009] Furthermore, when the air conditioning device is installed in a vehicle, miniaturization is desirable from the viewpoint of piping management 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 it is necessary to provide a location for connecting the piping, which makes the refrigerant circuit large. In addition, since it includes an internal heat exchanger, the size is large, and there is room for improvement in miniaturization.

[0010] Therefore, there is a demand for a manifold that can reduce the size of the heat exchange system.

[0011] A characteristic configuration of the manifold according to the present invention is that it comprises 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 occurs between the first cooling fluid flowing through the first flow path and the second cooling fluid flowing through the second flow path.

[0012] With this characteristic configuration, sufficient cooling performance can be achieved even with a small heat exchanger by performing heat exchange between a first cooling fluid flowing through a first flow path provided in the flow path housing of the manifold and a second cooling fluid flowing through a second flow path. Furthermore, because heat exchange can be performed within the flow path housing, the manifold can be made smaller than when a heat exchanger is externally attached to the flow path housing. Furthermore, cooling of the first cooling fluid flowing through the first flow path and heating of the second cooling fluid flowing through the second flow path can be performed within the flow path housing. By performing heat exchange between the fluids within this flow path housing, it is possible to improve the coefficient of performance of, for example, a compressor or an expansion valve. Therefore, heat exchange can be performed without the need for a small internal heat exchanger or a separate internal heat exchanger for cooling and heating the fluids, allowing the manifold to be made smaller.

[0013] FIG. 1 is a circuit configuration diagram of a cooling system having a manifold according to a first embodiment. FIG. 2 is a schematic configuration diagram of a manifold. FIG. 3 is a diagram illustrating the relationship between the first internal refrigerant passage and the eighth internal passage according to the first embodiment and other passages. FIG. 4 is a diagram illustrating the passage configuration of a manifold according to a second embodiment. FIG. 5 is a diagram illustrating the passage configuration of a manifold according to a modified example of the second embodiment. FIG. 6 is a diagram illustrating the passage configuration of a manifold according to another modified example of the second embodiment. FIG. 7 is a cross-sectional view illustrating a method of fixing a chiller to a passage housing according to a third embodiment. FIG. 8 is a schematic configuration diagram of a manifold according to a fourth embodiment. FIG. 9 is a cross-sectional view illustrating the configuration of a chiller within a passage housing according to the fourth embodiment. FIG. 10 is a circuit configuration diagram of a cooling system having a manifold according to a fifth embodiment. FIG. 11 is a schematic configuration diagram of a manifold according to the fifth embodiment. FIG. 12 is a diagram illustrating the relationship between the second refrigerant passage and the fourth refrigerant passage according to the fifth embodiment and other passages. FIG. 13 is a Mollier diagram illustrating a thermal cycle. FIG. 14 is a diagram illustrating a high-temperature passage and a low-temperature passage according to another embodiment. FIG. 15 is a diagram illustrating a high-temperature passage and a low-temperature passage according to another embodiment.

[0014] Hereinafter, embodiments of a manifold according to the present invention will be described in detail with reference to the drawings. Note that the embodiments described below are merely examples for explaining the present invention, and the present invention is not limited to these embodiments. Therefore, the present invention can be embodied in various forms without departing from the spirit of the present invention.

[0015] [First Embodiment] [Configuration of Cooling System] As shown in FIG. 1 , a cooling system A including a manifold 100 according to this embodiment is broadly divided into a coolant circuit B and a refrigerant circuit C. A coolant (an example of a second cooling fluid, a coolant) such as an antifreeze or long-life coolant mainly containing ethylene glycol or the like flows through the coolant circuit B, and a refrigerant (an example of a first cooling fluid) such as a hydrofluorocarbon (HFC) flows through the refrigerant circuit C. In FIG. 1 , the portion surrounded by a dashed line is the manifold 100 according to this embodiment. The manifold 100 includes a flow path housing 105 and auxiliary equipment including a chiller 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 configured as a four-way valve, a second electric pump 7, a switching valve 10 configured as a three-way valve, a third electric pump 11, a first expansion valve 23, and a second expansion valve 26. In FIG. 1 , the auxiliary components are depicted as being inside the flow path housing 105. However, as shown in FIG. 2 , they are actually mounted on the outer surface of the flow path housing 105. FIG. 2 shows a schematic configuration diagram of the manifold 100. However, in FIG. 2 , auxiliary components (e.g., pumps and valves) other than the chiller 110 and the water-cooled condenser 120 are omitted. In this embodiment, the flow path housing 105 is formed of a metal material with high thermal conductivity, including aluminum, and the flow paths constituting the coolant circuit B and the refrigerant circuit C are formed by directly drilling holes in the flow path housing 105. In this embodiment, an antifreeze or long-life coolant containing ethylene glycol or the like as a main component is used as the coolant, but a coolant composed of insulating oil such as paraffin may also be used. The refrigerant may also be a hydrofluoroolefin (HFO) or other refrigerant. These are the same for all embodiments described below.

[0016] First, the coolant circuit B will be described. The coolant circuit B is a flow path to the right of the chiller 110 and the water-cooled condenser 120 in FIG. 1 . The coolant 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 disposed midway along the first external flow path 31. The coolant flows through 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 in this order. Hereinafter, the upstream side and downstream side of the coolant flow direction in the coolant circuit B will also be simply referred to as the upstream side and the downstream side.

[0017] A second external flow path 32 and a third external flow path 33 branch off from the first external flow path 31 downstream of the radiator 1 and upstream of the first internal flow path 41. The second external flow path 32 is connected to a 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 coolant branched off from the first external flow path 31 to the second external flow path 32 flows through the second external flow path 32, cools the charger 2 and the DC-DC converter 3, and then flows into the third internal flow path 43. The coolant is pressurized in the third internal flow path 43 by the first electric pump 4, and then flows into the second internal flow path 42.

[0018] A 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. In the state shown in FIG. 1 , the fourth internal flow path 44 is connected to a fifth internal flow path 45 via a rotary valve 5. The downstream side of the fifth internal flow path 45 is connected to the second internal flow path 42.

[0019] The third external flow path 33 is connected downstream to a sixth internal flow path 46 formed inside the flow path housing 105. The sixth internal flow path 46 is connected to a seventh internal flow path 47 via a rotary valve 5. A second electric pump 7 is disposed midway along 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 through the third external flow path 33, cools the e-axle inverter 6, and flows into the sixth internal flow path 46. In the state shown in FIG. 1 , the cooling water is pressurized by the second electric pump 7 in the seventh internal flow path 47 via the rotary valve 5 and then flows out of the flow path housing 105. The e-axle inverter 6 is a unit that houses a rotating electric machine, a reducer, and a differential gear mechanism in a housing, and the inverter is provided integrally with the unit. 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.

[0020] 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 downstream to an eighth internal flow path 48 (an example of a second flow path, a cooling flow path) formed inside the flow path housing 105. The coolant flowing out of the seventh internal flow path 47 flows through the fourth external flow path 34, is cooled by the first heater core 8, is then heated by cooling the battery 9, and flows into the eighth internal flow path 48. The eighth internal flow path 48 is connected downstream to the chiller 110. The downstream side of the chiller 110 is connected to the second internal flow path 42. The coolant flowing through the eighth internal flow path 48 flows into the chiller 110, where it is cooled by the atomized refrigerant that flows in from a third internal refrigerant path 73 (an example of a first flow path, a refrigerant flow path) described later. The coolant flowing through the second internal flow path 42 flows into the first external flow path 31 connected to the outside of the flow path housing 105.

[0021] The first internal flow path 41, which is connected to the first external flow path 31, is connected to the water-cooled condenser 120 on the downstream side. The switching valve 10 and the third electric pump 11 are arranged in this order along the first internal flow path 41. The downstream side of the water-cooled condenser 120 is connected to a ninth internal flow path 49 (an example of a second flow path, a cooling flow path). The cooling water that flows into the first internal flow path 41 is pressurized by the third electric pump 11 and flows into the water-cooled condenser 120. Inside the water-cooled condenser 120, the cooling water absorbs heat from the refrigerant in a high-temperature compressed gas state that flows in from a second internal refrigerant path 72 (an example of a first flow path, a refrigerant flow path) described later, and is then heated. The cooling water then flows through the ninth internal flow path 49 and flows out of the flow path housing 105.

[0022] The ninth internal flow passage 49 is connected to the fifth external flow passage 35 outside the flow passage housing 105. The fifth external flow passage 35 is connected on the downstream side to a tenth internal flow passage 50 formed inside the flow passage housing 105. The tenth internal flow passage 50 is connected on the downstream side to the sixth internal flow passage 46. The coolant flowing out from the ninth internal flow passage 49 flows through the fifth external flow passage 35, is cooled by the second heater core 12, and flows into the tenth internal flow passage 50. The coolant flowing through the tenth internal flow passage 50 flows into the sixth internal flow passage 46.

[0023] 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 an 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 through the eleventh internal flow path 51, the cooling water flows from the first internal flow path 41 through the eleventh internal flow path 51, into the tenth internal flow path 50, and then flows into the sixth internal flow path 46.

[0024] Next, the refrigerant circuit C will be described. The refrigerant circuit C is a flow path to the left of the chiller 110 and the water-cooled condenser 120 in FIG. 1 . The refrigerant circuit C is formed inside the flow path housing 105, and a refrigerant flows through the refrigerant circuit C. The refrigerant circuit C has a first internal refrigerant passage 71 (an example of a first flow path or refrigerant passage) downstream of the chiller 110 in the refrigerant flow direction (hereinafter, the upstream and downstream sides of the refrigerant flow direction in the refrigerant circuit C are simply referred to as the upstream and downstream sides). The first internal refrigerant passage 71 is connected to a first external refrigerant passage 61 formed outside the flow path housing 105. The accumulator 21 and the compressor 22 are arranged in this order along the first external refrigerant passage 61. The downstream side of the first external refrigerant passage 61 is connected to a second internal refrigerant passage 72 formed inside the flow path housing 105. The downstream side of the second internal refrigerant passage 72 is connected to the water-cooled condenser 120. The downstream side of the water-cooled condenser 120 is connected to a third internal refrigerant passage 73 formed inside the flow path housing 105. The third internal refrigerant passage 73 is connected to the chiller 110 via a first expansion valve 23 disposed midway through the passage. In other words, in the passage housing 105, the water-cooled condenser 120 is mounted at a position on the upstream side of the third internal refrigerant passage 73 in the direction of refrigerant flow, and the chiller 110 is mounted at a position on the downstream side of the direction of refrigerant flow.

[0025] A fourth internal refrigerant path 74 branches off from the third internal refrigerant path 73 upstream of the first expansion valve 23. The second expansion valve 26 is disposed in the fourth internal refrigerant path 74. The fourth internal refrigerant path 74 is connected to a second external refrigerant path 62 formed outside the flow path housing 105. The evaporator 24 and the check valve 25 are disposed in this order in the second external refrigerant path 62. The second external refrigerant path 62 is connected to a 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.

[0026] Next, the flow of refrigerant in the refrigerant circuit C will be described. The refrigerant flows through the first external refrigerant passage 61 and becomes a high-temperature compressed gas in the compressor 22. The refrigerant then flows through the first external refrigerant passage 61 and the second internal refrigerant passage 72 into the water-cooled condenser 120. In the water-cooled condenser 120, the refrigerant is condensed and liquefied by the cooling water flowing from the first internal flow path 41. The liquefied refrigerant used for cooling the vehicle interior leaves the water-cooled condenser 120, flows through the third internal refrigerant passage 73 and the fourth internal refrigerant passage 74, expands in the second expansion valve 26, and becomes a low-temperature, low-pressure mist. The mist refrigerant then flows through the second external refrigerant passage 62 and is sent to the evaporator 24. The mist refrigerant absorbs heat from air introduced from the outside and evaporates in the evaporator 24. Conversely, the air is cooled by the refrigerant, becoming cool air and being sent into the vehicle interior. The evaporated refrigerant flows through the check valve 25 arranged in the second external refrigerant passage 62 into the fifth internal refrigerant passage 75 and flows out of the flow path housing 105 through the first internal refrigerant passage 71. The evaporated refrigerant then flows through the first external refrigerant passage 61 and is sent to the accumulator 21. If the evaporated refrigerant contains liquid, the accumulator 21 separates the liquid from the evaporated refrigerant. The evaporated refrigerant then flows through the first external refrigerant passage 61 and returns to the compressor 22, where it is compressed again to become a high-temperature compressed gas.

[0027] The refrigerant liquefied by the water-cooled condenser 120 that is not used for cooling the vehicle interior flows out of the water-cooled condenser 120, circulates through the third internal refrigerant passage 73, and is expanded by the first expansion valve 23 to form a low-temperature, low-pressure mist. The mist refrigerant then evaporates in the chiller 110 by absorbing heat from the coolant flowing in from the eighth internal passage 48. The evaporated refrigerant flows out of the passage housing 105 through the first internal refrigerant passage 71. The vaporized refrigerant then flows through the first external refrigerant passage 61 and is sent to the accumulator 21. The check valve 25 in the second external refrigerant passage 62 prevents the refrigerant from flowing into the evaporator 24. In the accumulator 21, if the vaporized refrigerant contains liquid, the liquid refrigerant is separated. The vaporized refrigerant then flows through the first external refrigerant passage 61 and returns to the compressor 22, where it is compressed again to form a high-temperature compressed gas.

[0028] Normally, heat exchange between the cooling water and the refrigerant is carried out only in the heat exchangers, the chiller 110 and the water-cooled condenser 120. However, in this embodiment, by bringing the flow paths of the cooling water circuit B and the refrigerant circuit C close to each other, heat exchange is carried out not only in the chiller 110 and the water-cooled condenser 120 but also between the flow paths.

[0029] 2 , the flow paths connected to the chiller 110 are arranged such that, in the flow path housing 105, the eighth internal flow path 48 of the coolant circuit B flowing into the chiller 110 and the first internal refrigerant path 71 of the refrigerant circuit C flowing out of the chiller 110 are arranged parallel to and adjacent to each other, and the second internal flow path 42 of the coolant circuit B flowing out of the chiller 110 and the third internal refrigerant path 73 of the refrigerant circuit C flowing into the chiller 110 are arranged parallel to and adjacent to each other. In this case, the flow direction of the coolant flowing through the eighth internal flow path 48 is opposite to the flow direction of the refrigerant flowing through the first internal refrigerant path 71, and the flow direction of the coolant flowing through the second internal flow path 42 is opposite to the flow direction of the refrigerant flowing through the third internal refrigerant path 73. Furthermore, in the flow path housing 105, the eighth internal flow path 48 and the first internal refrigerant path 71 exchange heat at an L-shaped portion, and the second internal flow path 42 and the third internal refrigerant path 73 exchange heat at a linear portion. With this configuration, heat exchange occurs not only within the chiller 110, but also between the cooling water flowing through the eighth internal flow path 48 and the refrigerant flowing through the first internal refrigerant path 71, and also between the cooling water flowing through the second internal flow path 42 and the refrigerant flowing through the third internal refrigerant path 73. Because heat exchange also occurs between the internal flow path outside the chiller 110 and the internal refrigerant path, sufficient cooling performance can be obtained even if a small chiller 110 is used.

[0030] 2 , the flow paths connected to the water-cooled condenser 120 are arranged such that, in the flow path housing 105, the first internal flow path 41 of the coolant 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 parallel to and adjacent to each other, and the ninth internal flow path 49 of the coolant 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 parallel to and adjacent to each other. In this case, the flow direction of the coolant flowing through the first internal flow path 41 is opposite to the flow direction of the refrigerant flowing through the third internal refrigerant path 73, and the flow direction of the coolant flowing through the ninth internal flow path 49 is opposite to the flow direction of the refrigerant flowing through the second internal refrigerant path 72. In the flow path housing 105, the first internal flow path 41 and the third internal refrigerant path 73 exchange heat at a linear location, and the ninth internal flow path 49 and the second internal refrigerant path 72 exchange heat at an L-shaped location. With this configuration, heat exchange occurs not only within the water-cooled condenser 120, but also between the cooling water flowing through the first internal flow path 41 and the refrigerant flowing through the third internal refrigerant path 73, and between the cooling water flowing through the ninth internal flow path 49 and the refrigerant flowing through the second internal refrigerant path 72. In this way, heat exchange also occurs between the internal flow path outside the water-cooled condenser 120 and the internal refrigerant path, so that sufficient cooling performance can be obtained even if a small water-cooled condenser 120 is used.

[0031] 3 is a diagram showing the relationship between the first internal refrigerant passage 71 and the eighth internal passage 48 according to this embodiment and other passages. As shown in FIG. 3, the first internal refrigerant passage 71, through which the refrigerant flowing out from the chiller 110 flows, and the eighth internal passage 48, through which the cooling water flowing into the chiller 110 flows, are provided at a distance shorter than the distance between the other passages provided in the passage housing 105. The first internal refrigerant passage 71 is a refrigerant passage through which the refrigerant flows from the chiller 110 to the accumulator 21. The eighth internal passage 48 is a cooling passage through which the cooling water flows from the battery 9 to the chiller 110. The other flow paths provided in the flow path housing 105 correspond to the first internal flow path 41 through which the cooling water flowing into the water-cooled condenser 120 flows, the ninth internal flow path 49 through which the cooling water flowing out of the water-cooled condenser 120 flows, the third internal refrigerant path 73 through which the refrigerant flowing out of the water-cooled condenser 120 flows, and the second internal refrigerant path 72 through which the refrigerant flowing into the water-cooled condenser 120 flows. 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. In other words, the eighth internal flow path 48 is configured to be 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.

[0032] In addition, it is preferable to configure the ninth internal flow path 49 closer to the second internal refrigerant path 72 near the water-cooled condenser 120 than the first internal flow path 41, the second internal flow path 42, and the eighth internal flow path 48, and to configure the first internal flow path 41 closer to 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 preferable to configure the second internal flow path 42 closer to the third internal refrigerant path 73 near the chiller 110 than the first internal flow path 41, the eighth internal flow path 48, and the ninth internal flow path 49.

[0033] Second Embodiment Next, a manifold 100 according to a second embodiment will be 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, which are arranged parallel to and adjacent to each other in the flow path housing 105, are different from those of the first embodiment. The other configurations are the same as those of the first embodiment, and detailed description of the same configurations will be omitted. Hereinafter, the eighth internal flow path 48, the portion of the second internal flow path 42 arranged parallel to and adjacent to the third internal refrigerant path 73, the portion of the first internal flow path 41 arranged parallel to and adjacent to the third internal refrigerant path 73, and the ninth internal flow path 49 will be collectively referred to as a parallel internal flow path 81. Furthermore, the first internal refrigerant path 71, the portion of the third internal refrigerant path 73 arranged parallel to and adjacent to the second internal flow path 42 and the first internal flow path 41, and the second internal refrigerant path 72 will be collectively referred to as a parallel internal refrigerant path 82.

[0034] As shown in FIG. 4 , in this embodiment, a plurality of closed internal flow paths 83 (an example of a second flow path) branch off from the parallel internal flow path 81 in a direction perpendicular to the extension direction of the flow path. Furthermore, a plurality of closed internal refrigerant paths 84 (an example of a first flow path) branch off from the parallel internal refrigerant path 82 in a direction perpendicular to the extension direction of the flow path. The closed internal flow paths 83 have closed ends and extend in a direction approaching the parallel internal refrigerant path 82. The closed internal refrigerant paths 84 also have closed ends and extend in a direction approaching the parallel internal flow path 81. The closed internal flow paths 83 and the closed internal refrigerant path 84 are arranged parallel to and close to each other. Furthermore, the closed internal flow paths 83 and the closed internal refrigerant path 84 have the same cross-sectional shape and the same flow path cross-sectional area as the parallel internal flow paths 81 and the parallel internal refrigerant path 82. The flow direction of the cooling water flowing through the parallel internal flow path 81 is opposite to the flow direction of the refrigerant flowing through the parallel internal refrigerant path 82.

[0035] With the manifold 100 having such a configuration, heat exchange between the cooling water and the refrigerant can be performed not only between the parallel internal flow paths 81 and the parallel internal refrigerant path 82, but also between the closed internal flow paths 83 and the closed internal refrigerant path 84. As a result, even if the distance between the parallel internal flow paths 81 and the parallel internal refrigerant path 82 is the same as in the manifold 100 of the first embodiment, it is possible to obtain sufficient cooling performance using a water-cooled condenser 120 that is even smaller than that of the first embodiment. Note that the number of closed internal flow paths 83 and closed internal refrigerant path 84 does not have to be multiple, and may be one (the same applies to the following modified examples).

[0036] If it is difficult to form the closed internal flow passage 83 and the closed internal refrigerant passage 84 by directly drilling holes in the flow passage housing 105, the flow passage housing 105 may be configured by joining two housings (not shown). In this case, grooves that form the parallel internal flow passages 81, the parallel internal refrigerant passage 82, the closed internal flow passage 83, and the closed internal refrigerant passage 84 are formed on each of the joining surfaces of the two housings, and then the two housings are joined together, thereby forming the parallel internal flow passages 81, the parallel internal refrigerant passage 82, the closed internal flow passage 83, and the closed internal refrigerant passage 84 in the flow passage housing 105.

[0037] [Modification of Second Embodiment] Next, a manifold 100 according to a modification of the second embodiment will be described. In this modification, the closed internal flow path 83 and the closed internal refrigerant path 84 are different from those of the second embodiment. The other configurations are the same as those of the second embodiment, and therefore detailed description of the similar configurations will be omitted.

[0038] 5 , the extension direction of the closed internal flow path 83 relative to the parallel internal flow path 81 is not perpendicular, but extends in a direction forming an acute angle θ (an example of an acute angle) with respect to the flow direction of the cooling water. Also, the extension direction of the closed internal refrigerant path 84 relative to the parallel internal refrigerant path 82 is not perpendicular, but extends in a direction forming an acute angle θ with respect to the flow direction of the refrigerant.

[0039] The closed internal flow path 83 branches off at an acute angle θ with respect to the flow direction of the cooling water in the parallel internal flow path 81, and the closed internal refrigerant path 84 branches off at an acute angle θ with respect to the flow direction of the refrigerant in the parallel internal refrigerant path 82, so that the closed internal flow path 83 and the closed internal refrigerant path 84 are arranged parallel to and close to each other. This configuration allows the lengths of the closed internal flow path 83 and the closed internal refrigerant path 84 to be longer than in the second embodiment, even if the distance between the parallel internal flow path 81 and the parallel internal refrigerant path 82 is the same as in the second embodiment. This allows heat exchange between the closed internal flow path 83 and the closed internal refrigerant path 84 to be performed more efficiently than in the second embodiment, thereby achieving sufficient cooling performance even when a smaller water-cooled condenser 120 is used. Furthermore, because the closed internal flow path 83 and the closed internal refrigerant path 84 branch off at an acute angle with respect to the flow direction of the cooling water or refrigerant, pressure loss of the cooling water or refrigerant when the cooling water or refrigerant flows into the closed internal flow path 83 or the closed internal refrigerant path 84 can be minimized.

[0040] Another Modification of the Second Embodiment Next, a manifold 100 according to another modification of the second embodiment will be described. In this modification, the closed internal flow path 83 and the closed internal refrigerant path 84 are different from those of the second embodiment and its modification. The other configurations are the same as those of the second embodiment, and therefore detailed description of the similar configurations will be omitted.

[0041] As shown in FIG. 6 , in this modification, the closed internal flow path 83 and the closed internal refrigerant path 84 each have a right-angled triangular shape in a plan view, and are composed of the hypotenuse and its adjacent side of the right triangle. The other adjacent side is part of the parallel internal flow path 81. The portion of the closed internal flow path 83 corresponding to the hypotenuse of the right triangle extends in the direction of the branch angle θ, which is an acute angle with respect to the flow direction of the coolant, and the portion corresponding to the adjacent side is perpendicular to the flow direction of the coolant. Furthermore, the portion of the closed internal refrigerant path 84 corresponding to the hypotenuse of the right triangle extends in the direction of the branch angle θ, which is an acute angle with respect to the flow direction of the coolant, and the portion corresponding to the adjacent side is perpendicular to the flow direction of the coolant. That is, in this modification as well, the closed internal flow path 83 and the closed internal refrigerant path 84 are arranged so that the portions corresponding to the hypotenuse and the portions corresponding to the adjacent sides are parallel and adjacent to each other.

[0042] The portion corresponding to the hypotenuse of the closed internal flow path 83 branches at a branch angle θ in an acute direction relative to the flow direction of the coolant in the parallel internal flow path 81, and the portion corresponding to the hypotenuse of the closed internal refrigerant path 84 branches at a branch angle θ in an acute direction relative to the flow direction of the refrigerant in the parallel internal refrigerant path 82. Therefore, the portions corresponding to the hypotenuses of the closed internal flow path 83 and the closed internal refrigerant path 84 are arranged parallel to and close to each other, as well as the portions corresponding to the adjacent sides. By configuring the closed internal flow path 83 and the closed internal refrigerant path 84 in this manner, even if the distance between the parallel internal flow path 81 and the parallel internal refrigerant path 82 is the same as 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 a plan view) can be made longer than in the second embodiment. This allows heat exchange between the closed internal flow path 83 and the closed internal refrigerant path 84 to be performed more efficiently than in the second embodiment, thereby achieving sufficient cooling performance even when a smaller water-cooled condenser 120 is used. Furthermore, the locations corresponding to the oblique sides of the closed internal flow path 83 and the closed internal refrigerant path 84 branch off at an acute angle to the flow direction of the cooling water or refrigerant, and the locations corresponding to the adjacent sides of the closed internal flow path 83 and the closed internal refrigerant path 84 branch off in a direction perpendicular to the flow direction of the cooling water or refrigerant, thereby minimizing the pressure loss of the cooling water or refrigerant when the cooling water or refrigerant flows into or out of the closed internal flow path 83 or the closed internal refrigerant path 84.

[0043] [Another embodiment of the first and second embodiments] In the first and second embodiments, the coolant and the refrigerant that exchange heat flow in opposite directions within the flow path housing 105. However, they may flow in the same direction. In this case, the chiller 110 may be provided upstream and the water-cooled condenser 120 may be provided downstream.

[0044] In the first and second embodiments, the flow paths that perform heat exchange within the flow path housing 105 are linear or L-shaped, but this is not limited to this. By making the flow paths that perform heat exchange as long as possible, the chiller 110 and the water-cooled condenser 120 can be made smaller. Furthermore, the flow paths that perform heat exchange may be configured to perform heat exchange using plate members.

[0045] [Third Embodiment] [Configuration of Cooling System] A cooling system A including a manifold 100 according to a third embodiment is similar to the cooling system A according to the first embodiment shown in Fig. 1. The schematic configuration of the manifold 100 is also similar to that shown in Fig. 2.

[0046] A method for fixing the chiller 110 to the flow path housing 105 will be described below with reference to FIGS. 2 and 7 . The chiller 110 is fixed to the flow path housing 105 by being directly connected to the third internal refrigerant passage 73, the first internal refrigerant passage 71, the eighth internal passage 48, and the second internal passage 42. The chiller 110 has a refrigerant inlet 111 through which the refrigerant flows, a refrigerant outlet 112 through which the refrigerant flows, a cooling water inlet (an example of a "coolant inlet") 113 through which the cooling water flows, and a cooling water outlet (an example of a "coolant outlet") 114 through which the cooling water flows. The third internal refrigerant passage 73 and the refrigerant inlet 111, the first internal refrigerant passage 71 and the refrigerant outlet 112, the eighth internal passage 48 and the cooling water inlet 113, and the second internal passage 42 and the cooling water outlet 114 are joined by brazing using a brazing material 116. Brazing is characterized by high joint strength and by being less likely to cause changes in the shape or material of each housing, as it is performed at a temperature close to the melting point of the brazing material 116, which has a lower melting point than the housing of the flow path housing 105 or the chiller 110. In addition, because the joining is performed by filling the brazing material 116, the joint has excellent airtightness and liquid tightness.

[0047] Conventionally, the chiller was fixed to the flow path housing 105 with bolts or the like, which required multiple bolts, piping connecting the flow path to the heat exchanger, and seals to prevent leakage of refrigerant or cooling water. This increased the number of parts and labor required to fix the chiller, and increased the volume of the chiller. However, in this embodiment, the flow path and the inlet and outlet of the chiller 110 are joined by brazing, which simultaneously achieves the following: fixing the chiller 110 to the flow path housing 105 without bolts or the like (high joint strength and compact size), communication between the flow path and the chiller 110 (no piping required), and ensuring airtightness and watertightness of the joints (no seals required). Therefore, by reducing the number of parts and labor required, a compact, low-cost manifold 100 can be realized.

[0048] The passage housing 105 of this embodiment is formed by joining an upper housing 105a and a lower housing 105b. As shown in FIG. 2 , the third internal refrigerant passage 73, the first internal refrigerant passage 71, the eighth internal passage 48, and the second internal passage 42 penetrate the upper housing 105a from the boundary between the upper housing 105a and the lower housing 105b. After the inlet and outlet of the chiller 110 are positioned in these penetrating passages, brazing material 116 is applied to the respective boundaries between the third internal refrigerant passage 73 and the refrigerant inlet 111, the first internal refrigerant passage 71 and the refrigerant outlet 112, the eighth internal passage 48 and the cooling water inlet 113, and the second internal passage 42 and the cooling water outlet 114. Then, a brazing tool is inserted into each of the third internal refrigerant passage 73, the first internal refrigerant passage 71, the eighth internal passage 48, and the second internal passage 42 from the underside of the upper housing 105a (the boundary with the lower housing 105b), and brazing is performed. At this time, the thinner the upper housing 105a, the easier it is to insert a brazing tool, and therefore brazing can be performed more easily.

[0049] Fourth Embodiment Next, a manifold 100 according to a fourth embodiment will be described with reference to Figures 8 and 9. In this embodiment, a chiller 110 is disposed inside a flow path housing 105. Specifically, a flow path having a heat exchange function for the chiller 110 is formed inside the flow path housing 105. The other configurations are similar to those of the third embodiment. Therefore, in the description of this embodiment, parts having the same configuration as those of the third embodiment are denoted by the same reference numerals, and detailed description of the similar configurations will be omitted.

[0050] The flow path housing 105 is formed by joining an upper housing 105a and a lower housing 105b. A heat exchange flow path 117 (an example of a laminated flow path) is formed inside the flow path housing 105, extending from the upper housing 105a to the lower housing 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 laminated flow path) and a plurality of heat exchange cooling water flow paths 117b (an example of a laminated flow path). The plurality of heat exchange cooling water flow paths 117b are connected to the eighth internal flow path 48 and the second internal flow path 42, respectively. In FIG. 9 , the plurality of heat exchange refrigerant flow paths 117a are depicted as independent flow paths, but in reality, they are connected to the third internal refrigerant path 73 and the first internal refrigerant path 71, respectively. A flow path wall 118, which separates the heat exchange refrigerant flow path 117a and the heat exchange cooling water flow path 117b, is supported by the flow path housing 105.

[0051] By disposing the chiller 110 inside the flow path housing 105 in this way, the manifold 100 can be made smaller than when the chiller 110 is attached externally to the flow path housing 105 .

[0052] Other Embodiments of the Third and Fourth Embodiments (1) In the third and fourth embodiments, the chiller 110 is fixed to the flow path housing 105 by brazing, but this is not limited to this. As long as the joining strength, airtightness, liquid-tightness, etc. of the chiller 110 to the flow path housing 105 can be ensured, any method such as welding may be used for joining instead of brazing.

[0053] (2) In the above third and fourth embodiments, the joining and fixing of the chiller 110 to the flow path housing 105 was described, but the same can also be applied to the water-cooled condenser 120 and other heat exchangers.

[0054] Fifth Embodiment Fig. 10 is a diagram showing the circuit configuration of a cooling system 300 including a manifold 201 of this embodiment. Fig. 11 is a diagram showing a schematic configuration of the manifold 201 of this embodiment. The manifold 201 is configured with a refrigerant circuit through which a refrigerant such as a hydrofluorocarbon (HFC) or a hydrofluoroolefin (HFO) flows.

[0055] The manifold 201 includes a flow path housing 210. The flow path housing 210 is formed using a metal material, such as aluminum, that has high thermal conductivity. The flow path housing 210 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 drilling holes in the metal material. An on-off valve (not shown) is provided in the third refrigerant flow path 213 upstream of a first expansion valve 235 (described later). For example, if the manifold 201 is provided in a vehicle, the on-off valve is opened when the vehicle is using interior air conditioning, and closed when the vehicle is not using interior air conditioning.

[0056] 11 , 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 chiller (an example of an "evaporator") 255 are provided on the outside of the flow path housing 210. In this embodiment, the water-cooled condenser 230, the evaporator 245, the check valve 250, and the chiller 255 are integrated with the flow path housing 210. Note that the accessories integrated with the flow path housing 210 are optional and are not particularly limited.

[0057] The first refrigerant flow path 211 is a flow path that circulates a refrigerant (an example of a "first cooling fluid") between the compressor 225 and the water-cooled condenser 230. The second refrigerant flow path 212 is a flow path that circulates a refrigerant (an example of a "first cooling fluid") 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 circulates a refrigerant (an example of a "second cooling fluid") between the first expansion valve 235 and the evaporator 245 and between the second expansion valve 240 and the chiller 255, respectively. The fourth refrigerant flow path 214 is a flow path that circulates a refrigerant (an example of a "second cooling fluid") between the evaporator 245 and / or the chiller 255 and the compressor 225.

[0058] The accumulator 220 is a gas-liquid separator that stores the liquid refrigerant and separates the refrigerant into gas and liquid. The gaseous refrigerant separated by the accumulator 220 flows through the fourth refrigerant flow path 214 and is sent to the compressor 225.

[0059] The compressor 225 compresses the gaseous refrigerant from the accumulator 220. This increases the pressure of the refrigerant, and its temperature (denoted as "T1"). The high-temperature, high-pressure gaseous refrigerant is sent to the water-cooled condenser 230 via the first refrigerant flow path 211.

[0060] Cooling water flows through the water-cooled condenser 230 via a 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, high-pressure gaseous refrigerant sent to the water-cooled condenser 230 loses heat to the cooling water. As a result, the high-temperature, high-pressure gaseous refrigerant condenses and becomes a medium-temperature, high-pressure liquid refrigerant. In other words, the temperature of the refrigerant drops from T1 to T2. The medium-temperature, high-pressure liquid refrigerant is sent to the first expansion valve 235 and / or the second expansion valve 240 via the second refrigerant flow path 212.

[0061] The first expansion valve 235 is configured so that the flow path area is suddenly narrower than that of the second refrigerant flow path 212, allowing only a small amount of refrigerant to flow. This causes the refrigerant pressure to decrease, and as the pressure decreases, the refrigerant temperature decreases, causing gaseous refrigerant to mix with the liquid refrigerant. The low-temperature, low-pressure refrigerant is sent to the evaporator 245 via the third refrigerant flow path 213. Here, it is assumed that the refrigerant temperature has decreased to T3.

[0062] The evaporator 245 takes in outside air and exchanges heat between the outside air and the low-temperature, low-pressure refrigerant. As a result, the temperature of the refrigerant rises and changes to gaseous refrigerant, which cools the outside air and is used to cool the interior of the vehicle. The medium-temperature, 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 out from the evaporator 245 at this time is designated as T4. T4 is higher than T3 but lower than T2.

[0063] A part or all of the refrigerant condensed by the water-cooled condenser 230 branches off from the second refrigerant flow path 212 and is sent to the second expansion valve 240. In the second expansion valve 240, the medium-temperature, high-pressure liquid refrigerant is transformed into a low-temperature, low-pressure refrigerant, similar to the first expansion valve 235. This low-temperature, low-pressure refrigerant is sent to the chiller 255 via the third refrigerant flow path 213.

[0064] Cooling water flows through the chiller 255 via a cooling water flow path 256 that is different from the third refrigerant flow path 213 and the fourth refrigerant flow path 214. The low-temperature, low-pressure refrigerant sent to the chiller 255 cools the cooling water and provides heat. This changes the refrigerant into a medium-temperature, low-pressure gaseous refrigerant. The gaseous refrigerant is sent to the accumulator 220 via the fourth refrigerant flow path 214. The refrigerant sent from the chiller 255 via the fourth refrigerant flow path 214 does not flow to the evaporator 245 due to the check valve 250.

[0065] As described above, a high-temperature, high-pressure refrigerant (refrigerant at temperature T1) is delivered from the compressor 225 to the first refrigerant flow path 211, and a medium-temperature, high-pressure refrigerant (refrigerant at temperature T2) is delivered from the water-cooled condenser 230 to the second refrigerant flow path 212. A low-temperature, low-pressure refrigerant (refrigerant at temperature T3) is delivered from the first expansion valve 235 to the third refrigerant flow path 213, and a medium-temperature, low-pressure refrigerant (refrigerant at temperature T4) is delivered from the evaporator 245 and / or chiller 255 to the fourth refrigerant flow path 214. Here, T1 > T2 > T4 > T3. That is, in this 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 manifold 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.

[0066] The flow path housing 210 is configured to perform heat exchange between the high-temperature flow path 201H and the low-temperature flow path 201L. In this embodiment, heat exchange occurs between the second refrigerant flow path 212, which is the high-temperature flow path 201H, and the fourth refrigerant flow path 214, which is the low-temperature flow path 201L. 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 this embodiment, the second refrigerant flow path 212, through which the refrigerant flows from the water-cooled condenser 230 to the first expansion valve 235 and / or the second expansion valve 240, and the fourth refrigerant flow path 214, through which the refrigerant flows from the evaporator 245 to the accumulator 220 via the check valve 250, are arranged parallel to each other between X1 and X2 along the X direction. Furthermore, in order to improve heat exchange efficiency, the distance Y1 in the Y direction perpendicular to the X direction is configured to be short. The distance Y1 is preferably set (the distance Y2 is preferably as close as possible) based on the machining accuracy when forming the second refrigerant flow path 212 and the fourth refrigerant flow path 214 by drilling. The refrigerant flow path for heat exchange is preferably formed on the cut surface of the flow path housing 210.

[0067] Between X1 and X2, the refrigerant flows from X2 to X1 in the second refrigerant flow path 212, and from X1 to X2 in the fourth refrigerant flow path 214. Therefore, in this embodiment, the refrigerant flows in the high-temperature flow path 201H and the low-temperature flow path 201L in opposite directions. This allows the refrigerant flowing through the second refrigerant flow path 212 to exchange heat with the refrigerant flowing through the fourth refrigerant flow path 214, and the refrigerant flowing through the fourth refrigerant flow path 214 to exchange heat with the refrigerant flowing through the second refrigerant flow path 212. The temperature of the refrigerant flowing through the high-temperature flow path 201H gradually decreases as it flows through the high-temperature flow path 201H in a first direction (from X2 to X1), and the temperature of the refrigerant flowing through the low-temperature flow path 201L gradually increases as it flows through the low-temperature flow path 201L in a 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 is equalized, thereby improving the heat exchange efficiency. Therefore, it is possible to perform heat exchange efficiently.

[0068] In this embodiment, the second refrigerant flow path 212, through which the refrigerant flows from the water-cooled condenser 230 to the second expansion valve 240, and the third refrigerant flow path 213, through which the refrigerant flows from the second expansion valve 240 to the chiller 255, are arranged parallel to each other between X3 and X4 along the X direction. To improve heat exchange efficiency, the distance Y2 between the second refrigerant flow path 212 and the third refrigerant flow path 213 is shortened. This distance Y2 is preferably set based on the machining accuracy when the second refrigerant flow path 212 and the third refrigerant flow path 213 are formed by drilling (preferably closer). The refrigerant flow paths for heat exchange are preferably formed on the cut surfaces of the flow path housing 210.

[0069] Between X3 and X4, the refrigerant flows from X4 to X3 in the second refrigerant flow path 212, and from X3 to X4 in the third refrigerant flow path 213. Therefore, here too, the flow directions of the refrigerant in the high-temperature flow path 201H and the low-temperature flow path 201L are configured to be opposite to each other. As a result, the refrigerant flowing through the second refrigerant flow path 212 exchanges heat with the refrigerant flowing through the third refrigerant flow path 213, and the refrigerant flowing through the third refrigerant flow path 213 exchanges heat with the refrigerant flowing through the second refrigerant flow path 212. The temperature of the refrigerant flowing through the high-temperature flow path 201H gradually decreases as it flows through the high-temperature flow path 201H in a first direction (from X4 to X3), and the temperature of the refrigerant flowing through the low-temperature flow path 201L gradually increases as it flows through the low-temperature flow path 201L in a 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 is equalized, thereby improving the heat exchange efficiency. Therefore, it is possible to perform heat exchange efficiently.

[0070] 12 is a diagram showing the relationship between the second refrigerant flow path 212 and the fourth refrigerant flow path 214 and other flow paths according to this embodiment. As shown in FIG. 12 , the second refrigerant flow path 212, which circulates refrigerant between the water-cooled condenser 230 and the first expansion valve 235, and the fourth refrigerant flow path 214, which circulates refrigerant between the evaporator 255 and the compressor 225, are provided at intervals shorter than the intervals between the other flow paths provided in the flow path housing 210. The second refrigerant flow path 212 is a refrigerant flow path through which refrigerant flows from the water-cooled condenser 230 to the first expansion valve 235. The fourth refrigerant flow path 214 is a refrigerant flow path through which refrigerant flows from the evaporator 245 to the compressor 225 via the accumulator 220. The other flow paths provided in the flow path housing 210 correspond to a first refrigerant flow path 211 through which refrigerant flows from the compressor 225 to the water-cooled condenser 230, and a third refrigerant flow path 213 through which refrigerant flows 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 distance shorter than the distance between the first refrigerant flow path 211 and the third refrigerant flow path 213.

[0071] That is, in the vicinity of the evaporator 245 , the fourth refrigerant flow path 214 is configured to be closer to the second refrigerant flow path 212 than the first refrigerant flow path 211 and the third refrigerant flow path 213 .

[0072] FIG. 13 is a Mollier diagram showing the thermal cycle of the cooling system 300. In FIG. 13, the horizontal axis represents the specific enthalpy of the refrigerant, and the vertical axis represents the pressure of the refrigerant. The Mollier diagram is divided into three regions depending on the combination of specific enthalpy and pressure: region R1 where the refrigerant exists in a supercooled state (liquid state), region R2 where the refrigerant exists as a wet vapor (gas-liquid mixed state), and region R3 where the refrigerant exists as a superheated vapor (gaseous state). The boundary between the supercooled state and the wet vapor state is the saturated liquid line L1, and the boundary between the wet vapor state and the superheated vapor state is the saturated vapor line L2. The boundary between the saturated liquid line L1 and the saturated vapor line L2 corresponds to the critical point CP.

[0073] When the refrigerant is pressurized (compressed) by the compressor 225, the specific enthalpy increases, and the medium-temperature, low-pressure gaseous refrigerant shown in (a) of FIG. 13 becomes the high-temperature, high-pressure gaseous refrigerant shown in (b) of FIG. 13. The high-temperature, high-pressure refrigerant shown in (b) of FIG. 13 is condensed when sent to the water-cooled condenser 30, and the specific enthalpy decreases under isobaric conditions. As a result, the refrigerant becomes the medium-temperature, high-pressure liquid refrigerant shown in (c) of FIG. 13. The medium-temperature, high-pressure refrigerant shown in (c) of FIG. 13 expands in the first expansion valve 235, and its pressure decreases. As a result, the refrigerant becomes the low-temperature, low-pressure gas-liquid mixture refrigerant shown in (d) of FIG. 13. The low-temperature, low-pressure refrigerant shown in (d) of FIG. 13 evaporates in the evaporator 245, and the specific enthalpy increases under isobaric conditions. As a result, the refrigerant becomes the medium-temperature, low-pressure gaseous refrigerant shown in (a) of FIG. 13.

[0074] In this embodiment, heat exchange between the second refrigerant flow path 212, which is the high-temperature flow path 201H, and the fourth refrigerant flow path 214, which is the low-temperature flow path 201L, in the flow path housing 210 allows the refrigerant to be preheated before being pressurized by the compressor 225. This increases the specific enthalpy of the refrigerant before pressurization, and the refrigerant generated by the compressor 225 is compressed along the dashed lines shown in (e) to (f). Meanwhile, heat exchange between the second refrigerant flow path 212, which is the high-temperature flow path 201H, and the fourth refrigerant flow path 214, which is the low-temperature flow path 201L, allows the refrigerant condensed in the water-cooled condenser 230 to be precooled. This reduces the specific enthalpy of the refrigerant before expansion in the first expansion valve 235, and the refrigerant expands in the first expansion valve 235 along the dashed lines shown in (g) to (h).

[0075] In this way, in the flow path housing 210, heat exchange occurs between the second refrigerant flow path 212, which is the high-temperature flow path 201H, and the fourth refrigerant flow path 214, which is the low-temperature flow path 201L, so that the refrigerant pressurized by the compressor 225 becomes a more superheated vapor state, and the refrigerant sent to the first expansion valve 235 becomes a more supercooled state. This makes it possible to improve the coefficient of performance with a compact configuration.

[0076] Other Embodiments of the Fifth Embodiment In the above embodiment, it has been described that heat exchange occurs in the flow path housing 210 between the second refrigerant flow path 212, which is the high-temperature flow path 201H, and the fourth refrigerant flow path 214, which is the low-temperature flow path 201L. For example, the flow path housing 210 can be configured so that heat exchange occurs between the first refrigerant flow path 211, which is the high-temperature flow path 201H, and the third refrigerant flow path 213, which is the low-temperature flow path 201L. Alternatively, heat exchange may occur between the first refrigerant flow path 211, which is the high-temperature flow path 201H, and the fourth refrigerant flow path 214, which is the low-temperature flow path 201L, or between the second refrigerant flow path 212, which is the high-temperature flow path 201H, and the third refrigerant flow path 213, which is the low-temperature flow path 201L. Furthermore, heat exchange may be performed between the first refrigerant flow path 211 and the second refrigerant flow path 212, which are the high-temperature flow path 201H, and the third refrigerant flow path 213, which is the low-temperature flow path 201L, or heat exchange may be performed between the first refrigerant flow path 211 and the second refrigerant flow path 212, which are the high-temperature flow path 201H, and the fourth refrigerant flow path 214, which is the low-temperature flow path 201L. Of course, heat exchange may be performed between the first refrigerant flow path 211, which is the high-temperature flow path 201H, and the third refrigerant flow path 213 and the fourth refrigerant flow path 214, which are the low-temperature flow path 201L, or heat exchange may be performed between the second refrigerant flow path 212, which is the high-temperature flow path 201H, and the third refrigerant flow path 213 and the fourth refrigerant flow path 214, which are the low-temperature flow path 201L.

[0077] In the fifth embodiment, the high-temperature flow path 201H and the low-temperature flow path 201L are described as being parallel to and adjacent to each other, but the high-temperature flow path 201H and the low-temperature flow path 201L may be arranged adjacent to each other but not parallel to each other, or the high-temperature flow path 201H and the low-temperature flow path 201L may be arranged so as to intersect each other. Furthermore, the shape of the high-temperature flow path 201H and the low-temperature flow path 201L arranged parallel to each other and adjacent to each other may be, for example, a serpentine flow path, and is not particularly limited.

[0078] In the above fifth embodiment, the flow directions of the refrigerant in the high-temperature flow path 201H and the low-temperature flow path 201L are described as being opposite to each other, but the flow directions of the refrigerant in the high-temperature flow path 201H and the low-temperature flow path 201L may be the same as each other.

[0079] In FIG. 11 of the fifth embodiment, the high-temperature flow path 201H and the low-temperature flow path 201L are shown extending in a predetermined direction (X direction). The high-temperature flow path 201H and the low-temperature flow path 201L may each be formed with a comb-like portion 260 that protrudes from one side of the high-temperature flow path 201H or the low-temperature flow path 201L toward the other side. The high-temperature flow path 201H and the low-temperature flow path 201L with such a comb-like portion 260 formed thereon are shown in FIG. 14. As shown in FIG. 14, the high-temperature flow path 201H is provided with a comb-like portion 260 (specifically, the comb-like portion 260H) that protrudes from the high-temperature flow path 201H toward the low-temperature flow path 201L, and the low-temperature flow path 201L is provided with a comb-like portion 260 (specifically, the comb-like portion 260L) that protrudes from the low-temperature flow path 201L toward the high-temperature flow path 201H. 14, the comb-tooth portion 260H and the comb-tooth portion 260L are configured in a state in which the comb-tooth portion 260H is inserted between two comb-tooth portions 260L, and the comb-tooth portion 260L is inserted between two comb-tooth portions 260H. This increases the area in which the high-temperature flow path 201H and the low-temperature flow path 201L are close to each other (the area contributing to heat exchange), thereby improving the heat exchange efficiency.

[0080] In the example of FIG. 14 , the comb-tooth portions 260 are formed to protrude from each of the high-temperature flow path 201H and the low-temperature flow path 201L in a direction perpendicular to the high-temperature flow path 201H and the low-temperature flow path 201L. However, as shown in FIG. 15 , the comb-tooth portions 260 may be configured to have an obtuse angle with respect to the perpendicular direction, or the comb-tooth portions 260 may protrude in an arc shape. Also, as shown in FIG. 16 , the comb-tooth portions 260 may be configured to have a triangular shape in a plan view. In this case, for example, the comb-tooth portions 260 may be configured to have a side that forms an obtuse angle upstream with respect to the flow direction of the refrigerant flowing through the high-temperature flow path 201H and the low-temperature flow path 201L, and a side that is perpendicular downstream with respect to the flow direction of the refrigerant flowing through the high-temperature flow path 201H and the low-temperature flow path 201L. Of course, the downstream side may be configured to have a side that forms an acute angle downstream with respect to the flow direction of the refrigerant flowing through the high-temperature flow path 201H and the low-temperature flow path 201L. Such a configuration can facilitate the entry of the refrigerant into the comb-tooth portions 260. Therefore, the high temperature flow path 201H and the low temperature flow path 201L can be brought closer to each other without interfering with the flow of the refrigerant in the high temperature flow path 201H and the low temperature flow path 201L.

[0081] In the fifth embodiment, the flow passages in the flow passage housing 210 are formed by drilling, but they may also be formed by casting or forging, for example.

[0082] [Outline of the above embodiment] The manifolds 100 and 201 described above will now be outlined.

[0083] (1) The manifold 100, 201 includes a flow path housing 105, 210 having 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, and is configured to perform heat exchange in the flow path housing 105, 210 between the first cooling fluid flowing through the first flow path 71, 72, 73 and the second cooling fluid flowing through the second flow path 41, 42, 48, 49.

[0084] According to this configuration, heat exchange is performed between the first cooling fluid flowing through the first flow passages 71, 72, 73 provided in the flow passage housing 105, 210 of the manifold 100, 201 and the second cooling fluid flowing through the second flow passages 41, 42, 48, 49, thereby achieving sufficient cooling performance even with a small heat exchanger. Furthermore, because heat exchange can be performed within the flow passage housing 105, 210, the manifold 100, 201 can be made smaller than when a heat exchanger is externally attached to the flow passage housing 105, 210. Furthermore, cooling of the first cooling fluid flowing through the first flow passages 71, 72, 73 and heating of the second cooling fluid flowing through the second flow passages 41, 42, 48, 49 can be performed within the flow passage housing 105, 210. By performing heat exchange between the fluids within the flow passage housing 105, 210, it is possible to improve the coefficient of performance of, for example, the compressor 22, 225 and the expansion valve 26, 235, 240. Therefore, the internal heat exchanger for cooling and heating the fluid can be made smaller or heat exchange can be performed without providing a separate heat exchanger, so that the manifolds 100 and 201 can be made smaller.

[0085] (2) In the manifold 100 described in (1), the first flow paths 71, 72, and 73 are refrigerant flow paths that circulate a refrigerant as a first cooling fluid between the evaporator 110 and the condenser 120, and the second flow paths 41, 42, 48, and 49 are cooling flow paths that circulate a coolant as a second cooling fluid to at least the battery 9.

[0086] According to this configuration, heat is exchanged not only between the evaporator 110 and the condenser 120, which are heat exchangers, but also between the refrigerant flowing through the refrigerant flow passages provided in the flow passage housing 105 of the manifold 100 and the coolant flowing through the cooling flow passages, so that the required cooling performance can be obtained even when using small evaporators 110 and condensers 120. Therefore, it is possible to provide a manifold 100 that can obtain sufficient cooling performance even when using small heat exchangers.

[0087] (3) In the manifold 100 described in (2), it is preferable that a water-cooled condenser 120 serving as a condenser 120 for the refrigerant is mounted in the flow path housing 105 at a position upstream of the refrigerant flow direction, and a chiller 110 serving as an evaporator 110 for the refrigerant is mounted at a position downstream of the refrigerant flow direction.

[0088] According to this configuration, by arranging the water-cooled condenser 120 as the condenser 120 at a position upstream in the direction of refrigerant flow, the refrigerant condensed in the water-cooled condenser 120 can be circulated to provide heat to the low-temperature cooling liquid, and therefore, it is possible to condense any refrigerant that was not completely condensed in the water-cooled condenser 120. Furthermore, by arranging the chiller 110 as the evaporator 110 at a position downstream in the direction of refrigerant flow, the refrigerant before flowing into the chiller 110 can be circulated to remove heat from the high-temperature cooling liquid, and therefore, a portion of the refrigerant can be evaporated before flowing into the chiller 110.

[0089] (4) In the manifold 201 described in (1), the first flow path is preferably a first refrigerant flow path 211 that circulates a refrigerant as a first cooling fluid between the compressor 225 and the condenser 230, or a second refrigerant flow path 212 that circulates a refrigerant between the condenser 230 and the expansion valve 235, and the second flow path is preferably a third refrigerant flow path 213 that circulates a refrigerant as a second cooling fluid that is at a lower temperature than the first cooling fluid between the expansion valves 235, 240 and the evaporators 245, 255, or a fourth refrigerant flow path 214 that circulates a refrigerant between the evaporators 245, 255 and the compressor 225.

[0090] According to this configuration, cooling of the refrigerant flowing through at least one of the first refrigerant flow path 211 and the second refrigerant flow path 212 and heating of the refrigerant flowing through at least one of the third refrigerant flow path 213 and the fourth refrigerant flow path 214 can be performed within the flow path housing 210. By performing heat exchange between refrigerants within this flow path housing 210, it is possible to improve the coefficient of performance of the compressor 225 and the expansion valves 235, 240. Therefore, since heat exchange can be performed without downsizing or separately providing an internal heat exchanger that cools and heats the refrigerant, it is possible to downsize the heat exchange system.

[0091] (5) In the manifold 100 described in (1), the first flow paths 71, 72, and 73 are refrigerant flow paths that circulate a refrigerant as a first cooling fluid through the heat exchanger, and the second flow paths 41, 42, 48, and 49 are cooling flow paths that circulate a cooling liquid as a second cooling fluid through the heat exchanger. The heat exchanger has a refrigerant inlet 111 through which the refrigerant flows, a refrigerant outlet 112 through which the refrigerant flows, a cooling liquid inlet 113 through which the cooling liquid flows, and a cooling liquid outlet 114 through which the cooling liquid flows. It is preferable that the heat exchanger is fixed to the flow path housing 105 by joining the refrigerant flow path and the refrigerant inlet 111, the refrigerant flow path and the refrigerant outlet 112, the cooling flow path and the cooling liquid inlet 113, and the cooling flow path and the cooling liquid outlet 114, respectively.

[0092] According to this configuration, the heat exchanger can be fixed to the flow path housing 105 without using bolts or the like, which eliminates the need to provide flanges for attaching bolts or the like to the heat exchanger, thereby reducing the size of the heat exchanger, thereby realizing a compact and low-cost manifold 100.

[0093] (6) In the manifold 100 described in (5), it is preferable that the heat exchanger has a laminated flow path 117.

[0094] According to this configuration, the manifold 100 can be equipped with the necessary functions as a heat exchanger.

[0095] (7) In the manifold (100, 201) described in any one of (1) to (6), it is preferable that the first flow paths (71, 72, 73) and the second flow paths (41, 42, 48, 49) are provided close to each other.

[0096] This configuration makes it possible to improve heat exchange efficiency by facilitating heat exchange between the first flow paths 71, 72, 73 and the second flow paths 41, 42, 48, 49. In addition, the arrangement of the first flow paths 71, 72, 73 and the second flow paths 41, 42, 48, 49 is simplified, allowing the manifolds 100, 201 to be made smaller.

[0097] (8) In the manifold 201 described in any one of (1) to (7), it is preferable that a comb-tooth portion 260 protruding from one side of the first flow path and the second flow path toward the other side is formed in each of the first flow path and the second flow path.

[0098] According to this configuration, heat exchange between the first cooling fluid and the second cooling fluid can be performed not only between the first flow path and the second flow path, but also in the comb-teeth-shaped portion 260. Furthermore, the comb-teeth-shaped portion 260 can increase the area where the first flow path and the second flow path are close to each other. This can further improve heat exchange efficiency. As a result, sufficient cooling performance can be obtained even when a smaller heat exchanger is used.

[0099] (9) In the manifold 201 described in (7), it is preferable that the flow path for circulating the refrigerant between the condenser 230 and the expansion valves 235, 240 and the flow path for circulating the refrigerant between the evaporators 245, 255 and the compressor 225 are arranged at intervals shorter than the intervals between the other flow paths provided in the flow path housing 210.

[0100] According to this configuration, heat exchange can be performed between the flow path through which the refrigerant flows between the condenser 230 and the expansion valves 235, 240 and the flow path through which the refrigerant flows between the evaporator 245, 255 and the compressor 225. For example, by making the flow direction of the refrigerant flowing through the flow path between the condenser 230 and the expansion valves 235, 240 and the flow path between the evaporator 245, 255 and the compressor 225 opposite (reverse) to each other, the temperature difference between the flow path between the condenser 230 and the expansion valves 235, 240 and the flow path between the evaporator 245, 255 and the compressor 225 becomes uniform, thereby improving heat exchange efficiency. Therefore, heat exchange can be performed efficiently.

[0101] (10) In the manifold 100 described in (7), it is preferable that the refrigerant flow path through which the refrigerant flows as a first cooling fluid flowing out from the evaporator 110 and the cooling flow path through which the cooling liquid flows as a second cooling fluid flowing into the evaporator 110 are arranged at intervals shorter than the intervals between the other flow paths provided in the flow path housing 105.

[0102] According to this configuration, heat exchange can be performed between the refrigerant flowing through the refrigerant flow path from the evaporator 110 and the cooling liquid flowing through the cooling flow path to the evaporator 110. As a result, even if a small evaporator 110 is used, sufficient cooling performance can be obtained.

[0103] The technology disclosed herein can be used in manifolds.

[0104] [First embodiment] 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 flow path, refrigerant pipe), 81: parallel internal flow path (second flow path, cooling flow path, cooling pipe), 82: parallel internal refrigerant path (first flow path, refrigerant flow path, refrigerant pipe), 83: closed internal flow path (second flow path, closed cooling flow path, cooling flow path, cooling pipe), 84: closed internal refrigerant path (first flow path, closed refrigerant flow path, refrigerant flow path, refrigerant pipe), 100: manifold, 105: flow path housing, 110: chiller (evaporator), 120: water-cooled condenser (condenser, heat exchanger).

[0105] Second embodiment 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)

[0106] [Third embodiment] 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, 230: water-cooled condenser, 235: first expansion valve, 240: second expansion valve, 245: evaporator, 255: chiller, 260: comb-like portion, 260H: comb-like portion, 260L: comb-like portion

Claims

1. a first flow passage through which a first cooling fluid flows; a second flow passage housing having a second cooling fluid therethrough; A manifold for exchanging heat between the first cooling fluid flowing through the first flow passage and the second cooling fluid flowing through the second flow passage in the flow passage housing.

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

3. 3. The manifold of claim 2, wherein a water-cooled condenser serving as the condenser for the refrigerant is mounted in the flow path housing at a position upstream of the flow direction of the refrigerant, and a chiller serving as the evaporator for the refrigerant is mounted in a position downstream of the flow direction of the refrigerant.

4. the first flow path is a first refrigerant flow path that circulates a refrigerant as the first cooling fluid between a compressor and a condenser, or a second refrigerant flow path that circulates the refrigerant between the condenser and an expansion valve, The manifold according to claim 1, wherein the second flow path is a third refrigerant flow path that circulates the refrigerant as the second cooling fluid, which has a lower temperature than the first cooling fluid, between the expansion valve and an evaporator, or a fourth refrigerant flow path that circulates the refrigerant between the evaporator and the compressor.

5. The first flow path is a refrigerant flow path that circulates a refrigerant as the first cooling fluid through the heat exchanger, The second flow path is a cooling flow path that circulates a cooling liquid as the second cooling fluid through the heat exchanger, the heat exchanger has a refrigerant inlet through which the refrigerant flows, a refrigerant outlet through which the refrigerant flows, a cooling liquid inlet through which the cooling liquid flows, and a cooling liquid outlet through which the cooling liquid flows, 2. The manifold of claim 1, wherein the heat exchanger is secured to the flow passage housing by joining the refrigerant flow passage to the refrigerant inlet, the refrigerant flow passage to the refrigerant outlet, the cooling flow passage to the coolant inlet, and the cooling flow passage to the coolant outlet, respectively.

6. The manifold of claim 5 , wherein the heat exchanger has stacked flow paths.

7. The manifold according to any one of claims 1 to 6, wherein the first flow passage and the second flow passage are provided adjacent to each other.

8. The manifold according to any one of claims 1 to 6, wherein each of the first flow path and the second flow path is formed with a comb-tooth-shaped portion protruding from one side of the first flow path and the second flow path toward the other side.

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

10. 8. The manifold according to claim 7, wherein a refrigerant flow path through which a refrigerant as the first cooling fluid flows out of an evaporator, and a cooling flow path through which a cooling liquid as the second cooling fluid flows into the evaporator are provided at intervals shorter than intervals between other flow paths provided in the flow path housing.